WO2017021768A1

WO2017021768A1 - Rotary connection

Info

Publication number: WO2017021768A1
Application number: PCT/IB2016/001057
Authority: WO
Inventors: Hubertus Frank
Original assignee: Imo Holding Gmbh
Priority date: 2015-08-04
Filing date: 2016-07-27
Publication date: 2017-02-09
Also published as: DE102015009865B4; ES2691639A2; WO2017021768A9; DE102015009865A1; DK180487B1; DK201870128A1; ES2691639B2; ES2691639R1

Abstract

At least one first annular connection element of the annular connection elements is equipped with a circumferential toothing on the connection element surface region facing the gap, wherein a toothed wheel meshes with the toothing. The rotational axis of the toothed wheel is parallel to the main rotational axis of the rotary connection and is received and/or mounted in a second annular connection element of the annular connection elements (2, 3). The circumferential toothing of the first annular connection element together with at least one of the connection element raceways for rolling bodies (39, 40, 41) that roll along the raceways is produced by machining and/or shaping a first main part, and at least one chamber (28) for receiving a toothed wheel that meshes with the toothing and/or at least one bore, bearing, or bearing depression for the rotational axis of a toothed wheel (29) that meshes with the toothing in a second annular connection element or a part thereof together with at least one of the connection element raceways for rolling bodies that roll along the raceways is produced by machining and/or shaping a second main part.

Description

rotary joint

The invention is directed to a rotary joint with two annular connection elements for connection to a machine of the plant part, chassis or foundation, which are concentrically arranged to form a gap running around concentric with each other, wherein at the two annular connection elements at their the gap facing surface areas respectively at least one raceway is provided, on each of which roll a number of rolling elements, so that the two annular connection elements about a main axis of rotation of the rotary connection against each other are rotatable, and wherein at least a first of the annular connection elements at its the gap facing surface area running around a toothing is provided, which meshes with a gear whose axis of rotation is parallel to the main axis of rotation of the rotary joint and received in a second of the annular connection elements and / or stored.

Slewing rings are often driven by a worm, resulting in the structure of a worm gear. However, such arrangements have a rehabilitation of disadvantages: worm gears have an extremely large gear ratio, and with increasing diameter of the toothed and driven by the worm, annular connection element, this ratio increases more and more, because the speed ratio ü _{s of} a worm gear with a single-flight worm is at _s = n _A : ns = 1: z _A , where z represents the number of teeth of the toothed connection element. Thus, the achievable on the sprocket to be adjusted rotational speed is extremely reduced. For example, if the foot of a rotor blade of a wind turbine has a diameter of 3 m, its circumference is about 9.42 m. With a total tooth width of, for example, 2 cm, not less than z _A = 471 teeth are produced along such a circumference. In this case, ü _s = 1: 471 = 0.002. Would the worm of a motor with a maximum speed of n _{s, max} = 600 rpm = 10 U / sec. driven, the maximum speed n _{r, m} ax would be at the rotor blade bearing even at n _{A, max} = n _s, max ^* ü _s = 10 U / sec. ^* 0.002 = 0.02 U / sec. This means that a single revolution would take about 50 seconds. Although this may seem little for the adjustment of a sheet bearing a wind turbine. However, ever-increasing wind turbines have the consequence that the rotor blades in the course of a revolution through different layers of air above the ground, the blade tips move, for example, between heights between 50 m and 200 m. Good regulations therefore try to create an optimum blade pitch for the different wind speeds at different heights above the ground. In addition, if possible, even in the event of sudden gusts of wind, it is necessary to provide control engineering compensation in order to protect the already heavily loaded blade bearings from overloading.

If, therefore, one wishes to achieve an optimal transmission ratio in the course of such applications in rotary joints with a large diameter of the connecting elements, worm gears with a single-flight worm are unsuitable for this purpose. However, multi-start screw require a helical toothing on the connection element, which can be produced only with great effort.

