DE202012011902U1 - Moment bearing with distance sensor for Condition Monitoring System (s) - Google Patents

Abstract

Moment or (large) rolling bearing (1) or rotary joint (1) comprising: - at least one non-contact sensing, preferably by inductive method measuring or detecting, alternatively by means of sound waves or eddy current method measuring or detecting, optionally measuring or detecting by means of capacitive method , Distance sensor (4), - for at least temporary, but preferably continuous, measurement or sensing or detection of the axial distance (Δs) or the displacement and / or the radial distance or the displacement (Δv) of at least two bearing rings (6; in which the at least one distance sensor (4) via a suitable means (9), preferably via a sensor bore per distance sensor (4), in one of the bearing rings (6, 7) and against a non-stage-like Contour or geometry (11) is fixed or introduced, - wherein the non-stepped contour or geometry (11 ) either a V-shaped contour (11 ') or a ramp-shaped contour (11' '), for example, with a continuous slope, or a rounded contour (11' ''), possibly similar to a Kuhle, or ...

Description

The invention relates to a moment or (large) rolling bearing or a rotary joint having at least one contactless sensing, preferably by inductive method measuring or detecting, alternatively by means of sound waves or eddy current method measuring or detecting, possibly a measuring by capacitive method or detecting, distance sensor, at least temporarily, but preferably continuously, measurement or detection of the axial distance or the axial displacement and / or the radial distance or the radial displacement of at least two bearing rings relative to each other in the bearing gap, wherein the at least one distance sensor via suitable means, preferably via each has a sensor bore, which is fixed or introduced at least in one of the bearing rings and against a non-stepped contour or geometry, wherein the non-stepped contour or geometry either a V-shaped contour or a r ampenförmige contour, for example, with a continuous slope, or a rounded contour, optionally similar to a Kuhle, or a survey, for example, which is formed by an additional body having. Further advantages and technical features emerge from the description and the claims.

State of the art:

In rolling bearings and slewing bearings, there is basically the inherent problem that after prolonged use the risk of fatigue or material fatigue in the form of damage or destruction of the raceways or rolling elements. In general, each rolling bearing or each slewing bearing, as well as a rotary joint and / or a moment bearing, calculated and designed for a certain life.

Even today, however, it is hardly possible to clearly determine the exact time of exhaustion, since in practice the calculation time often differs from the actual time of failure. Essentially, the actual outage depends on material, manufacturing and operating conditions. By continued good lubrication of such a bearing or such a rotary connection with oil, grease or other lubricant, is always always trying to keep the friction as low as possible. By a suitable and permanent lubrication, the life of the bearings, rotary joints, etc. may increase in principle.

The aforementioned damage or destruction begins, for example, with the formation of material breaks and / or depressions in the raceway, since the track is often designed in lower hardness than the cooperating with them rolling elements. These depressions can become larger with increasing operating time and lead to breakouts in the career. With continued use of the rolling bearing these breaks sometimes lead to even larger material outbreaks, which can then cause a sudden blocking of the bearing, which can lead to failure of the entire machine or the vehicle, used in or in the camp or the rotary joint becomes. In addition, existing spacers or cage segments may be damaged by the above-mentioned outbreaks possibly existing in the storage system, There are therefore various technical efforts to detect the wear of, for example, a rolling bearing or large rolling bearing early by suitable diagnostic and / or wear detection devices, d. H. before it comes to the aforementioned failure of the entire machine or system or the vehicle.

From the prior art, for example in the EP 0922 870 B1 described, therefore, are such large rolling bearings are known which have a wear measuring device for a slewing bearing in such a way that the slewing bearing consists of two bearing rings, while arranged in between them, a Wälzkörperbauraum forming rolling elements are arranged. The wear measuring device is provided with a display which indicates a predetermined deflection between the bearing rings and a probe which is arranged in an opening of a bearing ring and can come into contact with its end with a surface of the other bearing ring, wherein the probe opposite bearing ring with a groove is formed into which projects the end of the probe and wherein the surfaces of the groove each have a distance from the probe, which corresponds to a predetermined in the associated direction wear.

