EP2601422A2

EP2601422A2 - Assembly for sealing a rotational connection

Info

Publication number: EP2601422A2
Application number: EP11739104.5A
Authority: EP
Inventors: Hermann Willaczek
Original assignee: IMO Holding GmbH
Current assignee: IMO Holding GmbH
Priority date: 2010-08-05
Filing date: 2011-08-05
Publication date: 2013-06-12
Also published as: WO2012017094A3; RU2013109312A; US20130234403A1; WO2012017094A2; JP2013533444A; DE102010034033A1; CN103154544A

Abstract

The invention relates to an assembly for sealing a rotational connection, comprising at least one first annular main part (2) and at least one second annular main part (3), which are arranged concentrically about a common axis, and wherein at least one annular main part is rotatably arranged relative to at least one other annular main part, and wherein at least one circumferential gap (18) is provided between the at least one first annular main part (2) and the at least one second annular main part (3); wherein the first annular main part (2) comprises at least one convex profile curvature (8) projecting in the direction of the second annular main part (3), and wherein the second annular main part (3) comprises at least one convex profile curvature (9) projecting in the direction of the first annular main part (2); at least one sealing element (4), which is received in the circumferential gap (18) and which is sealingly seated against the first annular main part (2) and the second annular main part (3); wherein the sealing element (4) comprises at least four sealing lips (21), which are arranged in respective pairs, and wherein a respective pair of sealing lips (21) is associated with a respective convex profile curvature (21) such that in each case two sealing lips (21) enclose a convex profile curvature (21) and are sealingly seated thereon; wherein the sealing element (4) has axial symmetry with respect to at least one axis of symmetry (6), and wherein the at least one axis of symmetry is inclined relative to a vertical axis (13); and wherein the convex profile curvatures (8), (9) have points that project farthest in the direction of the sealing element (4), and wherein said points are essentially located on an axis (12) perpendicular to the axis of symmetry (6).

Description

DEVICE FOR SEALING A TURN CONNECTION The present invention relates to an arrangement for sealing a rotary joint.

Currently commercially available and in-use seals for slewing and slewing drives are very different in their shape and design, although the application is often very similar. It is always about the rotary joint or the swivel drive safe against external influences, such as moisture, sand or dirt or dirt, foreign objects, et cetera to protect.

Likewise, a practicable sealing arrangement is concerned with ensuring resistance to the internal lubricant pressure in the bearing. In principle, the seal should meet the requirements to prevent foreign objects from entering the bearing structure of the connection. At the same time, the seal must provide support that the lubricant remains in the bearing or only comes from the overall arrangement in small and defined quantities. So it must be able to withstand the internal pressure of the bearing, caused by the lubricant, to a reasonable extent. The expert speaks of a sealing effect of the seal.

It is currently state of the art that lubricants or lubricants are used in rotary joints and slewing drives, which come into contact with the sealing material.

It is also state of the art that commercially available and in use seals are vulcanizable and can be produced with all common methods for producing seal geometries from elastic see rubbery materials, such as FPM, Viton, NBR, ECO, HNBR and the like.

The common sealing arrangements according to the state of the art have in common that they are usually designed either in one or more parts, that is to say they consist of at least one sealing component. Very often, various annular sealing strands are inserted into the rotary joint or fastened in one or more recesses or grooves in the bulk material of the swivel joint or on the swivel drive, so that a fixation takes place. Fixing is done by inserting the elastic sealing material into a groove in the (metallic) solid material of the arrangement to be sealed. Frequently, this groove is produced by machining as a result of the so-called "puncturing rehearsing" during the production of the rotary joint or the swivel drive.

It is currently seen frequently and it is possible that several such grooves or punctures are present in the overall arrangement to be sealed off. As a rule, at least as many of these grooves exist as elastic sealing strands and the arrangement should be introduced and fixed.

The fixation of the sealing strips or of the sealing profiles in said grooves or egg nstichen happens in the normal case on the one hand by positive engagement, since the elastic springs or lips of the sealing strand or sealing profile, which are introduced into the grooves, often barb similar Profi lgeomet- rie (n) and, on the other hand, that possibly occurring deformation forces on the seals as a result of the customary operation of the rotary connection or the swivel drive are always approximately perpendicular to the axis of rotation of the aforementioned groove and thus not in the direction in which the profile geometry (FIG. n) of the Dichtungsri nges would be pulled out of said groove or said groove. It is also the case that the said fixation of the sealing arrangement in the metallic solid material can usually be released again by the application of force. This means by applying a certain tensile force, which opposite to the direction of the insertion force of the seal must act in the Vollmateri- al, the practitioner or specialist can solve the introduced seal of the metallic arrangement (rotary joint or swivel drive) again.

