DE102011011165A1 - Sealing device i.e. oil seal, for sealing gap between inner ring and nose ring of three-row roller bearing utilized in wind power plant, has stabilization or fastening components whose location within material recess is adjustable - Google Patents

Abstract

The device (1) has annular and resilient deformable sealing elements (2) with an easily deformable side resting against a rotatable part, and a non-deformable or deformation-stiff side resting against a material recess surface of another rotatable part. The expansion of the sealing elements in a radial direction is limited by the recess surface and by a seal contact surface (16) of the former part. The expansion the sealing elements in an axial direction is limited by inner or outer axial stabilization or fastening components whose location within a material recess (5) is adjustable. The former rotatable part is an inner ring (3), and the latter rotatable part is a nose ring (4). An independent claim is also included for a method for assembling and replacing a sealing device.

Description

The invention serves to seal a lubricated, in particular oil, large rolling bearing of a system, in particular a wind turbine, against leakage of lubricant and against the entry of dirt in this arrangement. Sealing device ( 1 ) for sealing the gap ( 21 ) between two mutually rotatable parts ( 3 ) ( 4 ), in particular metallic rotary or ring bodies ( 3 ) ( 4 ) according to the claims listed below. The invention also relates to a method for assembling and replacing such a device, according to the method claims listed below.

There are currently various technical solutions for sealing the connection between the rotationally moving part (shaft) and the surrounding construction (housing parts, apparatus, other parts of the plant). Many times such known as shaft seals sealing solutions are provided with Zugbandeinlage to secure the positional stability and the encompassing of the circular geometry to be sealed. It is often the case that in order to promote an even better sealing effect, a plurality of sealing rings, for example two shaft sealing rings, are mounted one above the other or axially adjacent to one another. This can be done either by direct superimposition or disregard, or by noting including a separating land between the adjacent sealing components. Such sealing solutions already exist, for example, for use in plants for the conversion of energy, for example in wind turbines. In wind turbines such stacked sealing solutions are used in particular for sealing the lubricant in the bearing, for example, to prevent the leakage of oil or lubricant from the camp.

So revealed the EP 1927795 A1 from 2006 a seal, for example, an oil seal, for providing a leakage protection for a bearing, comprising a first bearing ring and a second bearing ring which rotate at different peripheral speeds about a common axis of rotation, characterizing a sealing ring, coupled to the second bearing ring, said sealing ring a flexible Lip which presses against the sealing surface of the first bearing ring, characterized in that the oil seal component has a support ring which carries a first seal ring and a second seal ring, and wherein this support ring is coupled to the second bearing ring and slidably from a first sealing position a second seal position, wherein the first bearing ring has a seal abutment surface which opposes the flexible lip of the first seal ring when the support ring is in the first seal position - and a second seal has contact surface, which opposes the flexible lip of the second sealing ring when the support ring is slipped into a second sealing position.

Another type of superimposition or adjacent storage of multiple circumferential seal rings is known in the art, such as shown in the seal manufacturer's catalog JAMES WALKER "Walkersele® Radial Lip Seals" from 2009. page 29 shows various Zugbandeinlage sealing arrangements, which are arranged either in one direction or in opposite directions to achieve a sealing effect on a common plane or sealing surface. Such sealing solutions are sometimes referred to as multi-sealing solutions. The lubrication of such superimposed sealing rings takes place under certain circumstances by existing between the sealing rings openings. These openings are, as shown in the catalog, introduced into the component, on the side of the adjacent sealing rings are introduced.

Although several adjacent seal rings achieve a higher sealing effect in the axial direction than just an existing seal ring, as shown in the catalog, this prior art has a significant disadvantage. The disadvantage is the fact that at longer term of such a sealed arrangement, the sealing lips in engagement are ground, as well as touched by these sealing lips sealing abutment surfaces of the shaft to be sealed is obtained at longer term due to the seal friction grooves at those points where touching the sealing lips and rub as a result of the spinning action over a longer period of time. With a longer term of such mutually rotatable parts of the system, the seal is often due to wear due to the said friction, at the seal contact points or sealing contact surfaces, permeable. The consequences are leaks and failure of the originally desired sealing effect. The seal can no longer do justice to its purpose and is then renewed or replaced in practice. By replacing the sealing rings and / or the shaft to be sealed, the respective original state can be established. However, if only the seal assembly exchanged without renewing the shaft, so grasp the new sealing rings in the same sealing surfaces / grooves on the shaft to be sealed, as the exchanged, leaked or "worn" seals. In practice, for example, this could usually be avoided if the wave were also replaced. A possible exchange of the wave would be very costly. Great efforts in practice mean time and cost and are therefore disadvantageous. It would be better to create a system in which renewed sealing rings do not rest in the same grooves on the shaft as the exchanged old sealing rings.