In addition, according to the conventional state of the art, such probes or sensors which are supplied electrically or coupled with electrical lines are frequently used, which as a rule operate without contact, ie. H. For example, emit waves, such as mechanical waves such as sound waves or electromagnetic waves.

1 shows such a large rolling bearing according to the conventional art.

In practice, the following aspects of this technical embodiment have proven to be disadvantageous in the prior art, provided that a non-contact, for example wave-transmitting, sensor is used as the probe:
It can be monitored or determined by the sensor or the probe of the wear measuring device only the wear of the ball track. The effect of the wear measuring device thus does not go beyond this career. Damage that occurs outside of this career is therefore not measured or sensed.

If the sensor or the probe of the wear measuring device is not installed flush with the diameter of the inner ring, this can be damaged or even destroyed due to breakages or shavings of metallic material located in the raceway system.

Since the sensor or the probe of the wear measuring device according to the conventional art is often mounted very close to the screw heads or nuts, too high applied surface pressure or surface forces can damage or even destroy the sensor or the probe.

In addition, sensors or the probe of the wear measuring device according to the aforementioned prior art sometimes requires significantly high installation space, which is not always available in practice, in particular in small-scale precision applications.

However, the biggest disadvantages result from the shape and position of the groove, as described below:
Basically, firstly, in practice, this groove will very likely accumulate with lubricant, especially grease, as well as with metal particles of the aforementioned bursts or breaks. These particles can significantly influence or disturb the sensor signal or the transmitted waves. The quality of the sensed or measured or detected signal suffers due to these influences or disturbances partly considerable. Frequently, the quality of the sensor becomes so bad that the entire result of the sensing must be called into question.

Secondly, this groove and the position of the sensor or probe must be aligned in such a way that radial wear or tilting of the bearing can be detected by the sensor or the wear measuring device. This is usually only possible if the sensor tip or probe tip "targets" exactly on the groove, which is the case when the bearing is loaded only in the radial direction and undergoes no tilting in the axial direction. In practice, however, in particular when using the aforementioned torque bearings, tilting of the bearing in the axial direction almost always occurs. As a result, the groove is moved in the axial direction or rotated at least as a result of the moment by a certain angular displacement in the axial direction. The sensor tip or probe tip may "aim" at axial tilting or tilting of the bearing, or generally at axial displacement of the bearing, then at the edge or edge region of the groove. Since the edge region of a groove is always delimited by a step formation, the value sensed by the sensor tip or the probe tip can thereby change abruptly.

The connected probe or sensor electronics / electrics will consequently and erroneously detect a sudden change in the wear value. If you want to completely eliminate this misrecognition, so should a wear measuring device similar or exactly the doctrine of EP 0922 870 B1 for safety only be used for large bearings, which are loaded only in the radial direction and not in the axial direction.

A use of a wear measuring device similar or exactly according to the technical teaching of EP 0922 870 B1 The sensor or probe tip of the wear measuring device can even permanently damage or destroy a bearing ring when there is strong axial displacement, provided that an edge of the groove mechanically collides with the sensor or probe tip due to the axial displacement.

Only in rare cases, however, are heavily loaded machines or plants as well as vehicles, construction machinery, cranes, mobile cranes, wind turbines, tidal power plants, etc. so burdened that only radial loads act.

In summary, can be through this aforementioned groove shape, in particular by their step-like geometry, for example in the expression of the technical teaching of EP 0922 870 B1 , at the most a radial displacement, for example due to wear, but not an axial displacement, reliably sense.

Object of the invention and description:

From the disadvantages of the prior art described results in the invention initiating problem, axially and radially by (strong) forces and / or moments acted upon bearing or (large) rolling bearing or a rotary joint so educate, so that under operation a precise and accurate and reliable sensing or measurement or detection of the axial and / or radial displacement and / or the state of wear of the moment or (large) rolling bearing or the rotary joint in the axial and / or radial direction is given.

The solution to the problem is achieved by mounting in the axial and / or radial direction measuring or detecting distance sensors at defined locations of the bearing ring or the bearing rings, wherein such a distance sensor respectively the distance or the relative movement between the body (bearing ring) and measuring device (distance sensor ) is capable of sensation. This relative movement can either result from the wear of bearing components, or - possibly in superimposing manner - from the action of loads on the bearing or the rotary joint, ie due to externally applied forces and / or moments originate.