It is often according to the known prior art and significantly due to the fact described so that the sealing profiles used are barb similar designed due to the previously described profile geometry (s) and are generally characterized by strongly bent profiles. Despite the resulting problems in manufacturing and assembly, the sealing effect is usually respectably good, so that the expert currently preferred such solutions.

However, according to the known state of the art, it is never the case that such sealing profiles, which are introduced with the aid of their profile geometry (s) into existing grooves or recesses of the solid material, are completely symmetrical in both spatial axes of their own, ie in two-surface direction are.

However, according to known prior art, it is always the case that each seal is fixed at least at one point by the previously mentioned type of fixation in the solid material of the rotary joint or the swivel drive in order not to get out of the fixed position during the intended use. Despite the resulting problems in production and assembly, the resulting sealing effect is generally respectably good, so that the person skilled in the art currently chooses such fixation solutions.

It is currently seen frequently and it is possible that an elastic part of the described profile geometry (s) of the seal assembly on which a rotating part of a rotary joint is fixed, and another part of the same sealing arrangement is fixed to the other rotating part of a rotary joint, and that the sealing effect is achieved by the interaction of all the sealing components involved in the overall arrangement (for example a first elastic seal, an additional stainless steel band, an additional tension spring band and a second elastic seal, possibly third elastic sealing components) is caused. For example, EP 1 920 176 B1, based on DE 10 2005 041720 A1, describes such a successful arrangement for sealing a rotating connection, in which the sealing arrangement consists of approximately more than four individual components, each of which extends annularly and in which the sealing ring is fixed to one of the rotating parts in the above-mentioned manner.

The DE 103 093 83 AI, however, describes, inter alia, a seal assembly for a pivot bearing, which achieves a good sealing effect due to their strong asymmetric geometry in conjunction with an additional ring element made of a different material. Again, the strong asymmetric geometry of the sealing profile is fixed to one of the rotating parts in the above-mentioned manner.

The DE 10 2006 053832 Al deals with the use of an arrangement for sealing two mutually rotatable parts, which uses a spring or a Zugfederband as an additional component, and in which the sealing ring is fixed to one of the rotating parts in the above-mentioned manner. The European inventions EP 1 544 485 AI and EP 1 544 486 AI treated seals for bearings, in particular for sealingly closing a gap in a similar sense of the present invention, but in this case an additional so-called intermediate ring is used, which is in contact with a plurality of seals and these geo- Metric or physical separates. Likewise, in this case can not be sealed directly against each other rotatable parts, but it is necessary described in the invention intermediate ring for sealing effect according to the invention.

Furthermore, the documents WO 2010/043248 AI and WO 2010/043574 AI are known, which disclose a seal for a rolling bearing, wherein a seal has a substantially H-shaped cross section and is disposed between an inner ring and an outer ring of a rolling bearing.

In the end, even the German applications handle

DE 10 2008 025725 A1 and DE 10 2008 027890 A1. Sealing systems which, as mentioned above, incorporate several features of the known state of the art. Here, too, the respectively strongly asymmetrical geometries of the sealing profiles are fixed to at least one rotating part at least at one of the rotating parts in the above-mentioned manner.

From the perspective of the person skilled in the art or practitioner, precisely such seals would be the most optimal, which have simple and thus not strongly distorted profile geometry (s), so that the sealing arrangement or the element for sealing can be introduced into the sealed arrangement as confusion-proof as possible. In particular, profile geometry (s) that are symmetrical in their horizontal as well as in their lateral extent are optimal, because then it does not matter to the practitioner whether the seal is installed "laterally reversed" in the overall arrangement to be sealed.

Above all, profile geometry (s) of such sealing arrangements or elements are desired which can be introduced directly between the two rotating parts, which means that both directly rotating parts have physical contact with the most optimal sealing arrangement or element. All other state-of-the-art solutions have partially complex and multi-part designs. ments, which increase the assembly effort due to the multi-part or complexity. Increased assembly costs in practice costs time and money and is therefore disadvantageous. A disadvantage is in practice as well that complex and angular Prof i I- geometry (s) of the seals are filigree configured as simple and not strongly bent profile geometry (s) and thus in the application are more sensitive to environmental influences and thus premature to defect and thus Failure of the custom operation of the rotary joint or the swivel drive can lead. Also, such mentioned possibly occurring premature defects cost in practice time and money and this is therefore disadvantageous.