The object is therefore to provide a device and method in which after sealing replacement an optimal sealing effect is restored and in which set new and unverschlissene or "fresh" seal contact surfaces. To improve the system as possible, it is necessary to provide a system in which renewed sealing rings do not interfere with the same areas on the shaft as the exchanged old sealing rings. The position of the shaft to be sealed here is immutable, ie static, since it is also a task not to have to replace the seal shaft in order to avoid very large efforts in practice.

In the first described solution according to EP 1927795 A1 one of the disadvantages just mentioned is alleviated by the fact that scored, due to long-lasting friction on sealing lips, surfaces or circumferences of the shaft to be sealed are not static. In the case of the sealing contact surfaces, the support ring can be adjusted axially, so that after moving the carrier ring from a first sealing position to a second sealing position no longer the same sealing contact surface is subjected to scoring, and thus the sealing effect of the overall arrangement is improved after this displacement. The areas or perimeters of the shaft to be sealed are thus not static. Also the solution EP 1927795 A1 has significant disadvantage: The system can only rarely, usually only once, be adjusted because only two adjustment positions are available. At the same time, the adjustment of the system is very complex, since heavy plant parts must be moved by small lengths. This can be a big effort. Great effort in practice mean time and costs and are therefore disadvantageous. Similarly, the solution is that the old / worn seals remain in the overall system and continue to move. Likewise, the "new" seals from the beginning of the operating life of the plant are also moved, although not engaged, and are therefore subject to the temperature and weather-related aging as well as the initially engaged sealing systems. In general, only one seal arrangement per side is engaged in this described solution.

For possible improvement of the system, it is therefore necessary to provide a system in which sealing rings can be exchanged without great effort, and in which the renewed sealing rings no longer apply the same same seal contact surface with grooves as before the seal replacement and the per side always more than one adjacent sealing ring is engaged, which will increase the sealing effect. Briefly, the prior art does not create any new or "fresh" seal contact surfaces when changing the seal and, in general terms, provides little protection against ingress of dirt.

Considering these disadvantages in summary, it is therefore necessary to provide a system in which renewed sealing rings do not rest in the same grooves on the shaft as the exchanged old sealing rings, and in the case of the sealing rings without much effort in [0006] and in [0008] can be exchanged and in which per side always more than one adjacent sealing ring is engaged, which would increase the sealing effect. In order to reduce all of the mentioned disadvantages, the present invention offers particular advantages and features. The problems with the mentioned disadvantages are solved by the features listed in the patent claims. In this case, the terms (shaft) sealing ring and sealing ring or seal and circumferential sealing device are used absolutely synonymous. Equally equivalent are the terms initial assembly and delivery status. Equally equivalent are the terms exchange assembly and seal replacement.

In general, the following objects of the invention presented here are based: sealing of the inside against oil, sealing of the outside against dirt, generation of a new sealing contact surface during gasket replacement, simple gasket assembly in the factory and in the field (for example on the wind turbine) and lubrication of the chambers between the seals.

The present invention provides the following features or properties in the form of a brief description: Firstly, the sealing effect is produced from the inside out of the bearing-pressing oil by means of two or more sealing rings arranged one behind the other. Second, the sealing of the assembly from the outside becomes dirt or foreign matter. Third, the ability to mount the dust or seal lip is facilitated by making this at least one dust or seal lip lighter and separately mountable. This is achieved in that it is introduced between two discs or plates and is fixed by these form-fitting.

Fourthly, after the replacement of the seal, a new seal contact surface is generated in that, by positioning one or more spacer elements, for example a segmented sheet-metal ring offset by an amount T or X, another sealing contact surface on the shaft is contacted by the sealing rings. A fifth object of the invention is the simple seal assembly in the factory and in the field, for example on the wind turbine. A sixth object is that the shaft seals are first exchanged and fixed by the first row of segmented disks or plates, and then, in an optionally further step, the dust lip can be mounted and fixed with the second row.

Particularly noteworthy in the present invention is the lubrication of the chambers between the adjacent or side-by-side sealing rings: between these rings, which can be made as shaft seals, lubricant such as oil can be placed in lying in the inner ring of the rotary joint chambers. These chambers have one or, ideally, multiple inlet bores. Also exist in the inner ring so-called ventilation holes to reduce pressure build-up in the interior of the lubricated ring such that these ventilation holes should prevent negative pressure can arise in an active discharge of the lubricant. Also introduced into the inner ring are outlet holes, from which the above-mentioned via the inlet holes introduced lubricant, such as oil, can be sucked out of the assembly or pumped out. Ideally, the lubricant may leak out of the assembly due to the low intrinsic viscosity without the need for auxiliaries. For more viscous lubricants, pumping or suction devices are used which establish a closed lubricant circuit between inlet ports (eg, the sum of all inlet ports) and outlet ports (eg, the sum of all outlet ports). In the area between the outer shaft seal and the dust lip, for example, only one lubrication hole is introduced.

