DE29610473U1 - Distance-adjustable bracket for storing a pipeline - Google Patents

Description

PATENT ATTORNEYS

DiPL-ING. R. LEMCKE
DR.-NG. HJ BROMMER
DIPL-ING. F. PETERSEN

BISMARCKSTRASSE 16
76133 KARLSRUHE

TELEPHONE (0721) 912800
FAX (07 21) 21105

13 June 1996 16 667 (Bl/mr)

Description

The invention relates to a holder with variable spacing for supporting a pipeline, in particular in a height-adjustable manner, wherein the holder consists of a stationary lower bearing part and an upper bearing part with variable spacing therefrom, which at least indirectly supports the pipeline.

Such brackets are known in pipeline construction both for fixed bearings, in which the pipeline is firmly connected to the upper part of the bearing by welding, for example, and for roller bearings, in which the pipeline is arranged so that it can be moved using rolling bearings arranged on the upper part of the bearing. In order to be as flexible as possible with regard to the bracket position when installing the pipeline, such brackets are designed with variable spacing, i.e. the upper part of the bearing can be fixed at different spacing positions relative to the lower part of the bearing.

For example, the distance between brackets of the type described above can be changed by providing a spindle-nut drive between the lower and upper parts of the bearing. In this case, a rotating, but stationary threaded spindle is arranged on the lower part of the bearing.

net, which extends through a hole with an internal thread provided in the upper part of the bearing and whereby the upper part of the bearing is arranged so that it can be moved relative to the lower part of the bearing, but cannot rotate. A rotation of the threaded spindle thus leads to a displacement and change in the distance between the two bearing parts.

However, such brackets have the disadvantage that their construction and the change in distance during assembly are quite complex, particularly due to the spindle-nut drive. This is because spindle-nut drives are more suitable for small feed movements when under load, since even a large rotational movement only leads to a small change in distance. However, this aspect is more of a hindrance for a bracket with adjustable distance: This is because when the bracket is first and usually only installed once, a quick and simple feed movement is desired. In addition, the bracket is still unloaded at this point, which is why spindle-nut drives, in which a change in distance occurs while largely compensating for the forces acting in the feed direction, are incorrectly or over-dimensioned for the purpose at hand.

In addition, both connection or coupling points between the threaded spindle and the two bearing parts are arranged perpendicular to the direction of the change in distance and thus usually also perpendicular to the direction of action of the forces to be absorbed by the bracket. Consequently, they and their connections to the bearing parts must be designed to be sufficiently stable, which leads to a significant increase in the material thickness required for the effective forces.

Based on this, the present invention is based on the task of providing a distance-adjustable holder for pipelines, which is not only easy to manufacture, but is also characterized by a simple and easy-to-use device for changing the distance, but at the same time is also able to absorb any forces that may occur.

This object is achieved according to the invention in that the lower and upper parts of the bearing have sections that overlap one another and at least partially lie against one another, that in each of these sections at least one slot-shaped recess is provided for receiving a fastening means that secures the two bearing parts to one another, and that the recesses are arranged in a direction that differs from the direction of the change in distance and cross one another. This results in a drastic simplification of the mounting structure: Instead of having to provide corresponding projections on the bearing parts for arranging the spindle-nut drive, as in the prior art, only at least one slot-shaped recess is provided in each of the two bearing parts, through which a conventional fastening means, for example a screw-nut connection, can then extend. This means that the two bearing parts can be made from simple sheet metal parts with a low wall thickness, as no solid material needs to be provided for the insertion of a thread, as is the case with the spindle-nut drive.

On the other hand, the change in the distance between the two bearing parts is also greatly simplified: By slightly loosening the fastening means, the mutual fixation of the two bearing parts is removed, whereupon they can be moved relative to each other according to the length of the slot-shaped recesses, without the need for an additional feed movement of the fastening means, such as turning the screw to match the change in distance.