Above all, it is in the current state of the art a constant nuisance that for introducing the seal for direct sealing of two rotating parts, such as a rotary joint or swivel drive, the aforementioned groove or the aforementioned recess in the solid material of the overall arrangement (rotary connection or swivel drive ) must be present. In order to introduce this groove, additional production measures are necessary in the case of the generally chip-producing production of the assembly to be sealed. Again, this costs time and money in practice and is therefore disadvantageous.

From the perspective of the skilled person or practitioner, it is also important that in the case of maintenance or repair work on the rotary connection located in the field or in the field swivel drive this optimal seal or seal assembly or the element with reduced expenditure of time compared to today in the Market existing sealing arrangements of the prior art can be performed. This would save time and money in the maintenance / repair practice, because longer times for maintenance / repair tasks cost money in practice and are therefore also disadvantageous. All the aforementioned examples for the creation of sealing arrangements for sealing two mutually rotatable parts are used to cover the prior art and the disadvantages associated with the current state of the art. It is common to these examples that, as already explained in detail, they consist either of several components, of which at least some of the components are fixed to at least one of the mutually rotatable parts, and thus have no symmetrical or simple profile geometry (s) which enhances installation safety and service life could increase the seal in operation, or that, in the case of simple geometries, they do not allow direct sealing of the outer and inner rotating parts, which the skilled person or practitioner may desire.

Considering these disadvantages, it is necessary to create the best possible sealing arrangement or an element for sealing two directly mutually rotatable parts, which is designed simpler in terms of its profile geometry (s) than the systems previously prevailing in the market, and by whose simpler design selbige no longer needs to be attached or fixed separately to one or both of the rotatable parts of the rotary joint or the pivot drive, thus facilitating the assembly or replacement and can be made or manufactured easier or with less effort. Furthermore, it is the manufacturing or manufacturing process for the production of seals for mechanical and plant engineering to be chosen so that it corresponds to the current state of the art and no separate manufacturing process or process steps are needed.

In order to reduce all of the mentioned disadvantages, the present invention offers particular advantages and features. The problems of the mentioned disadvantages are solved by the features listed in claim 1. The solution to the detrimental problems according to the conventional art succeeds in particular when the seal assembly according to the invention or the element for sealing the device to be sealed has such a geometry that selbiges both during operation of the rotary joint, as well as in phases always and without involvement other components integrated in place can remain integrated in the overall structure, ie without falling out. As a primary task, it is always important to seal the sealed opening, by the inventive arrangement.

In particular, by an advantageous design of the so-called retaining tabs of the seal assembly, this can be achieved. In particular, these retaining tabs are parallel and annular to the rotary joint encircling integral components of the seal assembly, which are always applied laterally directly to the rotating main parts of the rotary joint. It can cause low friction during operation of the rotary connection, which is kept minimal by correspondingly conventional lubrication. These retaining tabs exist, as stated, on each side of the rotary joint. These retaining tabs are in the conventional sense sealing lips, which are guided along the twisting parts or rest to seal the construction. The symmetrical shape brings good manufacturing properties and ensures very good dimensional stability of the seal assembly according to the invention. About exactly these retaining tabs of the physical contact of the seal assembly is made with the respective rotatable body. It is precisely these retaining tabs that can also deform a maximum during operation when radial forces and tolerances occur that can cause the two respective rotatable main parts of the rotary joint to move towards or away from each other. The mechanism just described always provides for a type of self-centering of the seal assembly or element so that the same is never removed from the overall construction either automatically or due to the rotational movement. Due to the geometric design of the seal assembly or the element just mentioned movement and the so-called bearing clearance can be added. Then, the retaining tabs of the seal assembly deform, this deformation is reversible due to the elastic properties of the sealing material. One advantage of this is that the seal always deforms on both sides and thus will not be so heavily loaded on one side as the asymmetrical profile geometry (s) currently available on the market. An increased pressure resistance compared to the systems currently available on the market according to the current state of the art is given.

In addition, when a large bearing clearance or a large sudden out-of-round occurs during the rotationally directed movement, a rotation, as a result of rotatable (main) parts of the rotary joint moving toward or away from each other, the mutual clearances between the ( highest) profile bulge of the rotatable (main) parts and the seal arrangement changed.