The solution to the above-listed problems according to the conventional art is particularly successful when a controlled management of the lubricant, in this case the lubricant oil, is kept. The abovementioned components for producing a closed oil circuit then have sensors, for example for pressure measurement, temperature measurement, contamination measurement of the lubricant, as well as optionally also for direct or indirect measurement of the viscosity and aging of the lubricant. In the case of oil as a lubricant, this can be done in particular by measuring color, flow rate, electrical dielectric or particle quantity. Likewise, in this controlled management, there may be at least one lead or reservoir in which lubricant is replenished when lubricant to be exchanged is removed from the assembly, so that the total amount of lubricant is always sufficient to permit the required lubrication.

According to such an intelligent or controlled management of the oil level and various holes are introduced, for example, in the rotating inner ring of the oil-lubricated bearing in such a way that these holes both for ventilation of the bearing with the purpose of avoiding overpressure, as well as for the extraction of the oil the lower positions of the bearing rings serve. Likewise, inlet bores can be introduced into the upper positions of the bearing rings, into which lubricant can be added. From corresponding corresponding outlet holes in the lower positions of the bearing rings / this lubricant is then again escape from the overall construct or sucked. Alternatively, in a further embodiment of the invention, the outer ring may contain similar holes.

The core of the device according to the invention is described by the features in claim 1, but therefore the provision of an arrangement for fastening and holding down of circumferential sealing rings for sealing two mutually rotatable parts (for example, inner ring and outer ring) for use in wind turbines, comprising at least two axially juxtaposed circumferential sealing rings, which are arranged in particular in provided for these sealing devices recesses in the rotary body. Also present in this device is at least one circumferential dust or sealing lip, which is held and fixed at one end by positive locking between at least one hold-down plate and at least one receiving plate. The entire device is bolted to the rotary joint by at least one through the hold-down plate and receiving plate continuous screw. The material recess for receiving dust or sealing lip (s) may be incorporated in the receiving plate, or in the hold-down plate, or in both components.

According to claim 2 is provided a further important characterization of the invention, namely the presence of at least one recess located in the axial direction below the sealing device (s). Equally characteristic and essential to the invention is the presence at least one spacer element, in particular an annular spacer element, which is adjacent to at least one of the circumferential sealing devices. The spacer element is for example screwed to the rotary joint and is thus fixed, for example. The position / location of the at least one spacer element in the rotary joint can be changed. This usually occurs when the gasket (s) are to be replaced, so that the position / location of the gasket devices and gasket contact surfaces in the overall device can be changed. By said change in the position of the sealing devices and sealing contact surfaces results in the essential objective of the invention, namely the creation of new or not by abrasion / wear damaged sealing contact surfaces after replacement assembly.

According to a further feature of the invention, the at least one circumferential dust or sealing lip is curved or angled at its non-fixed portion, and the tip of the curved or angled portion points in the direction of the sealing devices, wherein the respective circumferential dust or sealing lip at its fixed end can be angled to have better positional stability when form fit. It would also be conceivable that one or more concentrically arranged fittings are present instead of the positive connection, so that the dust or sealing lip is not only positively, but also non-positively connected to the receiving plate / and or at the same time with the hold-down plate at one or more locations.

In further claims, a further feature of the invention is described, namely that at least the receiving plate and / or the hold-down plate, and / or the spacer disc or plate-shaped or are designed as concentric around the common axis of rotation of the rotary connection round discs small thickness. The thicknesses of these discs or plates may vary in thickness or may have similar dimensions. In particular, the spacer can have its own strength. This variation has the advantage that the plates or discs can be adapted to the overall strength of the rotary joint, because slewing rings for low load applications are naturally less material-consuming designed as rotary joints for the high load range.

It is also essential, for example, that all parts rotatable relative to one another are arranged about the same axis of rotation and that all the above-mentioned disk-shaped parts are arranged concentrically around the same axis of rotation.

The essence of the invention is further characterized in that all disk-shaped parts can be segmented, in particular each consist of individual ring segments. Thus, so the hold-down plate can be made circular, consisting of only two ring segments, or from three or four ring segments, or far more ring segments. The same can apply to the hold-down plate. Likewise, the spacer may also consist of one or more segments. The main advantage is that several and individual associated segments are in practice easier to handle and easier to assemble than large and heavy rings. So it is advantageous if the number of the respective segments of the disc-shaped parts is at least 2, but preferably more than 2 segments, in particular between 5 and 10 or many more segments, in particular 20 or more segments.

The invention is also advantageous if the attachment of the individual components of the device and the rotary body or on the rotary joint is solved meaningfully. This is achieved if the at least one screw connection frictionally coupled to at least one receiving plate with at least one hold-down, in particular screwed, and further this coupling is fixed non-positively in a rotating body, in particular screwed. Instead of screws but could also find bolts or rivets application. Essentially, it is important to achieve a sufficiently frictional connection of the hold-down plate with the receiving plate and the rotary body. However, threaded connections have the particular advantage of re-releasability.