Distance change devices are known from other specialist areas that have slot-shaped recesses for receiving fastening means, but the direction of extension of the slot-shaped recesses corresponds to the direction of distance change in order to achieve a maximum change in distance. However, such a solution is not suitable for a pipeline support with, in particular, vertically running bearing parts, since the force exerted by the pipeline runs in the same direction as the extension of the slot-shaped recesses. As a result, the fastening means are not only responsible for locking the two bearing parts together, but also for absorbing and transmitting the entire weight force exerted by the pipeline. The fastening means cannot usually provide such a large contact force.

The essential innovation of the present invention is that the recesses deviate from the

Distance change direction, for example perpendicular to this, but in particular at an angle, whereby a large part of the weight force corresponding to the recess inclination is absorbed by the recess webs. In order to ensure that the distance changeability of the holder is maintained, the recesses of the two bearing parts are designed with a different inclination and cross over each other in order to always obtain a fixing position for the fastening means in the distance change area. The recesses are inclined in opposite directions to each other in relation to the distance change direction in order to obtain a larger feed area, which is then twice as large as the extension of a recess in the distance change direction.

The advantages of the present invention are particularly evident when the adjacent sections of the bearing parts and the recesses run in a vertical plane, so that the effective weight forces can be transferred largely from the upper part of the bearing via the fastening means and the recess edges to the lower part of the bearing through the direct vertical contact. Accordingly, the direction of change in distance also runs vertically, so that the recesses are arranged obliquely in a direction deviating from the vertical.

It is particularly advantageous if two recesses arranged next to each other relative to the direction of the distance change are provided for two separate

rate fastening means and if the adjacent recesses of each bearing part are mirror images of each other relative to the central axis extending between them. In this way, a force balance can be achieved, whereby a force effect deviating from the direction of the change in distance, for example a tipping force, can be prevented.

In particular, if the slot-shaped recesses have to be very flat due to the large weight force to be absorbed, it is recommended to provide at least two recesses in one bearing part, one behind the other in the direction of the change in distance, which have the same inclination. This means that the fastening means can be removed from the first recess when the bracket is adjusted and can be inserted back into the second recess after the upper bearing part has been moved accordingly relative to the lower bearing part. This means that the variable distance can be doubled. If the two slots in a bearing part arranged one behind the other are arranged in such a way that the first slot ends where the second slot begins in terms of its extension in the direction of the change in distance, a continuous change in distance can be achieved despite the two different recesses.

For a stepless distance adjustment, it is also advantageous if the recesses have smooth peripheral sides so that the fastening element can be moved without hindrance within the recess when the fastening is released.

For a grid-like distance adjustment, the peripheral sides of the recesses can also be profiled, for example knurled. In this case, it is particularly recommended that the recess of the lower part of the bearing has at least one profiled peripheral longitudinal side and the recess of the upper part of the bearing has at least one profiled peripheral longitudinal side that is essentially opposite this. These profiled peripheral longitudinal sides are expediently located on the side of the recesses that is loaded by the acting weight force, whereby the fastening means can be adjusted by lifting it off the profile along the smooth-walled peripheral longitudinal side, while under load the fastening means is pressed against the profile and thus receives additional positional fixation within the recess due to the profile.

Such a profiling of the circumferential longitudinal sides can be designed in a stepped manner, in particular, whereby the shape of the part of the fastening means located within the recesses is expediently adapted to this stepped profiling. This creates a positive connection within the recess between the bearing parts and the fastening means, which further increases the introduction of force into the loaded lower part of the bearing.

A particularly simple embodiment is, for example, if the recesses are each inclined by 45° relative to the direction of the change in distance with correspondingly inclined smooth-walled peripheral sides

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and if the shape of the fastening means within the recesses is square and adapted to this.

To increase the holding force, the fastening means can expediently consist of a screw-nut connection, which can have conical sections with a diameter decreasing in the direction of the recess, whereby the largest diameter of the conical sections should be larger and the smallest diameter smaller than the cross-section of the recess.