The solution of this problem is achieved in particular by the fact that in the sense of the present invention at least one contactless sensing, preferably a measuring or detecting by inductive method, alternatively by means of ultrasonic or eddy current method measuring or detecting, possibly by means of capacitive method measuring or detecting, distance sensor for at least temporary, but preferably continuous, measurement or detection of the axial distance (Δs) or the axial displacement and / or radial displacement (Δv) or the radial distance of at least two bearing rings is used relative to each other.

This at least one distance sensor is preferably introduced by suitable means in the bearing gap between the respective mutually rotatable bearing rings, preferably via a sensor bore in one of the bearing rings that compared to the distance sensor is given a non-step-like contour or geometry, this non-stepped contour or geometry in is located opposite the distance sensor bearing ring and about the width of the bearing gap, preferably at least 0.20 mm, ideally between 0.20 and 9.5 mm or even between 1.0 mm and 4.0 mm, optionally spaced by the width of the bearing gap +/- 0.2 to 3.5 mm from the distance sensor is.

The non-stepped contour or geometry in this case has either a V-shaped contour or a ramp-shaped contour or a rounded contour. Alternatively, this non-stepped contour or geometry can be formed by one or by an additional body, which is introduced or fixed in those bearing ring, which is opposite to the distance sensor.

Of course, the invention relates not only to the use in rolling or moment bearings, but also to all types of slewing and slewing bearings, ideally for use in machines and equipment and vehicles such as: tunnel boring machines, stackers, construction machinery, agricultural machinery, cranes , Mobile cranes, aerial work platforms, wind turbines, tidal power plants, medical apparatus, for rotatably adjusting carriages in military vehicles or for adjusting water cannons on fire engines, for rotary storage of turbines and / or rotors in power plants, in solar systems, rides in amusement parks, et cetera.

In a further embodiment, the invention is also used in rotary joints of rotary actuators, also called "swivel drives", and associated with associated worm gear systems.

These torque or roller bearings or slewing bearings and or rotary joints can be designed as a barrel roller bearing, cylindrical roller bearings, needle roller bearings, tapered roller bearings or even as ball bearings, with at least one row of rolling elements. Alternatively, even as a cross roller bearing or combination bearing or even in the design of a four-point ball bearing.

Individual descriptive features, details, advantages and effects on the basis of the invention will become apparent from the following description of preferred embodiments of the invention and from the following drawings:
So shows about 2 clearly the non-step-like contour or geometry ( 11 ), in particular as a V-shaped or ramp-shaped contour in the distance sensor ( 4 ) opposite bearing ring ( 6 ). In this first advantageous embodiment of the invention is the sensing or detecting end of the distance sensor ( 4 ) in a bearing ring a continuously changing in the axial direction contour or geometry ( 11 '' ) in the opposite bearing ring opposite.

2 also describes the following embodiment by way of example:
This non-step-like geometry is in 2 in contrast to the prior art - see 1 - ramped ( 11 '' ). This has the particular advantage that, when one bearing ring is displaced relative to the other bearing ring in the axial direction, the direct distance (Δs) between the bearing-gap-side end (A) of the sensor (FIG. 4 ) to the opposite bearing ring ( 6 ) assumes a steadily changing amount until such time as a vertex (S) is reached.

Starting, for example, from the upper axial end of the gap ( 10 ), this continuous change of the contour ( 11 ; 11 '' ) as a notch or notch - or just as the aforementioned 'ramp' - dar.

This aforementioned continuous change of the distance between the slot (A) of the sensor ( 4 ) and the non-stepped contour or geometry ( 11 ) is due to the measuring method of each non-contact distance sensor ( 4 ) detectable or sensible or detectable. Wrid, for example, a sound wave based measuring method of the distance sensor ( 4 ), the aforementioned change in the distance due to the changed duration of the sound wave is recognizable, because in metallic material, the speed of sound is higher than z. B .: as in the air in the bearing gap ( 10 ). Even if the bearing gap ( 10 ) is filled with oil and / or lubricant, resulting in a changed duration of the wave against a metallic material, for example. of the bearing ring.