For the same reason, it is recommended that the spacer elements or the spacer element is non-positively coupled, in particular screwed, with a rotary body, so that the position can always be maintained, because the or the spacer elements ensure in practice that the sealing rings in place and Should remain place.

The advantageous aspect of the lubrication bores mentioned in [0013] is achieved, in particular, by applying said bores at at least one point, but preferably at several and different points in at least one ring of the rotary joint (inner ring and / or outer ring). According to the invention, these bores make particular sense if they are arranged radially opposite the sealing devices, that is, they are each directed away from the axis of rotation and in the radial direction. The number of holes should be at least 2 for reasons of runoff and inflow. Hoses can be connected to the holes or Pressure lines, which are connected to mechanical or electrical equipment and control devices, in particular connected to sensors. In order to realize a closed circuit, at least one conveying system for conveying lubricant or at least one engine, in particular at least one pump or a motor, and associated sensors and control devices for the intelligent control of the lubricant flow are furthermore necessary.

The core of the invention is therefore further characterized in that each is provided separately for a holes for the purpose of supplying or discharging lubricant are introduced into the device, in particular for the lubrication of the sealing rings, and serve for the purpose of ventilation or pressure equalization.

Not only the device is characteristic of the invention. In particular, the method for assembling and replacing such sealing devices with the particular aim that after the replacement of the seal (replacement assembly), a new, "fresh" seal contact surface based on the state of the initial assembly ex works (initial assembly). The method according to the invention provides, under protection, at least one special method for assembling and replacing such device for fastening and holding down circumferential sealing rings for sealing two mutually rotatable parts for use in wind turbines, comprising at least two axially adjacent circumferential sealing devices, which are in particular arranged for them Sealing devices provided recesses in the rotary body, as well as containing at least one circumferential dust or sealing lip and containing at least one screw.

According to the method claim of the invention results after the initial assembly at time I, when viewing the plan view in the axial direction, the following installation situation: (At least) a hold-down plate is located on (at least) a receiving plate, at the same time in that position positively fixing at least one dust or Sealing lip, wherein at least one receiving plate rests on the rotary body and at the same time on (at least) a spacer, which in turn rests on this spacer at least one of the optionally. A plurality of superposed circumferential sealing device (s). This sealing device (s) rests on the rotary body and adjoin a recess. After an exchange of the sealing package, so at a later time II., There is a changed installation situation. It is then so that when viewing the plan view in the axial direction, said spacer comes to lie directly on the rotary body and there by a screw coupled / screwed to the rotary body, so that it adjoins the further recess, and wherein the receiving plate side sealing device then directly touches the receiving plate. As a result, then the position of the peripheral sealing device (s) is axially displaced by a distance in height X or in the amount of Distanzelementdicke compared to the initial assembly at time I.

Equally to the procedure just presented, the procedure in alternative order also makes sense, but its concept of invention is synonymous. Accordingly, it is such that after the Austauschmontage (time II.) When viewing the top view in the axial direction, a hold-down plate rests on a receiving plate, at the same time in that position positively fixing the at least one dust or seal lip wherein the receiving plate rests on the rotary body and at the same time on a spacer element. Further, this spacer element is located on at least one of the peripheral sealing device (s) arranged one above the other, wherein this sealing device is respectively arranged in recesses provided in the rotary body, and wherein the at least one circumferential sealing device rests on the rotary body and adjacent to the above-mentioned further recess.

It then turns out that at first assembly (time point I.) When looking at the top view in the axial direction, the spacer element comes to rest directly on the rotary body and there is coupled by a screw with the rotary body, so that it adjoins the said further recess. Then, the receiving plate side sealing device contacts the receiving plate directly. Also in this modified method of the same inventive idea, it is such that at first assembly (time I.) When viewing the top view in the axial direction, the position of the circumferential sealing device (s) is axially displaced by a distance X, or in the amount of Distanzelementdicke opposite the exchange assembly (time II.).

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 shows:

1 an exemplary part of a large rolling bearing according to the current state of the art for a more detailed explanation of the position to which the invention can be applied.

2 the exemplary placement of said holes in the inner ring of a slewing bearing.

3 the section through a segment of an exemplary Drehvebindung or a large rolling bearing, exemplifying the inventive structure of the device.

4 the section through a segment of an exemplary Drehvebindung or a slewing bearing, revealing the sequence of the procedure for assembly and replacement, thereby indicating the original state ("delivery state") z. For example: at initial installation and the state of replacement ("after gasket replacement").

5 the section through a segment of an exemplary Drehvebindung or a slewing bearing, revealing the sequence of alternative but equivalent method for assembly and replacement, thereby indicating the original state ("delivery state") z. For example: at initial installation and the state of replacement ("after gasket replacement").

6 the exemplary placement of holes in the inner ring of a slewing bearing, while additionally representing the upper and lower portions of such a bearing in respective sectional view.