Various variants are possible for the design of the holder itself, in which the advantages of the invention can be realized. For example, the lower bearing part can have a U-shaped cross-section perpendicular to the direction of the change in distance and can guide the upper bearing part arranged within the U-profile laterally by means of the two U-legs. In addition, the lower and upper bearing parts can each have two sections extending in the direction of the change in distance, which are opposite one another and run parallel to one another, resulting in a pairing of corresponding sections, each consisting of a bearing upper part section and a bearing lower part section.

Further features and advantages of the present invention will become apparent from the following description of embodiments based on the drawings, in which:

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Figure 1 shows a distance-adjustable holder for pipelines according to the invention in a perspective side view;

Figure 2 shows an alternative application of a holder according to the invention in two different height positions in front view;

Figure 3 shows the bracket from Figure 2 in the lower position, partially shown in side view;

Figure 4 shows the bracket from Figure 2 in the higher position, partially shown in side view;

Figure 5 shows an embodiment for the construction of the lower and upper bearing parts in a perspective side view;

Figure 6 shows the embodiment from Figure 5 in plan view;

Figure 7 is a schematic representation of a height-adjustable bracket with a special design of the lower and upper bearing sections;

Figure 8 shows an alternative embodiment to Figure 7;

Figure 9 is a schematic representation of a suitable slot-fastener arrangement;

Figure 10 is another schematic representation of an alternative slot-fastening center arrangement;

Figure 11 shows the fastening means from Figure 10 in a separate representation;

Figure 12 shows a preferred design of a recess for the bearing base;

Figure 13 shows a preferred design of a recess for the upper bearing part;

Figure 14 the interaction of the two bearing parts from

Figures 12 and 13 with a fastening device during an adjustment process in the unloaded state;

Figure 15 shows the interaction according to Figure 14 in the loaded fixing state;

Figure 16 shows an embodiment of a suitable fastening means in a partially sectioned side view;

Figure 17 shows an alternative embodiment of a fastening means;

Figure 18 shows a further embodiment of a fastening means; and

Figure 19 shows another embodiment of a recess for the lower or upper part of the bearing.

Figure 1 shows a distance-adjustable holder according to the invention in the form of a height-adjustable pipeline bearing 1, which has a stationary bearing lower part 2 and a bearing upper part 3 that can be adjusted in height relative to it. The bearing lower part 2 comprises a horizontally extending base web 4 and a vertical profile web 5 that runs vertically upwards relative to it with a U-shaped horizontal cross-section, which enables the bearing upper part to be guided laterally and secured against tipping and consists of two legs 6 that are parallel to one another and a vertical base 7 that connects the two legs. Two slot-shaped recesses 8 and 9 are provided in this base, which are partially covered by the bearing upper part 3 in Figure 1 and are therefore mostly shown in dashed lines. The two slots 8 and are oriented approximately in a V shape, i.e. they are

each inclined by approximately 45° from the vertical and enclose an angle of approximately 90° between them. In addition, both recesses are arranged at the same vertical height, which ensures symmetrical load transfer to the bearing base 2.

The upper part of the bearing 3 consists essentially of a vertical web 10, which is surrounded on three of its circumferential sides by the U-shaped vertical profile web 5. On the upper side of the vertical web 10, two pipe clamp lower halves 11 and 12 are arranged, which serve to accommodate a pipeline (not shown in Figure 1) and to secure it to the bearing 1.

The upper bearing part 3 also has slot-shaped recesses 13 and 14 provided in its vertical web 10, which are also arranged at an angle of 45° from the vertical, but not in a V shape, but with an opposite orientation, i.e. tapering upwards. This ensures that when the height of the upper bearing part 3 is adjusted relative to the lower bearing part 2 along the direction of distance change indicated in Figure 1 with an arrow 15, the recesses 8 and 9 of the lower bearing part 2 and the recesses 13 and 14 of the upper bearing part 3 each cross over at a point along an adjustment range corresponding to the vertical extension of both recesses 8 and 12 or 14.