The invention is therefore based on an arrangement in which a gear is used instead of a worm. This gives you much better options to adjust the gear ratio. For in this case applies to the gear ratio: ü _z = n _A : n _z = z _z : z _A , where z _{A is} the number of teeth of the toothed connection element and z _z, the number of teeth of the meshing gear. For a gear with a sprocket diameter about 6.4 cm results in a circumference of 20 cm, and with a tooth width of 2 cm so a number of teeth z _z of z _z = 10. For the above example of a sprocket with 471 teeth is then the Transmission ratio at _{z z} = z _z : z _A = 10: 471 ^Ä 0.02. At a maximum Engine speed of n _s , _m ax = 600 rpm = 10 U / sec. results in a maximum speed n _r , _m ax at the rotor blade bearing even at n _A , _m ax = n ₂ , _max ^* ü _z = 10 U / sec. ^* 0.02 = 0.2 U / sec. Thus, a single revolution would only take about 5 seconds. In addition, a gear shorter bearing distances of a higher speed is capable of a screw. Of course, a rotor blade bearing will generally never make a full turn; but it depends much on the short-term achievable speed, which is significantly slower in a worm gear than in a gear transmission. Incidentally, a worm gear is almost or completely self-locking, and therefore, for many applications where a flexible response to unforeseeably externally applied (disturbing) forces such as gusts of wind, etc., is required. With a worm gear, such external (interfering) forces are completely absorbed by the worm bearing, which can be destroyed in the process. For precisely this reason, a dynamic speed change of a worm shaft should be limited as possible, as from an abrupt start due to inertia or other braking torques could also result in an overload of the worm bearing or even the worm thread itself.

This disadvantage does not arise in gear transmissions because there lack of self-locking all intermeshing gears can dodge in a suitable direction of rotation and therefore threatens no overloading of transmission parts.

So if you start from driven by pinion or gear rotary joints, it has already been tried to surround the radially outer connecting element with an outer toothing and to arrange the drive motor for a meshing pinion via an outwardly projecting flange on the inner ring. However, this does not normally provide sufficient encapsulation of the gear and the toothing; In addition, the mounting flange engages over the outer ring on one of the two end faces, so that at the respective Front side no determination of the outer ring is possible, which further restricts the design possibilities.

According to the invention, therefore, preference is given to an arrangement wherein the meshing engagement between the all-round toothing of a connection element and a gear meshing therewith takes place directly in the region of the gap between the two connection elements. This has the consequence that the relevant drive gear can be mounted in an annular connection element and directly drives the other connection element. It is therefore not necessary that a flange connected to the inner connection element surrounds the outer connection element on one side. It is also possible to arrange the gear within a chamber which is open only to the gap on the one hand where the meshing engagement with the other connecting element takes place, and to the shaft of the drive motor on the other hand, from where the drive energy comes from, but otherwise outwardly closed is. The one opening can be sealed, for example by arranged at the gap openings in the region of the upper and lower end faces of the rotary joint, all-round seals, the other opening by flanging or otherwise securing the drive motor, possibly with inserted seal. Thus, such an arrangement is a fully enclosed transmission, in particular because possibly existing (rolling) bearings of the movable transmission parts, namely the toothed connection element on the one hand and the gear meshing therewith, are completely integrated into the transmission. As a result, an improved precision can be achieved, in particular when the bearing of the gear wheel takes place directly inside the untoothed connection element and therefore the remote mounting of the output shaft of a flanged drive motor is not attempted. Because with a bearing of the gear on the untoothed connection element there is no lateral tolerance as in the flanging of a motor, the other hand, due to the considerable play between eyelets on the one hand and these sweeping screws comparatively large inaccuracies in itself. The invention further provides that at least one chamber for receiving a meshing with the toothing gear and / or at least one bore or bearing or bearing recess for the axis of rotation of a meshing with the toothed gear in a second annular connection element or a part thereof together with at least one is made of its raceways in the gap for rolling along it rolling elements, or together with several or all of its tracks in the gap rolling rolling elements along it, by machining and / or shaping a common, preferably untoothed body (are), in particular by preferably cutting Processing the same. This results in a precise adjustment of the gear disposed within the chamber relative to the storage for the other, toothed connection element, and thus also with respect to the arranged on that connection element toothing. Thus, a high precision of the intermeshing teeth on the toothed connection element on the one hand and on the gear wheel meshing therewith can be ensured on the other hand, as otherwise can typically only be achieved within a completely encapsulated transmission. In a further development of the invention it can be provided that the all-round toothing of the first annular connection element together with at least one of its raceways in the gap for it rolling rolling elements along, or together with several or all of its tracks in the gap for rolling rolling elements along it , is made by machining and / or shaping a first body (are), in particular by preferably machining the same. By such a measure, the storage precision is further increased because separate race rings completely eliminated. It is within the scope of the invention that the toothed connection element and / or the gear meshing therewith is end-toothed and / or straight-toothed. Such gears can be produced with the least possible effort but in the realization of an involute a constant torque transmission.