7 a detail from 3 , thereby exemplifying a dust or sealing lip.

1 shows a section through slewing bearings according to the current state of the art and descriptive previous possible mounting methods of shaft seals, illustratively emphasizing two opposite circular cutouts, in which, for example, each two circumferential sealing devices can be axially superimposed, thus the designated recesses or cavities ( 5 ) to fill. It is easy to recognize each one screw connection ( 7 ), which, for example, connects a single annular disc ( 19 ) with a total package of two sealing arrangements and the rotary body ( 4 ). The recesses ( 5 ) for the sealing devices ( 2 ) are not in example in the nose ring ( 3 ) of the slewing bearing, but in the other mutually rotatable part of the plant, such as support ring ( 4 ) or retaining ring ( 4 ), simply called "rotary body". The slewing bearing is designed for example as a three-row roller bearing, of course, any other bearing designs would be conceivable. The recesses ( 5 ) for the sealing rings are integrated here in supporting ring ( 4 ) and retaining ring ( 4 ) and sealing the support ring ( 4 ) to the nose ring ( 3 ) or the retaining ring ( 4 ) to the nose ring ( 3 ). For example, be used in the drawing radial and axial Rollenwälzkörper ( 18 ) with a diameter of 50 mm or 60 mm. Distinguishing from this exemplary prior art, all other drawings show embodiments according to the invention.

3 shows according to the invention one of the circular cutouts 1 in detail, being contrary to the state of the art 1 in 3 the device according to the invention, including drawn sealing components, is shown.

3 shows therefore the section of a slewing bearing or of a swivel drive or of a similar rotational connection of two mutually rotatable parts ( 3 ) ( 4 ), by way of example including the arrangement according to the invention ( 1 ), the inventive arrangement ( 1 ) is characterized by a dashed line bordered area, which, for example, in 1 was indicated in a circle. The sealing package contains two adjacent sealing rings ( 2 ), which are contained in recesses ( 5 ), as well as a dust or sealing lip ( 6 ) and a screw connection ( 7 ). Furthermore, at least one disc-shaped receiving plate ( 8th ), this receiving plate ( 8th ) on the right-hand end thereof, also characterized by the circular area F shown in dashed lines, material recesses ( 9 ), for example, introduced by correspondingly shaped manufacturing mold or by chip-removing production process, for receiving the at least one further circumferential dust or sealing lip ( 6 ) owns. This at least one further circumferential dust or sealing lip ( 6 ) is factory-installed in the receiving plate ( 8th ) brought in. The hold-down plate ( 10 ), which the lip ( 6 ) always held in place by positive fixation and therefore not slipping with its fixed end ( 14 ) is the material recesses of the receiving plate ( 8th ). Hold-down plate ( 10 ) and receiving plate ( 8th ) are in the drawing shown touching each other surface.

Further shows 3 in the arrangement according to the invention ( 1 ) is at least one further recess ( 11 ), for example a cavity ( 11 ). This recess is, for example, an area which serves as a precondition for the case that is connected to this cavity (FIG. 11 ) adjacent seal ( 2 ) moves under load, so that in the axial direction in the direction of the cavity ( 11 ) is pressed or deflected. Without the recess ( 11 ), the seal on the rotary body ( 4 ), for example on the support ring ( 4 ), Which could adversely affect the service life of the seal. It is therefore particularly advantageous if the seal ( 2 ) even in the most heavily loaded case always only one Sealing contact surface ( 16 ) has, in all other spatial directions so can be freely deflected without getting to another attack surface. The recess ( 11 ) is thus generally at least so great that the deformation movement of the adjacent seal ( 2 ), as stated, can be accommodated without the seal touching other parts.

This cavity ( 11 ) in 3 is enlarged, for example, if the adjacent sealing arrangement ( 2 ) through the spacer ( 12 ) is additionally spaced from the rotary body. Then the cavity or the recess ( 11 ) is increased by an amount defined by the area T · K. The size of the cavity ( 11 ) or the recess, if the adjacent sealing arrangement ( 2 ) not by the spacer ( 12 ) is additionally spaced by the rotating body is regularly defined by the area ΔL · K. The spacer element ( 12 ), which may be annular and of particular thickness (T), is adjacent, for example, to the peripheral sealing devices ( 12 ), wherein the at least one further recess is always adjacent to at least one of the peripheral sealing devices ( 12 ). Exactly this variable T defines the axial dimension around which the sealing arrangements ( 2 ) in the axial direction when they are exchanged or changed according to the inventive method. Then arise also by the distance T shifted axial sealing contact surfaces 16 ). The region in which the seals start in the radial direction on the shaft to be sealed is shown in dashed lines and framed by the region G. Furthermore, to recognize in 3 ,

are two holes ( 20 ), through which the seals ( 2 ) can be supplied for example with lubricant, such as oil.