This crossing point serves to accommodate a fastening means 16, which in Figure 1 is shown in the form of a

Screw-nut connection and shown in an exploded view. On the one hand, the fastening means secures the two bearing parts 2 and 3 to one another, but on the other hand serves in particular to transfer the bearing forces from the upper bearing part to the lower bearing part directly, not only via the contact surfaces between the fastening means 16 and the two bearing parts, but in particular via the slot flanks of the recesses 8, 9, 13 and 14. The upper flank of the slots 13 and 14 of the upper bearing part 3 presses on the shaft of the fastening means 16, which in turn transfers the forces to the lower flanks of the recesses 8 and 9 of the lower bearing part.

The height of the bearing shown in Figure 1 is adjusted in a simple manner by slightly loosening the screw-nut connection, but not having to remove it completely from the recesses; the upper part of the bearing can then be raised or lowered, whereby the fastening means arranged in each pair of slots 8/13 or 9/14 are not only moved vertically due to the height adjustment of the upper part of the bearing, but also horizontally due to the inclination of the slots. The symmetrical arrangement of the slots to one another means that in every height position the fastening means are arranged at the same height or the same distance from the vertical center axis of the upper part of the bearing. This achieves a symmetrical force transmission, which can prevent the occurrence of, for example, tilting movements.

Figure 2 shows an alternative application of a height-adjustable bracket 21 for pipelines, which consists of a lower bearing part 22 and an upper bearing part 23. The lower bearing part 22 is - as indicated in Figures 3 and 4, which show side views of the bracket 21 from Figure - U-shaped with two vertical legs 24 arranged parallel to one another in Figure 2 and a horizontal base 25 connecting the two legs to one another.

The upper part of the bearing 23 is guided between the two vertical legs 24 and is designed in the form of a housing of a roller bearing. The housing 23 shown schematically in the figure consists, among other things, of two vertical supports 26 which run parallel to one another in accordance with the vertical legs 24 and each rest against the vertical legs 24 on their inside. Two bearing rollers 27 and 28 are connected to the vertical supports 26 in a manner not shown in detail, which track a schematically indicated pipe 29 on their vertical upper side.

The further structure, which is the same for the front vertical leg 24 and the rear vertical leg (not shown) as well as for the front vertical support 26 and the rear vertical support (not shown), will be explained below using only one pair of vertical supports/legs as an example: The vertical leg 24 of the lower bearing part has two obliquely running slots 30 and 31, which are arranged with their upper ends converging symmetrically to the bearing center axis 32 shown in dash-dotted lines.

In Figure 2, the central axis 32 also indicates a dividing line between two types of representation: the lowest adjustment position of the holder 21 is shown on the left half of Figure 2 and the highest adjustment position of the holder 21 is shown on the right half of the image. While the position of the lower bearing part 22 does not differ in the two halves of the image due to its positional stability, the upper bearing part 23 is arranged correspondingly lower in the left half of the image and correspondingly higher in the right half of the image.

Two slots 33 and 34 are also provided in the vertical support 26, which are symmetrically inclined from the vertical and arranged in a V-shape relative to one another. A fastening means 35 is provided in the slot pair 30/33 and a fastening means 36 is provided in the slot pair 31/34. The structure of the fastening means 35 and 36 is indicated in Figures 3 and 4: Accordingly, the fastening means consist of a screw-nut connection and a spacer sleeve which extends between the two vertical supports 26 and transmits the fastening force between the screw and nut.

From Figure 2, the different positions of the fastening means 3 5 and 3 6 can be seen depending on the height of the bracket; while the fastening means 35 is in the horizontally outermost position, i.e. the position furthest away from the central axis 32, in which it is positioned at the lowest point of the slot 3 0 of the lower bearing part and at the highest point of the slot 33 of the upper bearing part, which corresponds to the lowest possible bracket position, the fastening means

tel 36 is arranged horizontally in the innermost position and within the slots in the highest possible mounting position. The fact that the fastening means 35 or 36 extend on the left side and the slots extend to the right of them is due to the symmetrical arrangement of the slots to the central axis 32.