If there are several bearings or rows of rolling elements, the desire is to arrange them as far apart as possible in the axial direction; On the other hand, the height of a rotary joint between the two end faces should often be as small as possible. To meet these requirements alike, the all-round teeth of the first or toothed, annular connection element between two raceways for each row of rolling elements can be arranged.

In particular, when the toothing of the toothed connection element is located between two rows of rolling elements, the drive shaft of a meshing with the toothed gear must sit radially as far as possible outside. In order to meet this requirement, the invention recommends that the all-round toothing of the first or toothed, annular connection element is located on a region of the same connection element that is raised in the radial direction relative to an adjacent raceway. Thus, the gear - and consequently also the drive shaft - relative to the bearing or the rolling elements radially offset to the outside, where the drive shaft collision can be performed on the bearing past.

One possibility for carrying out the above inventive concept is that the all-round toothing of the first or toothed, annular connection element is located on an end face of a circumferential federal whose flanks are formed as raceways for each row of rolling elements. In such a case, the various boundary surfaces of such a collar can all be used in a particularly optimized way: its flanks are particularly suitable for transmitting axial forces between the connection elements, namely rolling elements rolling along them, while the front side is suitable as a particularly exposed surface for the introduction of torques is, namely on the tooth flanks of a circumferentially arranged row of teeth. For example, so that a connection element can be positioned and mounted with a completely running collar within a second connection element, such that the collar is encompassed on its two flanks, the invention recommends that the second or untoothed connection element is divided into two superposed rings, which along a joint or separation surface abut. These sub-rings can therefore be temporarily removed from each other for assembly and then reassembled around the collar.

This makes it possible that the second or untoothed connection element has an approximately C-shaped cross-section with an all-round, groove-shaped depression in the region of the gap. In this depression area, for example, a covenant or other, all-round projection of the toothed element engage.

Further advantages result from the fact that the chamber is located in the second or untoothed connection element at the level of a groove-shaped depression in the region of its lateral surface facing the gap and is open towards the latter. In order for a arranged within this chamber gear is positioned in direct contact with a toothing on engaging in the groove-shaped recess federal government.

The chamber in the second or untoothed connection element should be open in the radial direction, relative to the axis of rotation of the gear, along a first center angle α to the gap, for example along a first center angle α> 60 °, preferably along a first center angle α> 75 °, in particular along a first center angle α> 90 °. This opening should be large enough to accommodate the meshing engagement between the pinion and gear and the teeth of the splined terminal. If the untoothed ring is not divided, must through this opening, the pinion or gear in the Chamber before assembly with the dazhnten connection element.