These free spaces are usually partially wetted with lubricant and are located to the right and left of the line of symmetry, which has the seal assembly or the element. By possibly occurring in operation succession to each other or Voneinanderfortbewegungen of the two mutually rotatable parts, the seal may compress due to the elastic material own shafts (contraction) or relieve (relaxation).

Equally meaningful in the sense of the teaching of the invention is that the seal arrangement or the element can have the maximum self-centering mechanisms, especially if the angle of the at least one symmetry axis is not too large and not too small. In practice, an angle of about 30 ° has proven to be very good. Similar angles are conceivable, but the angle should not exceed the perpendicular to the absolute vertical, ie 90 °. The invention has proven particularly useful if the geometry of the sealing arrangement at least always has at least one symmetry in one of its two central surface directions. Then it can easily be mounted laterally reversed and less expensive tools are required during assembly. The same applies to the inventive elimination of the previously existing state of the art always present Fixierippel. These in the form of lips or barb-shaped faucets emerge like a lobes as part of the profile geometry (s) of the seals currently in the market from the sealing profile and must according to the latest state of the art in the context of assembly always separately in the grooves or recesses provided in the Rotary connection introduced (fixed).

This need no longer exists with the profile geometry according to the invention due to the no longer existing need for separate fixation on at least one of the rotatable parts of the rotary joint or the pivot drive. Due to the, in contrast to the current state of the art simplified arrangement without the use of fine or filigree sealing lips, the system can be used as an inner seal, as well as an outer seal for slewing or slewing drives. This means, in particular, that the sealing effect of the sealing arrangement according to the invention seals both inwardly and outwardly. It is also preferred that, when assembling seals to be repaired in the field components, the seal assembly according to the invention can be removed much more time-optimized or reinserted. In particular, the elastic sealing material or the sealing material does not have to be drawn, nor should it be upset and also not be pressed in. The mounting safety is thereby considerably increased with regard to the current sealing systems according to the known state of the art. Furthermore, another advantage is that the assembled seal assembly can relax again after mounting the entire circumference. The fact that the entire sealing arrangement is always self-centering, saves time in the production when it comes to the fact that the seal in the solid material (usually steel) of the rotary joint or the pivot drive must be introduced. The previously necessary grooves or recesses are no longer needed. This regularly leads to decreasing necessary times for the production. The geometry, in particular the simplicity of the geometry according to the invention makes it possible that, in addition, fewer components have to be used in the repair in the field as well as in the new installation. Assembly time is reduced and fault possibilities are minimized by fewer parts to be installed, which are also easier to handle by a specialist.

By designing the entire sealing arrangement such that the same does not project beyond the planar surface in the horizontal extent, which is spanned in space by the outermost upper edge of all rotating parts of the overall construction, the new sealing arrangement or element according to the invention obstructs the subsequent one Connecting construction, which is usually only in the field and at m customer a is brought, never.

If any use of the teaching according to the invention as a composite system, the gist of simplicity under the pretense yet, as well as heretofore, kei ne grooves or recesses for fixing in the rotary joint or the pivot drive are needed. Any additional components to be used, such as, for example, a steel strip or a spring-loaded strip or a combination of the two, are fixed in the connection similar to the previous and cited prior art. The g roße difference from the prior art is that the bearing seal assemblies, which steel tape and / or spring tension tape record, not sel bst must be fixed separately in the rotatable parts must, as previously explained in detail. Further advantages can provide the sealing arrangement according to the invention or the element for sealing in that the selected contours are made as round as possible and thus little angled to give the solution a special simplicity and robustness. While the previous solutions as explained above and cited occasionally strongly bent and rather filigree and thus often mechanical load cases of buckling or bending or bending or any other combination of the load cases mentioned results, so the new and inventive construction and geometric Ausges - Design of the seal assembly or the element essentially, as also explained, claimed to elongation and compression. Exactly those two load cases are those which can be taken up very well from rubber-like elastic materials from a material point of view, without fear of appreciable damage, which in turn has a positive effect on the service life and durability of the solution according to the invention.

It has proved to be advantageous that these "roundings" do not promote the load situation of the notch effect.This notch effect likewise frequently occurs in strongly crooked constructions and is undesirable.

Corresponding to the preferred cross section, the assembly and disassembly of the sealing solution according to the invention is much simpler and less complex than the currently valid solutions of the prior art.