Figure 5 shows a design of a bracket 41 with a bearing base 42 and two bearing tops 43 and 44 arranged symmetrically thereto. The bearing base 42 is profiled in a U-shape in the vertical direction with two vertical legs 45 and 46 and a base 47 as well as a connecting web 48 which - as can be seen from Figure 6, the top view of the bracket 41 - extends between the two vertical legs 45 and 46 while resting on the base 47. The two vertical legs 45 and 46 and the connecting web 48 thus form a double U-profile in the horizontal cross section. Each ü serves to accommodate a bearing upper part 43 or 44, which is also profiled in the horizontal cross-section, with the ü outer sides of the bearing upper parts 43 or 44 resting on the U inner sides of the double U bearing lower part 45. Both the bearing upper part 43 and the bearing upper part 44 each have two inclined slots 49 and 50 in their ü base, which together with correspondingly inclined slots provided in the connecting web 48 (not shown in Figure 5) serve to accommodate fastening means (not shown). The bearing upper part is guided laterally by the lateral σ legs, which is particularly important when adjusting the height.

Figure 7 shows a schematic drawing of an alternative holder 51, in which the slot-shaped recesses of each component are not provided in the same vertical section, but in opposite sections that run parallel to one another. The holder 51 is composed of a U-shaped lower bearing part 52 and a U-shaped upper bearing part 53, whereby the upper bearing part 53 corresponds in structure to the lower bearing part 45 from Figure 5 and has a connecting web 54 between two U-legs 55 and 56 for stabilization. The upper bearing part 53 also has two U-legs 57 and 58, which rest with their outer sides on the inner sides of the U-legs 55 and 56 of the lower bearing part 52. All four U-legs have recesses designed in the manner indicated above to accommodate fastening means not shown and thus form two pairs of legs 55/57 and 56/58, which run parallel to each other and are opposite each other.

Figure 8 shows a holder 61 which corresponds in structure to the holder 51 from Figure 7 with the only difference that it has a bearing upper part 62 which consists only of two vertically running legs 63 and 64 and a vertically arranged connecting web 65 connecting the two legs, omitting the U-base which also connects the two legs.

Figure 9 shows the basic interaction of two recesses 71 and 72 with a fastening means 73. Both recesses run around

45° from the vertical in opposite directions to each other, whereby they form an angle of 90" between them. This results in the advantage that the fastening means can be provided in a simple manner with a sleeve 74 with a square circumferential cross-section, the circumferential surfaces of which correspond to the cross-section of the two recesses, whereby the sleeve rests on the long sides of the recess with relatively little play. In this way, the majority of the force to be transmitted from the upper part of the bearing to the lower part of the bearing can be transmitted through the sleeve and does not have to be passed on to the end faces of the bearing part with the help of the contact pressure of the fastening means.

An even better force transmission is provided by the embodiment according to Figure 10, in which both slot-shaped recesses 81 and 82 have stepped circumferential longitudinal sides, which are composed of only vertical and horizontal sections. The horizontal sections are here as long as the fastening means 73 from Figure 9 to be inserted into the recesses or the square sleeve 74 surrounding the fastening means. This fastening means 73 is shown again separately in Figure 11. By specially adapting the shape of the recess to the shape of the sleeve, the sleeve 74 can be anchored in a form-fitting manner in each recess 81 or 82, whereby the full weight force can be transferred from the upper part of the bearing to the lower part of the bearing. As a result, the fastening means itself only has to ensure that the

The two bearing parts that are in contact with one another do not move away from one another and the sleeve 74 of the fastening means 73 is not accidentally pressed out of the recesses. Accordingly, the force to be absorbed by the fastening means 73 is relatively low.