3a shows another variant of the aforementioned ramp-shaped ( 11 '' ) Contour or geometry. In 3a this non-step-like geometry ( 11 ) by a separate body, the so-called. Additional body ( 12 ), in the moment or (large) rolling bearing ( 1 ) or in the rotary joint ( 1 ) brought in. It may be in this additional body ( 12 ) act around a rotating ring. See the description below.

The aforementioned advantage which the non-step-like geometry ( 11 ) brings possibly even increased, if according to 3a and or 3b the vertex (S) of the maximum elevation on this non-stage geometry or contour ( 11 ) and into the bearing gap ( 10 ) protrudes.

In 3a and 3b this vertex (S) is executed as a peak. This results in an analytical discontinuity of the non-step-like contour ( 11 ) at the vertex (S).

In 4a and 4b whereas this vertex (S) is the highest point on a curve contour ( 11 ), where the analytic continuity is given at the vertex (S).

The above variants or embodiments (cf. 3a and 3b compared to 4a and 4b ) have the great advantage that the vertex (S) is considered a "switching point" in the sensing of the axial displacement (Δs). For example, in rest position, ie at a non-loaded torque or (large) bearings ( 1 ) or a non-loaded rotary joint ( 1 ), the bearing gap-side end (A) of the distance sensor ( 4 ) directly aligned with this vertex (S) or aligned, it is during the later operation of this momentary or (large) rolling bearing ( 1 ) or this rotary joint ( 1 ) is easily possible to detect or detect or sense displacements due to stress and / or wear in the axial direction (Δs) starting from this vertex (S).

The vertex (S) thus serves as a "zero position" or as a "reference position" for the measured values or measurement results of a non-contact distance sensor ( 4 ).

After the hitherto conventional technology in the sense of 1 this is clearly not possible, since even with axial displacement of the large rolling bearing (G) of the sensor ( 4 ) always on a groove ( 5 ), whereby this groove always has the same depth of penetration along its foot. A dedicated information about the displacement path in the axial direction (Δs) is in a slewing bearing after 1 clearly not given.

The vertex (S) of the non-step-like contour or geometry ( 11 ) within the meaning of the invention ( 1 ), however, marks the location of the maximum elevation - or alternatively the location of the maximum notch as in 2 represented - the non-stepped contour or geometry ( 11 ) opposite to this contour ( 11 ) bearing ring ( 6 ) and thus provides feed for evaluable travel information in the axial direction (Δs), which is the conventional state of the art, cf. 1 , misses.

In a very advantageous embodiment, such as in 2 as in 3a and also in 3b is the non-step-like contour or geometry ( 11 ), alternatively its vertex (S), approximately to the width of the bearing gap ( 10 ), from the distance sensor ( 4 ), in particular from the bearing gap end (A) of the distance sensor ( 4 ), spaced.

It is also possible within the meaning of the invention to apply to a non-step-like contour ( 11 ) without vertex (S), such as in 5a and 5b shown. This is particularly recommended when the area to be sensed (B) in the vicinity of a paragraph or an edge of a bearing ring ( 6 ; 7 ), for example in the vicinity of rolling elements ( 8th ) or between two rows of rolling elements ( 8th ).

The direct distance of the non-step-like geometry or contour ( 11 ) from the distance sensor ( 4 ), ie in particular of its bearing gap-side end (A), in any case, for example, at least 0.20 mm, possibly even be in a wide range between 0.20 and 9.5 mm, ideally even between 1.0 mm and 4.0 mm.

It is further found that according to the invention and advantageously the distance sensor ( 4 ) always in the non-stepped contour or Geometry ( 11 ) opposite bearing ring ( 6 ) is introduced.

3a such as 3b and 5a and also 5b have a region (B) in which the non-step-like contour or geometry ( 11 ) is available. This area (B) is preferably designed so spacious that between the bearing gap-side end (A) of the distance sensor ( 4 ) at least 0.2 mm or 3.5 mm distance to non-step-like contour or geometry ( 11 ) in the opposite bearing ring ( 6 ) can be maintained.