On the other hand, the chamber should be limited in the second or untoothed connection element in the radial direction, with respect to the axis of rotation of the gear along at least a second center angle ß of a preferably rotationally symmetrical lateral surface, for example along a second center angle ß> 120 °, preferably along a second center angle ß> 150 °, in particular along a second center angle ß> 180 °. This lateral surface serves to encapsulate the chamber and thus the entire transmission, so that on the one hand dust and Schmutpartikel be kept away and on the other hand, a lubricant is held in the transmission. The invention can be further developed such that the rotationally symmetric region of the lateral surface of the chamber in regions follows the shape of the lateral surface of a hollow cylinder, a hollow barrel or a hollow calotte. While the course of the lateral surface of the chamber is predetermined by the rotational symmetry of the pinion or toothed wheel enclosed by it, the shape of the cross section through this lateral surface can be adapted to the enclosed toothed wheel or pinion. Thus, a gear made of a cylindrical base body may be surrounded by a hollow cylindrical surface, a machined from a spherical or dome-shaped base gear, the longitudinal curvature of the curvature corresponds in the circumferential direction, may be enclosed by a hollow-calotte-shaped lateral surface, and a gear with a slightly curved in its axial direction envelope, wherein the longitudinal curvature of the curvature does not correspond in the circumferential direction, of a hollow-cylindrical shell surface. Preferably, the lateral surface of the chamber in the second or untoothed connection element in the radial direction, based on the axis of rotation of the gear along at least one further center angle range γ a straight course, for example, from the edges of the opening of the chamber to the Gap up to the beginning of the rotationally symmetric boundary surface. Theoretically, the rotationally symmetrical lateral surface section could extend as far as the edge-side opening in the chamber, so that the following applies: α + β = 360 °. However, in this case, the opening is almost always less than 180 °, so that a gear can not be applied through this opening into the chamber. Such an embodiment with α + β = 360 ° is therefore feasible at best in a divided into sub-rings, untoothed connection element. For other embodiments, at least one transition area is required so that the opening is wide enough to feed a gear or pinion into the chamber.

A largely or completely symmetrical arrangement of the chamber with a sufficiently large for the installation of a gear opening is obtained when the chamber in the second or untoothed connection element in the radial direction, based on the axis of rotation of the gear along at least a third center angle γ-ι and a fourth center angle γ ₂ is limited by flat surfaces, for example along a third center angle Yi> 15 ° and along a fourth center _angle γ ₂ > 15 °, preferably along a third center _angle γ _Ί > 30 ° and along a fourth center _angle γ ₂ > 30 °, in particular along a third center angle γι> 45 ° and along a fourth center angle γ ₂ > 45 °. Overall, then: α + β + γι + γ ₂ = 360 °. A typical design would be for example: α = 90 °; β = 180 °; γι = γ ₂ = 45 °. Then, the two flat surfaces would be parallel to each other and, together with the top and bottom of the chamber would form a shaft with a rectangular cross-section, through which a gear can be pushed to its preferred position.

In order to allow the subsequent installation and removal of the gear in and out of the chamber without disassembly of the untoothed connection element, should be from the chamber opening in the region of the gap up to the opening facing away from this region of the chamber, but at least up to a mouth of a hole or other recess for a drive shaft of the gear, a shaft extending whose clear width in the entire area always the same or greater than a maximum cross section through the gear to be built in or out along its axis of rotation or axis of symmetry. The sides of this shaft can finally pass without kink or step in the adjacent surfaces of the chamber, in particular in the top and bottom on the one hand and in a concave lateral surface area on the other. If the installation and removal of a gear is to take place through such a shaft, the shaft may indeed have a greater width than the relevant gear cross section along the rotational or rotational axis of symmetry, but not smaller than that gear cross section.

Another, preferred design rule states that the chamber is limited in the second or untoothed connection element in the axial direction of a flat top and a parallel, planar bottom. Preferably, these planes extend parallel to a main plane of the bearing, which is penetrated vertically by the main axis of rotation of the rotary joint. They are in turn penetrated vertically by the drive axle of the gear. Thus, the main plane of the meshing with the toothing on the toothed connecting element gear is given, and in such case, the latter can rotate without contact and thus smoothly within the chamber.

In the area of the top and / or the bottom of the chamber should be provided for a gear driving the axis axis. This storage (s) is (are) thereby arranged in the immediate vicinity of the gear, so that it is optimally guided. This bearing (s) takes over (take over) all forces acting on the gear and tilting moments, except for a torque to be introduced on the toothed connection element. Exactly this is the other hand applied by a drive motor and passed through the drive shaft without any relative displacement of the same directly to the gear, and initiated by that desired to the toothed connection element. An optimized for this purpose storage for a gear driving shaft is designed as a radial bearing. A radial bearing ensures that there is no radial relative movement between the gear and the untoothed connecting element, and in the case of a precise bearing between the two connecting elements keeps the rotation axis of the gear or its drive shaft thus a defined, constant distance to the main axis of rotation of the bearing and thus finally against the teeth of the toothed connection element. It thus prevail permanently for the meshing intervention optimal conditions, resulting inter alia, the desired longevity of the arrangement according to the invention results.