Another advantageous design option for slot-shaped recesses is shown in Figures 12 to 15: Figure 12 shows a bearing base 91 with a recess 92, the lower circumferential side of which is roughly profiled, while the upper side is designed with smooth walls. The bearing upper side 93 shown in Figure 13 has a recess 94, the circumferential sides of which are designed in reverse, that is, the upper circumferential side is roughly profiled and the lower side is designed with smooth walls. This results in the two recesses interacting with a fastening means 95, as shown in Figures 14 and 15: When the height of the holder is adjusted, the upper circumferential longitudinal side of the lower bearing part 91 and the lower circumferential longitudinal side of the upper bearing part 93, both of which are designed with smooth walls, are acted upon by the fastening means 95. This means that during the height adjustment, the fastening means is adjusted along the smooth-walled circumferential longitudinal sides without any major resistance being opposed to this adjustment movement. In contrast, when the holder is loaded, the upper bearing part 93 presses with its upper circumferential longitudinal side via the fastening means 95 against the lower circumferential longitudinal side of the lower bearing part 91. In this case, the two profiled circumferential longitudinal sides are therefore acted upon by the fastening means

applied, whereby the force transmission within the holder is promoted with the help of the profiling. If the profiling is adapted to the outer contour of the fastening means 95, similar effects can be achieved as in the embodiment in Figure 10, i.e. the fastening means can transmit the effective bearing forces due to the form fit, without greater contact forces being required.

Figures 16 to 18 show further embodiments of fastening means which aim to increase the holding force of the fastening means. Figure 16 shows a fastening means 101 which extends through recesses 102 and 103, respectively, which are provided in two adjacent bearing parts 104 and 105, respectively. The fastening means 101 consists of a screw 106, the screw head of which is conical with a diameter that decreases in the direction of the adjacent recess 102. The screw 106 is tightened with a screw nut 107 arranged on the opposite side of the bearing parts, which is also conical with a diameter that decreases in the direction of the adjacent recess 103. Both conical sections have in common that the larger outer diameter is larger and the smaller outer diameter is smaller than the recess cross-section. As a result, when screwing the fastening means 101, the contact pressure between the screw head and the bearing part 104 or between the screw nut 107 and the bearing part 105 is increased, which leads to an increase in the holding force and also the transferable weight force

leads.

In Figure 17, it is proposed that instead of providing conical sections on the screw head or on the screw nut, conical sleeves 111 or 112 be pushed onto the screw shaft of a fastening means 110 in order to achieve the same effects as in the embodiment from Figure 16.

This also corresponds to the embodiment of a fastening means 120 according to Figure 18 with the only exception that instead of a screw and a nut, a threaded pin 121 and two nuts 122 and 123 that can be screwed onto it are provided. As in the embodiment according to Figure 17, two conical slip-on sleeves 124 and 125 are also provided here in order to increase the holding force.

Finally, the embodiments of Figures 16 to 18 also have in common that the screw or the threaded pin within the recesses are adapted in their cross-section to the cross-section of the recesses by means of separate sleeves or other diameter enlargements in order to ensure a force transmission from the upper part of the bearing to the lower part of the bearing and at the same time to prevent too much play in the fastening means within the recess and thus prevent it from tipping over.

Figure 19 finally shows another possibility of designing a recess 130, namely to provide it with a scale on one of its long sides,

which indicates the height position of the bracket.

In summary, the advantage of the invention is that with a greatly simplified mounting structure, which can, for example, only consist of individual sheet metal parts, a reliable height adjustment and fixing of the adjacent bearing parts to one another can be achieved, whereby the assembly effort is also greatly reduced.