Each distance sensor ( 4 ) is advantageously along its longitudinal axis or longitudinal extent (L) in each means ( 9 ) to the sensor receptacle, preferably a machined sensor bore ( 9 ) brought in.

This introduction of at least one distance sensor ( 4 ) is done in practice by joining or pressing or screwing - alternatively even by gluing and / or by means of locking pin.

This means ( 9 ) to the sensor receptacle, for example, the sensor bore or sensor recess, can be produced by machining or non-cutting metal-working, for example, by casting production technology or cold-forming technology or bumping or Scherfertigungstechnologie.

It has proved to be particularly advantageous if a plurality of distance sensors ( 4 ) per moment or (large) rolling bearing ( 1 ) or rotary joint ( 1 ) are present, for example, as in 6a and or 6b shown.

Accordingly, three distance sensors ( 4 ) in a bearing ring ( 7 ) and with their bearing gap-side ends (A) in the direction of the other bearing ring ( 6 ) - at least always in the direction of the storage gap ( 10 ), Where, for example, three distance sensors ( 4 ) can be spaced apart from each other clockwise by 120 ° each - or, for example, four distance sensors ( 4 ) can be spaced from each other clockwise by 90 °. Letz mentioned embodiment according to 6a has opposite 6b the advantage that a sensor ( 4 ) per circle sector, whereby the measurement technique receives more evaluable data than if only three sensors ( 4 ) per moment or (large) rolling bearing ( 1 ) or rotary joint ( 1 ) available.

According to the teaching of the invention ( 1 ) is the bearing gap ( 10 ), alternatively the area (B), between distance sensor ( 4 ), in particular from the bearing gap end (A) of the distance sensor ( 4 ), and the non-step-like contour or geometry ( 11 ) filled with grease or oil or lubricant, in particular to promote the transmission of sound waves or even ultrasonic waves, because it is known from physics ago that sound waves or even ultrasonic waves in fluid media, selsbt in viscous fluid media, have a higher propagation velocity than in air media.

In this respect, a filled with oil or lubricant bearing gap ( 10 ) within the meaning of the invention ( 1 ) a "ventilated", ie an "air-filled", bearing gap ( 10 ) to be preferred. However, if we do not use a method which measures or detects sound waves, but instead uses, for example, a purely inductive non-contact distance measuring method, it is irrelevant whether the bearing gap (FIG. 10 ) is filled with fluid (especially oil and / or lubricant) or is not filled with oil / lubricant - ie only "filled with air" is.

The invention works particularly well if several distance sensors ( 4 ) in a common 9 ) are inserted to the sensor receptacle or pressed or screwed. It is advantageous if, for example, a first distance sensor ( 4 ) measures or senses or detects radial (Δv) displacement or the radial (Δv) distance and a second distance sensor ( 4 ) Measures the axial (Δs) distance or the axial displacement (Δs) or sensed or detected.

Thus, the user of the invention ( 1 ) likewise qualified displacement and / or distance data of the two bearing rings ( 6 ; 7 ) Both in the axial and in the radial direction, in particular with regard to the wear and / or loading direction.

Basically, the moment or (large) rolling bearing ( 1 ) or the rotary joint according to the invention ( 1 ) such that the axial extension of the non-stepped contour or geometry ( 11 ) Does not exceed 20.0 mm and / or the radial extent of the non-stepped contour or geometry ( 11 ) Does not exceed 10.0 mm. Practical and therefore particularly advantageous, for example, this non-stepped contour or geometry ( 11 ) ramped ( 11 '' ) - is approximately at an angle between 5 ° and 95 °, preferably between 30 ° and 65 °, in particular by about 45 °, preferably wherein preferably in the end point of the ramp, the vertex (S) is formed.

The aforementioned additional body ( 12 ) is ideally made of a metallic material, for example of a ferromagnetic material, for example, as a the distance sensor ( 4 ), in particular the bearing gap-side end (A) of the distance sensor ( 4 ), opposite measuring reference body to act.

In a further embodiment of the invention, the additional body ( 12 ) may be embodied as an annular coil or conductor loop, preferably which is electrically isolated from its bearing ring by means of an electrically insulating material, such as ceramic or elastomeric material or plastic material or cardboard or paper material.