In a further embodiment of the invention, sealing lips assigned to the first annular main part, in particular adjacent to a free space, have a coefficient of friction and / or a coefficient of friction which is different from the coefficient of friction and / or the coefficient of friction of the sealing lips associated with the second annular main part. or that the sealing lips associated contact surfaces of the first annular main part a coefficient of friction and / or have a coefficient of friction which is different from the coefficient of friction and / or the coefficient of friction of the sealing lips associated contact surfaces of the second annular main part.

The sealing profile can be coated or greased on only one side prior to insertion into a rotary joint, so that the sealing profile is coated or greased on only one side and is thus quasi-fixed in operation on the one main part and on the other main part a good lubricity having.

Further features, characteristics, advantages and effects on the basis of the invention will become apparent from the following descriptions of a preferred embodiment of the invention, as well as further advantageous embodiments of the invention, and with reference to the drawings. Hereby show:

1 shows a first consideration of the sectional geometry of a one-piece embodiment of this seal arrangement or of the element (4) when looking at the end section of a cut segment; It is a section through a rotary joint (1), which can use as rolling elements balls or rollers or sliding components, or a hybrid form of all this. Fig. 2 shows another embodiment of this sectional geometry of this one-piece design of this seal assembly or element (4), wherein the contours of the seal are slightly different in contrast to Fig. 1. Fig. 3 is a further consideration of the cut geometry of a one-piece design of this seal assembly or Elements in view of the cross-sectional area cut a segment; This is a section through a swivel drive, which for the purpose of rotational adjustment of the outer ring of a rotary joint to a Rotary connection with balls as rolling elements. In this Fig. 3 for comparison purposes, an exemplary conventional sealing element (22) can be seen, which is fixed in one of the aforementioned conventional groove or recess (23) according to the prior art by means of fixing nipple.

Fig. 4, however, shows no swivel drive, but shows the invention executed as a one-piece element, which was installed directly between the inner ring and outer ring of a rotary joint, without the seal assembly or the element needs to be fixed in a groove or in a groove. It is such that neither on the inner ring nor on the outer ring, such previous or conventional fixation is necessary.

It can be seen in all FIGS. 1 to 4 inclusive that the sealing arrangement or element (4), which is a sealing element, is neither fixed to one of the parts which rotate directly against one another, namely a first rotatable main part (3) the other of the directly against each other rotatable parts, a second rotatable main part (2). Depending on the design of the rotary joint or the swivel drive, the first or the second main part (2), (3) may also be stationary, for example arranged on a machine or plant bed. The sealing element (4) is arranged between the first rotatable main part (2) and the second rotatable main part (3) so that a relative movement between the sealing element (4) and the first and second rotatable main part (2, 3) is made possible. During operation of the rotary joint or swivel drive (1), relative movements therefore result in each case between the first and second rotatable main part (2, 3) and the sealing element (4). In practice, by the attached to a bearing or on a swivel drive connection structures that connect above the outermost upper edges of all rotating parts, significant deformations in the bearing up to the several millimeter range between inner ring, for example (2), and outer ring, for example ( 3). Egg- ner of the main advantages of the invention is that the deformations divide on both sides of the retaining tabs or on both sides of the lip pairs to about similarly large loads. This has, among other things, the advantage that virtually twice the deformation can be absorbed by the sides of the seal arrangement or element (4). The sealing element (4) has a symmetrical cross section, namely an axisymmetric cross section with an axis of symmetry (6) or line of symmetry, wherein the line of symmetry (6) passes through a seal center (7). At the same time, the cross section of the sealing element (4) also exhibits axial symmetry with a vertical (12) to the symmetry line. In the center of sealing, a vertical (12) intersects the line of symmetry and an absolute vertical (13). Furthermore, the sealing element (4) on four sealing lips (21) or retaining tabs, of which two in each case on the first rotatable main part (2) and two on the second rotatable main part (3), preferably flat, abut. Between the sealing lips (21) resting against the first rotatable main part, an upper free space (10) or else a recess is formed, which is provided between the profile bulge of the first rotatable main part and the sealing arrangement or the sealing element (4). Corresponding to the axial symmetry, a lower free space, or a recess, between the profile bulge of the first rotatable main part and the sealing arrangement or the sealing element (4) is also located between the two opposing sealing lips (21) resting on the second rotatable main part (3). intended. The first rotatable main part (2) has an upper rounded profile convexity (8) rounded off at the triangular point as a triangular point. Likewise, the second rotatable main part (3) has an upper rounded profile convexity (9) rounded off at the triangular point as a triangular tip. The profile bulges (8), (9) are arranged on the main parts (2), (3) in such a way that the points of the profile bulges (8), (9) protruding furthest in the direction of the sealing element (4) on the vertical (12) lie to the symmetry line. As a result, the profile bulges (8), (9) lie opposite each other during operation of the rotary joint or the swivel drive (1). over, whereby the passage to be sealed by the profile element (4) is limited.