Claims (16)

Protection claims 1. Distance-adjustable holder for the particularly height-adjustable storage of a pipeline, whereby the holder consists of a stationary lower bearing part and a distance-adjustable upper bearing part, which at least indirectly supports the pipeline, characterized in that that the bearing lower part (2, 22, 42, 52, 91) and upper part (3, 23, 43, 44, 53, 62, 93) have mutually overlapping and at least partially abutting sections (7, 10, 24, 26, 48, 55-58, 63, 64), that in each of these sections at least one slot-shaped recess (8, 9, 13, 14, 30, 31, 33, 34, 49, 50, 92, 94) is provided for receiving a fastening means (16, 35, 95) that fixes the two bearing parts to one another, and that the recesses run in a direction that differs from the direction of change in distance (15) and are arranged to cross one another. 2. Distance-adjustable holder according to claim 1, characterized in that that the recesses are arranged in a direction that runs obliquely with respect to the direction of change in distance (15). -L-U 3. Distance-adjustable holder according to claim 1, characterized in that that the recesses (8, 9, 13, 14, 30, 31, 33, 34, 49, 50, 92, 94) have an opposite inclination relative to one another in relation to the direction of change in distance (15). 4. Distance-adjustable holder according to claim 1, characterized in that the adjacent sections (7, 10, 24, 26, 48, 55-58, 63, 64) and the recesses (8, 9, 13, 14, 30, 31, 33, 34, 49, 50, 92, 94) run in a vertical plane. 5. Distance-adjustable holder according to claim 1, characterized in that that the distance change direction (15) is vertical. 6. Distance-adjustable holder according to claim 1, characterized in that that two recesses (8, 9, 13, 14, 30, 31, 33, 34, 49, 50) are provided for two separate fastening means (16, 35) per bearing part (2, 3, 22, 23, 42, 43, 44, 52, 53, 62), that the recesses of a bearing part are arranged next to one another in relation to the direction of change in distance (15) and that the adjacent recesses of each bearing part are mirror-inverted relative to the central axis extending between them. 7. Distance-adjustable holder according to claim 1, characterized in that at least in one bearing part there are provided at least two recesses arranged one behind the other with respect to the distance change direction (15), which have the same inclination as one another. 8. Distance-adjustable holder according to claim 1, characterized in that the recesses (B, 9, 13, 14, 30, 31, 33, 34, 49, 50, 71, 72) have smooth circumferential sides for a continuous change in distance. 9. Distance-adjustable holder according to claim 1, characterized in that, for a grid-like distance change, the recess (92) of the lower bearing part (91) has at least one profiled circumferential longitudinal side and the recess (94) of the upper bearing part (93) has at least one profiled circumferential longitudinal side substantially opposite thereto. 10. Distance-adjustable holder according to claim 9, characterized in that the profiled circumferential longitudinal sides of each component (91, 93) are arranged on the side of the recesses loaded by the respective acting weight force. 11. Distance-adjustable holder according to claim 9, characterized in that the profiling of the circumferential longitudinal sides of the recesses (51, 82) is designed in a stepped manner and that IH-UO the shape of the part (74) of the fastening means (73) located within the recesses is adapted to the step-shaped profiling. 12. Distance-adjustable holder according to claim 1, characterized in that that the fastening means (16, 35, 36, 73, 95, 101, 110, 120) consist of a screw-nut connection. 13. Distance-adjustable holder according to claim 12, characterized in that that the screw-nut connection (101, 110, 120) has conical sections (111, 112, 124, 125) with a diameter decreasing in the direction of the recess (102, 103) in order to increase the holding force, the largest diameter of the conical sections being larger and the smallest diameter being smaller than the recess cross-section. 14. Distance-adjustable holder according to claim 1, characterized in that that the recesses (71, 72) are each inclined by 45° relative to the direction of the change in distance with correspondingly inclined smooth-walled peripheral sides and that the shape of the fastening means (73, 74) within the recesses is square and adapted to this. 15. Distance-adjustable holder according to claim 1, characterized in that that the bearing base (2, 42) is perpendicular to the distance change direction (15) has a U-shaped cross section and guides the bearing upper part (3, 43, 44) arranged within the U-profile laterally by means of the two U-legs (6, 45/ 46). 16. Distance-adjustable holder according to claim 1, characterized in that that the bearing lower part (52) and upper part (53, 62) each have two sections (55, 56, 57, 58, 63, 64) extending in the direction of the distance change direction (15), which are opposite one another and run parallel to one another.