In order to create space for the chamber according to the invention, the second or untoothed connection element on its side facing away from the gap lateral surface in the region of the chamber to a thickening in the form of a radial extension. The maximum radial thickness D _{max of} the untoothed connection element in the region of this thickening can be estimated from the diameter d of the gear received in the chamber, the minimum radial thickness extension D _{min of} the untoothed connection element at a different location thereof, and the wall thickness W of the chamber housing in the region of its maximum extent D _max according to the following condition:

Dmax> d + W - D _min , or according to the more stringent condition:

In the context of a preferred embodiment, a recess or bore for receiving a drive shaft for the gear meshing with the toothing extends to a flat outer surface of the second or untoothed connection element, so that a torque can be introduced into the drive shaft from outside the rotary connection. Since the introduction of a torque is generally not possible without the derivation of an opposing moment in the untoothed connection element of the rotary joint or in an associated machine or plant part, chassis or foundation, the invention further provides that in the region of the mouth of the recess or bore for receiving a drive shaft for meshing with the toothed gear in a flat outer surface of the second or untoothed connection element one or more means for fixing the housing of a drive motor are provided, for example one or more, preferably annularly distributed around the mouth mounting holes. By attaching, in particular screwing, a motor housing whose stator is fixed, and the rotor, in contrast, can apply the desired torque.

In the context of a preferred embodiment of the invention, the mouth of the recess or bore for receiving a drive shaft for meshing with the toothed gear opposite, flat outer surface of the second or untoothed connection element is designed as its connection surface for abutment with a machine or plant part, chassis or foundation. Consequently, there is no drive motor to be provided on this end face intended for mechanical connection to a machine or system part, chassis or foundation, and there is therefore sufficient space there for the machine or system part in question, etc. available.

The connection with a machine or plant part, chassis or foundation to be connected is made possible by fastening means being provided in the flat connection surface of the second or untoothed connection element, preferably fastening bores arranged in a circle around the main axis of rotation of the rotary connection, in particular blind-hole bores provided with internal threads. If the axial length of such blind holes is smaller than the distance between the Chamber and the connection surface of the untoothed connection element, such screw connections or holes can be provided at uniform intervals completely along the circumference, ie also in the region of

Chamber or caused by those, radial thickening of the untoothed connection element.

If the connection surface of the second or untoothed connection element is designed to be raised in the axial direction relative to the adjacent end side of the first connection element, it is ensured that the toothed connection element is not attached to the mounting surface when fixed to a planar mounting surface of a machine or system component, chassis or foundation along stretches.

To protect against penetrating dust or dirt particles, the gap in the region of its mouths in the region of the top and bottom of the rotary joint can be sealed.

It is within the scope of the invention that the gap in the sealed area is completely or partially filled with a lubricant, preferably with lubricating grease. This ensures equally for optimum lubrication of rolling between the raceways on the two connecting elements rolling elements, as well as for optimizing the meshing engagement, and possibly also for lubrication of integrated bearings of a drive shaft of the gear.

In the context of a first embodiment of the invention, the all-round toothing is arranged on the inner and / or concavely curved lateral surface of the radially outer connection element. This means that the first, toothed connecting element is arranged radially inside the second, untoothed, the chamber (s) for receiving engaging in the toothed gears connecting element. With such a construction, the drive motors coupled to the toothed wheels meshing with the circumferential toothing are easily accessible from outside. In addition, it is also possible for the all-round toothing to be arranged on the outer and / or convexly curved jacket surface of the radially inner connecting element. In this case, the first, toothed connection element is located radially outside the second, untoothed, the chamber (s) for receiving engaging in the toothed gears connecting element. Such an arrangement has the advantage that the drive motors coupled to the toothed wheels meshing with the circumferential toothing are protected against external influences inside the rotary joint or a connected machine or plant part.