4 , From this drawing, the method according to the invention is readily apparent by way of example when replacing one or more of the sealing rings ( 2 ). In order to avoid complexities, the sealing components ( 2 ) ( 6 ) not shown, but instead only the space provided for this purpose ( 5 ) or recesses ( 9 ). Shown is the method of assembling and replacing such device ( 1 ) for fastening and holding down circumferential sealing devices ( 2 ), in particular of sealing rings ( 2 ) for sealing two mutually rotatable parts ( 3 ) ( 4 ). After the initial assembly, or assembly from the factory so in the "delivery state", when viewing the top view (DS) in the axial direction, comes a disc-shaped hold-down plate ( 10 ) lie on a disc-shaped receiving plate ( 8th ), at the same time positively fixing a dust or sealing lip ( 6 ), wherein the disc-shaped hold-down plate ( 10 ) lies on the rotating body ( 4 ) and a disk-shaped spacer element ( 12 ), wherein the disc-shaped spacer ( 12 ) lies on at least one of the peripheral sealing devices ( 4 ). It is quite clear that the spacer element ( 12 ), characterized by (T), has a bore which is provided with a countersink. Through this hole, a screw can be inserted through, so that the spacer element, for example, with the overlying plate ( 8th ) can be screwed. However, it is equally possible - and exactly as it is shown in 4 - that the spacer element ( 12 ) without being screwed between the mounting plate ( 8th ) and a sealing device ( 4 ) comes to rest. If the spacer element ( 12 ) but in the plate ( 8th ) is screwed above, so it must, of course, top-bottom-reversed than in 4 be introduced into the overall arrangement, so that the lowered screw portion not to the plate ( 8th ) but lies on the opposite side. In general, instead of countersunk screws, the more usual Allen screwed connections are also suitable. The sealing device (s) ( 4 ) in turn are each arranged in designated recesses ( 5 ) in the rotary body, and wherein the at least one circumferential sealing device comes to rest on the rotary body and adjacent to the further recess.

In 4 , one clearly sees that in the original state, also called initial assembly or delivery state, the above-described recess ( 11 ) has less volume than after the replacement of the seal, that is, after exchange assembly of the sealing devices ( 2 ). This is due to the fact that at the time of the seal replacement not only the sealing devices ( 2 ), for example the sealing rings ( 2 ), but at the same time when replacing the renewed sealing rings ( 2 ) the spacer ( 12 ), also intermediate piece ( 12 ), the position changes. Before (at first assembly) the spacer was above the sealing devices ( 2 ), ie in an axial position directly between sealing devices ( 2 ) and receiving plate ( 8th ). Afterwards (with exchange assembly) the spacer is below the sealing devices ( 2 ), ie in an axial position directly between the lower sealing device ( 2 ) and rotary body ( 4 ), this spacer for better fixation usually with the rotary body ( 4 ) can be screwed ( 15 ). It is clearly recognizable that the recess ( 11 ) before the replacement of the gasket a smaller volume than after the replacement of the gasket. In general, for example, after a seal replacement, the difference length X have the same value as the height T.

5 As an alternative to the described method in the immediately following section, its changes in the construction according to the inventive method of the 4 is clearly recognizable, it is also possible according to the invention, for example, to reverse the order, as described below. An alternative method according to the invention for assembly and replacement of the device results ( 1 ). For the sake of completeness are in 5 According to the invention, the sealing components in the designated spaces completely drawn, for example, the dust or sealing lip ( 6 ) drawn in the space or the material recess ( 9 ) between hold-down plate ( 10 ) and receiving plate ( 8th ), contacting the associated sealing contact surface ( 16 ), and the sealing rings ( 2 ) are marked in the recesses provided for this purpose ( 5 ) in the rotary body ( 4 ), touching the respectively associated sealing contact surfaces ( 16 ).

In this drawing 5 is exemplified that in the state of delivery, ie the initial assembly, the spacer element ( 12 ) is directly adjacent to the rotary body ( 4 ) and possibly bolted to it ( 15 ). When viewing the plan view (DS) in the axial direction applies to the replacement of the seal, so for the exchange assembly that a hold-down plate ( 10 ) rests on a receiving plate ( 8th ), at the same time positively fixing in that position the at least one dust or sealing lip ( 6 ), the hold-down plate ( 10 ) rests on the rotary body ( 4 ) and at the same time on a spacer element ( 12 ), this spacer element ( 12 ) from below into the receiving plate ( 8th ), or for example in the retaining plate ( 10 ), can be screwed (thus pointing from the bearing inside in the screwing direction to the bearing outer side and the receiving plate) and rests on two superposed circumferential sealing devices ( 2 ), which are each arranged in provided recesses ( 5 ) in the rotary body, and wherein the at least one circumferential sealing device ( 2 ) is mounted directly on the rotary body ( 4 ). Then the recess ( 11 ) after the replacement of the gasket a smaller volume than before the replacement of the gasket. Of course it is with this arrangement 5 in such a way that when delivered, ie during initial assembly, the spacer element ( 12 ) analogous to the previous method of fastening, so to the rotary body ( 4 ) ( 15 ) can be that the recess ( 11 ) releases a higher volume. For example, even after a seal replacement, the difference length X may have the same value as the height T.