The teaching of the invention ( 1 ) further provides that the non-step-like contour or geometry ( 11 ), or even, alternatively, the auxiliary body ( 12 ), annularly attached to at least one point of the him / him housing bearing ring or is introduced.

In this case, this attachment or introduction can even be ring segment-shaped, so that the non-step-like contour or geometry ( 11 ), or alternatively the auxiliary body ( 12 ), in at least one ring segment of the bearing ring ( 6 ; 7 ) is applied or introduced, preferably insoluble or introduced, alternatively glued or soldered or even pressed.

Coming back to the aforementioned vertex ( 12 ) it should be noted that the same is the maximum 11 * ) of the non-step-like contour or geometry ( 11 ) Are defined. This survey can also be performed negative (notch). Due to the assumed notch effect, however, the positive case is preferable. In order to assemble the invention ( 1 ) despite such a survey ( 11 * ) in practice, should be at most about four-fifths of the width of the bearing gap ( 10 ), for example, however, at most 7.5 mm.

LIST OF REFERENCE NUMBERS

1

Torque or (large) rolling bearing or rotary joint

2

drilling

3

drilling

4

distance sensor

5

groove

6

bearing ring

7

bearing ring

8th

rolling elements

9

Means, e.g. B. Sensor bore

10

bearing gap

11

non-step-like geometry

11 '

V-shaped contour

11 ''

ramp-shaped contour

11 '' '

rounded contour

11 *

survey

12

additional body

13

gap seals

14

poetry

.DELTA.s

distance

.DELTA.v

shift

A

bearing gap-side end

B

Area

G

slewing bearings

L

longer extension

S

vertex

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 0922870 B1 [0005, 0014, 0015, 0017]

Claims (15)

Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) comprising: - at least one distance-sensing sensor (preferably measuring or detecting by inductive method), alternatively measuring or detecting by means of sound waves or eddy current methods, optionally measuring a distance sensor by means of capacitive method ( 4 ), At least temporarily, but preferably continuously, measuring or sensing or detecting the axial distance (Δs) or the displacement and / or the radial distance or the displacement (Δv) of at least two bearing rings ( 6 ; 7 ) relative to each other in their bearing gap ( 10 ), Wherein the at least one distance sensor ( 4 ) via an appropriate means ( 9 ), preferably via one sensor bore per distance sensor ( 4 ), into one of the bearing rings ( 6 ; 7 ) and with respect to a non-step-like contour or geometry ( 11 ) is fixed or introduced, wherein the non-stepped contour or geometry ( 11 ) either a V-shaped contour ( 11 ' ) or a ramp-shaped contour ( 11 '' ), for example with a continuous slope, or a rounded contour ( 11 ''' ), possibly similar to a Kuhle, or a survey ( 11 * ), for example, which by additional body ( 12 ) is formed. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1, characterized in that the non-stepped contour or geometry ( 11 ) in the distance sensor ( 4 ) opposite bearing ring ( 6 ; 7 ) is located. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or according to the preceding claim, characterized in that at least one vertex (S) of the non-stepped contour or geometry ( 11 ) characterizing the location of the maximum elevation of the non-step-like contour or geometry ( 11 ) opposite to this contour ( 11 ) bearing ring ( 6 ; 7 ). Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or according to the preceding claim, characterized in that the non-stepped contour or geometry ( 11 ), alternatively its vertex (S), approximately to the width of the bearing gap ( 10 ), for example by at least 0.20 mm, optionally by between 0.20 and 9.5 mm, ideally even by between 1.0 mm and 4.0 mm, from the distance sensor ( 4 ), in particular from the bearing gap end (A) of the distance sensor ( 4 ), or that of the non-stepped contour or geometry ( 11 ) opposite bearing ring ( 6 ; 7 ), is spaced. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or according to one of the two preceding claims, characterized in that the non-stepped contour or geometry ( 11 ), alternatively their vertex (S) to exactly the width of the bearing gap ( 10 ) minus or in addition an area (B), for example the size of (B) = +/- 0.2 mm to (B) = +/- 3.5 mm, from the distance sensor ( 4 ), in particular from the bearing gap end (A) of the distance sensor ( 4 ), or that of the non-stepped contour or geometry ( 11 ) opposite bearing ring ( 6 ; 7 ), is spaced. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or one of the preceding claims, characterized in that in each case a distance sensor ( 4 ) along its longitudinal axis or longitudinal extent (L) in each case a means ( 9 ) to the sensor receptacle, preferably a machined sensor bore ( 9 ), inserted or pressed in or screwed in, alternatively adhesively bonded and / or provided by means of locking pin, whereby alternatively this means ( 9 ) was made without cutting metal-processing, for example, by casting production technology or cold-forming technology or shock or shear manufacturing technology. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or one of the preceding claims, characterized in that the bearing gap ( 10 ), alternatively the area (B), between distance sensor ( 4 ), in particular from the bearing gap end (A) of the distance sensor ( 4 ), and the non-step-like contour or geometry ( 11 ) is filled with grease or oil or lubricant, in particular to promote the transmission of sound waves or even ultrasonic waves. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) as an alternative to the preceding claim, characterized in that a plurality of distance sensors ( 4 ) in a common 9 ) are inserted or pressed or screwed in to the sensor receptacle, for example, wherein a first distance sensor ( 4 ) measures or senses or detects radial displacement (Δv) and a second distance sensor ( 4 ) measures or senses or detects axial distance (Δs). Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or one of the preceding claims, characterized in that the axial extension of the non-stepped contour or geometry ( 11 ) Does not exceed 20.0 mm and / or the radial extent of the non-stepped contour or geometry ( 11 ) Does not exceed 10.0 mm, for example where this non-stepped contour or geometry ( 11 ) ramped ( 11 '' ) is executed at an angle between 5 ° and 95 °, preferably between 30 ° and 65 °, in particular by about 45 °, preferably wherein in the end point of the ramp, the vertex (S) is formed. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or one of the preceding claims, characterized in that at least one additional body ( 12 ) consists of a metallic material, for example of a ferromagnetic material, for example, further as a the distance sensor ( 4 ), in particular the bearing gap-side end (A) of the distance sensor ( 4 ), opposite measuring reference body to act. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or one of the preceding claims, characterized in that the non-stepped contour or geometry ( 11 ), alternatively the additional body ( 12 ), annularly circumferentially at at least one point of the him / him housing bearing ring ( 6 ; 7 ) is mounted or inserted, alternatively even ring-segment-shaped in at least one ring segment of the bearing him housing bearing ring ( 6 ; 7 ) is applied or introduced, preferably insoluble or introduced, alternatively glued or soldered or even pressed. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or one of the preceding claims, characterized in that the survey ( 11 * ) of the non-step-like contour or geometry ( 11 ) at most about four-fifths of the width of the bearing gap ( 10 ), for example at most 7.5 mm, but preferably at most about three quarters of the fifth of the width of the bearing gap ( 10 ), but ideally less than 3.0 mm. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or one of the preceding claims, characterized in that an additional body ( 12 ) is designed as an annular coil or conductor loop, preferably which opposite to the bearing ring ( 6 ; 7 ), electrically isolated by means of an electrically insulating material such as ceramic or elastomeric material or plastic material or cardboard or paper material. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 and designed as a tapered roller bearing or as a ball bearing, alternatively as a cylindrical roller bearing, alternatively as a needle bearing, alternatively as a barrel roller bearing, further comprising at least one annular circumferential row with rolling elements ( 8th ) and installed or mounted in a machine or plant assembly, for example in a tunnel boring machine or in a construction machine or in an agricultural machine or in a crane or in an aerial work platform or in a wind or tidal power plant or in a medical apparatus for rotary relative adjustment several bearing rings ( 6 ; 7 ) into each other, for example, for relative adjustment of a carriage of a military vehicle or alternatively to the relative adjustment of a water extinguishing gun of a fire engine or for relative adjustment of the rotor of an energy power plant, possibly even for relative adjustment of a pivot axis of a solar or photovoltaic system. Moment or (large) rolling bearings ( 1 ) or rotary joint ( 1 ) according to claim 1 or according to the preceding claim comprising a rotary drive or swivel drive device equipped therewith and / or a worm gear system associated with such a swivel drive or swivel drive device.

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