Despite the possibility that the seal arrangement or the element deforms due to the rotationally directed actuation of the rotary joint or the swivel drive (1), it is, of course, the case that the nominal radius or the diameter of the seal arrangement, that is to say the distance, is meant here between the seal center point (7) and the circle center of rotation of the rotation (the pivot drive or the pivot connection) does not substantially change. This means that any changes in the radius or the diameter of the seal arrangement take place only by the elastic properties and / or by temperature effects and / or due to the radial and axial deformations in the bearing. For example, FIG. 2 shows a sealing element (4) with a cross-section which is changed relative to the sealing element (4) in FIG. The cross-section is formed in its contour around, wherein the free-spaces (10), (11) forming sealing lips are undercut, or in other words have a distance such that the free spaces have a nearly closed concave shape.

The elastic sealing material in all of the mentioned figures always consists of a rubber-like material, for example, which is vulcanizable and can be used together with all materials commonly used in mechanical engineering for the lubrication of rotary joints. In Fig. 3 is a section through a pivot drive is shown, which is equipped for the purpose of rotational adjustment of the outer ring with a rotary joint. The rotary joint wide rolling elements (14). A first main part (2) is arranged stationary, and is in operative connection with a second rotatable main part (3). The second rotatable main part (3) is connected by means of rolling elements (14) to a rotary joint, wherein by way of example a conventional sealing element (22) is shown, which is fixed in a groove or a recess (23) by means of fixing nipples. First main part (2) and second rotatable main part (3) are so to each other arranged that between the two main parts of an opening to be sealed (18) is provided, the maximum passage area is defined by the removal of the profile bulge (8) of the first main part and the profile bulge (9) of the second main part from each other. Between the two profile bulges (8), (9), the sealing element (4) is arranged so that the profile bulges (8), (9) are received in the respective associated free space (10), (11) or the respective associated recess. The drive of the swivel drive (1) is realized by means of a shaft (16) which comprises a sprocket (17), via which the second rotatable main part (3) can be moved in rotation. The lubrication of the swivel drive (1) via a grease nipple (15). The sealing element (4) seals the drive of the swivel drive from the environment. In Fig. 5 for the first time a multi-part version of the seal assembly according to the invention is shown, which consists of a plurality of sealing rings, which has one or more further sealing lips (25). It is noteworthy that the just mentioned further sealing lips (25) are not the same components as the above-mentioned retaining eyes (21), since they do not have the function of abutting the profile bulges of the directly rotating parts. Rather, they rest against other sealing lips (25).

In the case of the multi-part design, it may be so, based on the seal assembly according to the invention and on FIG. 5, that on at least one lip of a sealing ring on the circumference along running closed band (5) made of a different material can rest. The band may for example consist of stainless steel or of another metal material. Optionally, a Zugfederstrang (19) may also be inserted into the seal assembly to give the entire seal assembly additional stability in the radial direction. The sealing element (4) is constructed as follows. The sealing element (4) has four sealing lips (21) whose arrangement is based on the principle of symmetry already described. The sealing element (4) is in an opening to be sealed (18) arranged, in such a way that the profile bulge of the first main part (2) in a Freiram (10) and the profile bulge of the second main part (3) and a free space (11) are accommodated. The cross section of the profile of the sealing element (4) is in two parts and has on one of the profile bulge (8) of the first part facing profile part further, in particular four, sealing lips (25) which are in contact with the profile part, which the profile bulge (9). facing the second part. The two parts of the sealing element are inserted one after the other in an assembly process, whereby the closed band (5) and / or the tension spring strand can be preassembled on one of the parts of the sealing element (4).