6 shows according to the invention in the middle a large roller bearing for use in wind turbines after the device claim, which are indicated by arrows respectively in the upper part of the drawing, a section of the bearing, in enlarged detail pointing the holes ( 20 ) for lubricating the device ( 1 ) or the sealing arrangements ( 2 ), for example, by oil as a lubricant, and being indicated by arrows in the lower part of the drawing, a section of the bearing, in enlarged detail pointing holes ( 20 ) for lubricating the device ( 1 ) or the sealing arrangements ( 2 ), for example by using oil as a lubricant. In the in the drawing 6 Executed version, the bearing is, therefore, vertically inserted.

Accordingly, further described according to the invention in 2 and 6 each a large roller bearing for use in wind turbines according to the device claim, which is characterized in the upper part of the drawing, a section of the bearing, showing in enlarged detail the oil inlet holes (D) (D3) for lubrication of the seal contact surfaces ( 16 ), and where indicated by arrows in the lower part of the drawing, a section of the bearing, showing in enlarged detail Ölauslassbohrungen (D1) for lubrication of the sealing contact surfaces ( 16 ). In both drawings 2 and 6 are further characterized by arrows laterally in the inner ring existing holes (D2) which serve the air circulation and thus were introduced to counteract the emergence of a pressure gradient between the top of the bearing and the bottom of the bearing. These holes (D2) to prevent pressure build-up could for example also be introduced into the outer ring. In the illustrated example embodiment, the bearing is, therefore, used vertically. These holes (D2) to prevent the pressure build-up could also be present above the symmetrical center line of the vertically inserted bearing, but should always be introduced above the present in the existing bearing oil sump.

7 describes according to the invention the detail F from 3 closer and has an embodiment, as the dust or sealing lip ( 6 ) at its unfixed area ( 13 ) is curved and the tip in the direction of the sealing arrangements ( 2 ) shows. It is further shown in detail that one end of the dust or sealing lip ( 6 ) is angled, here, for example, bent at right angles. This bend serves for an even better fit and thus against the slipping of the lip ( 6 ) within the recess provided for the seal ( 9 ).

In 4 and 5 Is it easy to recognize the method according to the invention for replacing the sealing components: After the initial assembly, when the plan view (DS) is viewed in the axial direction, a hold-down plate (FIG. 10 ) lying on a receiving plate ( 8th ), at the same time in that Position positively fixing the at least one dust or sealing lip ( 6 ). The receiving plate ( 8th ) lies on the ring body ( 4 ) and simultaneously on a spacer or spacer element ( 12 ) on. This spacer or spacer element ( 12 ) lies on at least one superposed circumferential sealing element ( 2 ) This at least one circumferential sealing element ( 2 ) lies on the ring body ( 4 ) and adjacent to another recess ( 11 ). In the case of replacement assembly, however, when viewing the plan view (DS) in the axial direction, the Distanzstück- or spacer element ( 12 ) lie directly on the ring body ( 4 ) and is there by a screw ( 15 ) coupled to the rotary body ( 4 ), so that it is adjacent to the further recess ( 11 ), wherein the receiving plate-side sealing element ( 2 ) then directly the receiving plate ( 8th ), wherein the axial position of the at least one sealing element ( 2 ) is displaced axially by a length or a distance, in particular by a distance equal to the spacer or Distanzelementdicke (T), compared to the initial assembly.

LIST OF REFERENCE NUMBERS

1

Device for fastening and holding down

2

Sealing device; Sealing ring; Shaft seal ring. sealing element

3

against each other rotatable part; rotating body

4

against each other rotatable part; rotating body

5

recess

6

Dust or sealing lip

7

screw

8th

mounting plate

9

material cut

10

Hold-down plate

11

recess

12

spacer

13

non-fixed area of the dust or sealing lip

14

fixed end of the dust or sealing lip

15

further screw connection

16

Seal contact surfaces

17

(Common) rotation axis

18

rolling elements

19

Single ring disk

20

drilling

X

length difference

I.

Axial position of the sealing device after an initial assembly

II.

Axial position of the sealing device after a replacement assembly

DS

Top view of arrangement / device in the axial direction

T

Thickness of the spacer element

D

Lubricating hole between the shaft seals

D1

Outlet holes between the shaft seals

D2

Ventilation holes between the shaft seals

D3

Lubricating holes between dust seal and outer shaft seal

K

horizontal cavity defining

.DELTA.L

vertical cavity defining

M

The axial distance of those points where press several annular sealing elements in each case against the sealing surface

Cited patent literature:

• EP 1927795 A1 DARWIND DEV & DEMONSTRATION BV [NL]

Quoted Non-Patent Literature:

• Catalog of the Year 2009 of the seal manufacturer JAMES WALKER "Walkersele® Radial Lip Seals"

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 1927795 A1 [0003, 0007, 0007]

Cited non-patent literature

• JAMES WALKER "Walkersele® Radial Lip Seals" from 2009. Page 29 [0004]

Claims (11)

Sealing device ( 1 ) for sealing the gap ( 21 ) between two mutually rotatable parts ( 3 ) ( 4 ), in particular metallic rotary or ring bodies ( 3 ) ( 4 ), comprising at least one annular and elastically deformable sealing element ( 2 ), which is arranged in a circle around a common axis of rotation ( 17 ) and is inserted in a circumferential material recess ( 5 ) in the second of the rotatable ring body ( 4 ), wherein a more easily deformable side of the respective sealing element ( 2 ) bears against the first of these rotatable parts ( 3 ) and at least one non-deformable or deformation-rigid side of the same sealing element ( 2 ) abuts a first material recess surface ( 22 ) of the second part ( 4 ), and wherein the extension of the at least one sealing element ( 2 ) is limited in the radial direction by this first material recess surface ( 22 ) on its one side and through the sealing contact surface ( 16 ) of the first rotatable part ( 3 ) on the opposite side, characterized in that - the extent of the at least one sealing element ( 2 ) in the axial direction is limited by internal or external axial stabilization or fastening components, - wherein inner axial stabilization or fastening components within the material recess ( 5 ) are mobile, - as a result of the first part ( 3 ) axially movable sealing contact surfaces ( 16 ) of the at least one sealing element ( 2 ). Apparatus according to claim 1, characterized in that external axial stabilizing or fastening components relative to a ring body ( 4 ) are immovable, such as in particular a horizontal material recess surface ( 23 ) of the second ring body ( 4 ) or horizontally on this ring body ( 4 ) attached bodies ( 8th ) ( 10 ). Device according to claim 1 characterized in that inner axial stabilization or fastening components, in particular also in the form of at least one spacer or spacer element ( 12 ), relative to the ring bodies ( 3 ) ( 4 ) in the geometric space of the material recess ( 5 ) are mobile, in particular axially translationally displaceable, are. Device according to at least one of the preceding claims, characterized in that the sealing device ( 1 ) as a subunit in a bearing assembly, in particular in an assembly for supporting the main axis of a wind turbine, is used, wherein always at least one annular and elastically deformable sealing element ( 2 ), but in particular two and more such sealing elements ( 2 ) are directly adjacent and at the same time sealingly in operation. Device according to at least one of the preceding claims, characterized in that at least one circumferential dust or sealing lip ( 6 ) is available. Device according to at least one of the preceding claims, characterized in that at least one of the outer stabilizing or fastening components is designed disc-shaped, in particular in the form of a receiving plate ( 8th ) and also in the form of a hold-down plate ( 10 ), but ideally also the inner stabilizing or fastening components, for example the spacer or spacer ( 12 ), is disc-shaped Device according to at least one of the preceding claims, characterized in that at least one of the outer stabilizing or fastening components, the device for the device ( 1 ) are fixed in place, these outer stabilizing or fastening components being associated with an adjacent construction which, from above, in particular in the direction of the top view (DS), belongs to the device (FIG. 1 ), and thus in particular disc-shaped stabilizing or fastening components ( 8th ) or ( 10 ) replace. Device according to at least one of the preceding claims, characterized in that all mutually rotatable parts ( 3 ) ( 4 ) around one and the same axis of rotation or rotation ( 17 ) and all stabilizing or fastening components or disk-shaped parts ( 8th ) ( 10 ) ( 12 ) concentrically about this same axis of rotation ( 17 ) are arranged. Device according to at least one of the preceding claims, characterized in that disk-shaped parts ( 8th ) ( 10 ) ( 12 ) are segment-like, in particular each consist of individual ring segments. Method for assembling and replacing such sealing device ( 1 ) for sealing the gap ( 21 ) between two mutually rotatable parts ( 3 ) ( 4 ), comprising at least one axially juxtaposed circumferential sealing element ( 2 ), which are in particular arranged in one for this at least one sealing element ( 2 ) provided recess ( 5 ) in the ring body ( 4 ), characterized in that when looking at the axial position of the at least one circumferential sealing element ( 2 ) after an initial assembly (I.) and after an exchange assembly (II.), an axial displacement of the Berührortes the Sealing lip of the at least one sealing element ( 2 ) with the sealing contact surface ( 16 ) is present by a difference length (X). A method according to claim 10, characterized in that the axial distance (M), those points at which a plurality of annular sealing elements ( 2 ) in each case against the seal contact surface ( 16 ) or sealingly contact them after exchange assembly has a different distance (M) than before replacement assembly, in particular increased or decreased distance (M).

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