In the following, the one-piece design is again considered: Here, the seal assembly or element (4) for sealing two directly against each other rotatable parts (3) (2) and designed as a circumferential ring consists of an elastic sealing material. In Fig. 4 one sees one of the essential features of the invention very well, namely that in the invention for local fixation of the sealing ring no positive connection or adhesion between the seal assembly and the directly mutually rotating parts is necessary, and thus no grooves or punctures. As a result of the symmetrical geometry of the sealing arrangement, which is also present, simple and torsion-proof assembly and quick exchangeability are ensured for the practice. Furthermore, it can be seen from the example of Fig. 4, where the end sectional area of a cut segment of this rotary joint or this pivot drive is considered that in at least one of the two surface directions, the seal assembly has a complete symmetry of itself. Furthermore, it is clearly visible that the symmetry line (6) is inclined in the direction of the vertical (13) by less than 90 ° to the vertical (13). In practice, has currently been particularly advantageous if the angle is about 30 °. It is always to be noted according to the invention that this angle is chosen as it seems the most meaningful of the adjacent construction, because it applies the following. The- that direction in which the two profile curvatures, which are meant to be encompassed or enclosed by the retaining tabs or sealing lips, move towards each other, usually by the geometric center (7) of the sealing element or the sealing arrangement. However, whether the direction of this movement actually points through the center (7), or whether this center (7) acts merely as a momentum pole of a rotational movement due to the relative movement of the two rotating parts (2) and (3), is highly dependent on the one used Bearing design and also highly dependent on the connection structures, which are connected to the left and right of the entire rotary joint.

This connection construction is usually connected by screws. It is also worth mentioning that in practice, depending heavily on the application of the rotary joint or the swivel drive, the deformations of the elastic sealing element (4) are not always based on one half on radially acting forces and the other half on axially acting forces. In fact, the forces acting on (4) can sometimes be predominantly axial and sometimes predominantly radial.

The actual distribution of forces depends on the bearing design and, accordingly, the angle at which the seal is inclined to the vertical is selected. In many cases, this angle is due to the bearing design and due to the male Radial- or axial forces about 30 °, but also all other angles between 0 ° and 90 ° are within the meaning of the invention, however, conceivable and useful.

Another embodiment and design feature of the invention can be seen very well in Fig. 1, in particular in Fig. 3. The invention provides that the seal assembly or that element (4) is designed and geometrically designed so that they are connected to the Never clamp or touch the rotary joint (or the slew drive) construction. It is nicely apparent from the figures that between the highest upper edge (20) of the outermost rotating parts, and the Upper edge of all underlying rotating parts always a remaining free gap or when spatially a non-remaining circular surface (24) remains. This situation can be found, for example, on both sides of a rotary joint. This freed geometry (s) ensures that the sealing element according to the invention or the sealing arrangement according to the invention does not drag against a possible connecting structure and additionally brake and thus be abraded.

Consider further, for example, Fig. 1. The following symmetrical considerations further explain very well what is important in the present invention: The seal arrangement or element has at least one line of symmetry (6) in the direction of the vertical (13) and an imaginary perpendicular (Fig. 12), wherein this perpendicular (12) intersects the line of symmetry from the vertical (13) in the seal center (7) and approximately in the direction of these perpendicular (12) each triangular and rounded at their triangle top profile bulges (9) of the two against mutually rotatable parts (3) (2) in the direction seal center (7) penetrate. During the intended operation of the rotary joint or the swivel drive (1), the seal arrangement or the element according to the invention can be significantly deformed. According to the invention, it is such that on both sides of the profile bulges (8) (9) between the sealing material and the respective profile bulge rounded free spaces ideally, for example, exactly round (10) (11) remain, which allow this penetration movement and at the respective ends tangentially clinging to the triangular profile bulges.

In all of the drawings set out below (FIGS. 1 to incl. FIG. 5), the principle of self-centering according to the invention is very clearly visible. Characterized in that the forces are absorbed either in the radial direction and / or in the axial direction of the invention device (4) and all these forces in approximately the direction of the sealant Point (7) act, the seal is automatically centered at each rotational movement of the rotary joint or the swivel drive (1).

Reference number list

1 rotary joint

2 first annular main part 3 second annular main part

4 sealing element

5 revolving closed band

6 symmetry axis

7 geometric center 8, 9 profile bulges

10, 11 free spaces

12 axis

13 vertical axis

14 rolling elements

15 grease nipples

16 wave

17 sprocket

18 gap

19 tension spring train

20 upper edge

21 sealing lips

22 sealing element

23 puncture

24 area

25 sealing lips

Claims

claims

An assembly for sealing a rotary joint comprising at least a first annular body (2) and at least a second annular body (3) concentrically disposed about a common axis and wherein at least one annular body is rotatably disposed relative to at least one other annular body and wherein at least one circumferential gap (18) is provided between the at least one first annular main part (2) and the at least one second annular main part (3);

the first annular main part (2) having at least one profile bulge (8) which projects in the direction of the second annular main part (3), and the second annular main part (3) having at least one profile bulge (9) pointing in the direction of the first annular main part (2) protrudes;

at least one sealing member (4) received in said circumferential gap (18) and sealingly abutting said first annular body (2) and said second annular body (3);

wherein the sealing element (4) has at least four sealing lips (21) which are arranged in pairs and wherein each pair of sealing lips (21) is associated with one of the profile bulges (8, 9), so that each two sealing lips (21) has a profile bulge (8, 9) and sealingly abut against this;

the sealing element (4) having axis symmetry with respect to at least one axis of symmetry (6) and the at least one axis of symmetry (6) being inclined relative to a vertical axis (13) and / or a horizontal axis;

and wherein the profile bulges (8, 9) have points which project furthest in the direction of the sealing element (4) and which points lie substantially on an axis (12) perpendicular to the axis of symmetry (6). Arrangement for sealing a rotary joint according to claim 1, characterized in that the circumferential gap (18) during a rotary movement of the first annular main part (2) relative to the second annular main part (3) and / or during a rotary movement of the second annular main part (18). 3) relative to the first annular main part (2) has a clearance, in particular a bearing clearance, wherein the sealing element (4) is deformable such that the sealing element sealingly against the first and second annular main part (2), (3), even if the size of the circumferential gap (18) is increased and / or reduced due to the game.

Arrangement for sealing a rotary joint according to one of the preceding claims, characterized in that the sealing element (4) consists of an elastic sealing material, in particular a rubber material, is vulcanizable and used together with all commonly used in mechanical engineering materials, in particular lubricants, for the lubrication of rotary joints can.

Arrangement for sealing a rotary joint according to one of the preceding claims, characterized in that the second annular main part (3) is enclosed by the first annular main part (2) and wherein the sealing element (4) is formed in several parts, in particular two parts, and wherein at least one Part of the sealing element (4) on the second annular main part (3) sealingly abuts, wherein at least the second annular main part (3) sealingly abutting part of the sealing element (4) has a closed band (5) and / or a Zugfederstrang, so in that the sealing element (4) resting against the second annular main part (3) is pressed at least partially against the second annular main part (3). Arrangement for sealing a rotary joint according to one of the preceding claims, characterized in that the sealing element (4) to at least one axis of symmetry (6) axis symmetry and wherein the at least one axis of symmetry (6) by less than 90 °, preferably by 30 °, relative is inclined to the vertical axis (13).

Arrangement for sealing a rotary joint according to one of preceding claims, characterized in that the

Seal member (20) below an outermost upper edge of the annular main parts (2), (3) is arranged.

Arrangement for sealing a rotary joint according to one of the preceding claims, characterized in that the sealing element (4) within the circumferential gap (18) and / or relative to the first and / or second annular main part (2), (3) self-positioning, in particular self-centering, in particular during a rotary movement of the first annular main part (2) relative to the second annular main part (3) and / or during a rotary movement of the second annular main part (3) relative to the first annular main part (2).

Arrangement for sealing a rotary joint according to one of the preceding claims, characterized in that the rotary connection comprises a swivel drive, wherein the first annular main part (2) is arranged stationary and is in operative connection with the second annular main part (3) and wherein a drive of the swivel drive is realized by means of a shaft (16) which comprises a toothed rim (17), via which the second annular main part (3) can be moved in rotation. Arrangement for sealing a rotary joint according to one of the preceding claims, characterized in that the first annular main part (2) associated sealing lips (21), in particular adjacent to a free space (10), (11) have a coefficient of friction and / or a coefficient of friction is different from the coefficient of friction and / or the coefficient of friction of the second annular main part (3) associated sealing lips (21) and / or that the sealing lips (21) associated contact surfaces of the first annular main part (2) have a coefficient of friction and / or a coefficient of friction that is different from the friction coefficient and / or the friction coefficient of the sealing lips (21) associated contact surfaces of the second annular main part (3).

Arrangement for sealing a rotary joint according to claim 9, characterized in that the first annular main part (2) associated sealing lips (21) or the second annular main part (3) associated sealing lips (21) and / or the sealing lips (21) associated Contact surfaces of the first annular main part (2) or the sealing lips (21) associated contact surfaces of the second annular main part (3) have a partial coating, in particular a powder coating and / or a lubrication and / or a paint coating.