Finally, it is the teaching of the invention that several, each open to the gap open chambers for receiving a meshing with the toothed gear in the second, untoothed, annular connection element or in at least one annular part of the same incorporated or molded, preferably in equidistant Distributed intervals over the circumference of the toothing, ie offset from each other at equal intermediate angles. By such an arrangement, the torque to be applied by the rotary joint can be multiplied and, moreover, a higher symmetry of the torque introduction can be achieved, that is, without causing radial force components through the torque introduction elsewhere in the bearing. Further features, details, advantages and effects on the basis of the invention will become apparent from the following description of a preferred embodiment of the invention and from the drawing. Hereby shows:

Fig. 1 is a plan view of a rotary connection according to the invention;

Figure 2 is a section through the rotary joint of Figure 1 along the line II - II. Fig. 3 is a representation corresponding to Figure 2 of another embodiment of the invention with disassembled Antreibsmotor.

Fig. 4 is a view corresponding to FIG. 3 a modified again

Embodiment of the invention; such as

Fig. 5 is a corresponding to FIG. 3 representation of a further modified embodiment of the invention. The rotary joint 1 of Fig. 1 is designed for use as an adjustable blade bearing for a wind turbine, but can also be used for other applications. The same applies to the embodiments of rotary joints V according to FIGS. 3 and 1 "according to FIGS. 3 and 1" constructed according to the same basic principle but deviating in particular design features thereof according to FIG. 4.

It can be seen in Fig. 1, the annular or centerless arrangement.

As can be seen more clearly in FIG. 2, the rotary joint 1 essentially comprises two annular connecting elements 2, 3 which each have at least one, preferably two, flat end faces 4, 5, 6, 7, of which at least one each serves as a connecting surface 4, 7 serves, for connection to a machine or plant part, chassis, foundation od. Like. In order to allow such a connection, each pad 4, 7 of a plurality of annularly distributed mounting holes 8, 9 passes through. 2, these can be through holes 8 or blind holes 9 with internal thread 10. Darin screws can be inserted and / or anchored, which also bore holes or other recesses in the relevant machine or system part, Pass through chassis or foundation and thereby set the relevant connection element 2, 3 at that. From Fig. 2 further shows that each a preferred connection surface 4, 7 is formed raised with respect to the adjacent end face of the respective other connection element 2, 3. Both connecting elements 2, 3 are arranged radially in one another, concentric with a common central axis 11, which passes through the main ring planes or the planes of the end faces 4, 5, 6, 7 vertically.

Between the mutually facing lateral surfaces 12, 13 of both connection elements 2, 3 there is a gap 14 which prevents direct contact between the two connection elements 2, 3.

In order to ensure a completely uniform width of the gap 14, rolling elements 39, 40, 41 roll off within the gap 14.

Furthermore, it can be seen that a first connection element 2 - in the illustrated embodiment, the radially inner, which is by no means mandatory, but just as well could be the radially outer - has a circular geometry, ideally with a - apart from the mounting holes 8 - unchanged Cross-section along its entire circumference.

In the region of its lateral surface 12 facing the gap 14, this first connection element 2 has an all-round toothing 15. The toothed connection element 2 thus has a circular geometry, ideally with a cross section 16, whose outer periphery 18 formed by the two end faces 4, 5, the lateral surface 12 facing the gap 14 and the lateral surface 17 facing away from the gap 14, are circumferentially about the axis of rotation 11 does not change. As can be seen from Fig. 1 further, the second connection element 13 has - in the illustrated embodiment, the radially outer, which is by no means mandatory, but just as well could be the radially inner - a geometry deviating from the ideal circular shape, ie with a cross-section 19 changing in the circumferential direction about the axis of rotation 11.

This manifests itself in such a way that the course of the lateral surface 20 of the untoothed connecting element 3 facing away from the gap 14 is composed of a plurality of different sections:

In a first region 21, which extends over a center angle α around the rotation axis 11 of 180 ° or more, preferably over a center angle α of 210 ° or more, in particular over a center angle α of 240 ° or more, the peripheral surface has a rotationally symmetric Gestalt, and follows there, for example, a cylinder surface.

Although in a second region 22, the lateral surface 20 also has a rotationally symmetrical shape, for example a cylinder jacket-shaped shape which is concentric with an axis 23 which is parallel to the main rotational axis 11 but eccentrically arranged. This region 22 extends over a center angle β about the eccentric axis 23 of 180 ° or less, preferably over a center angle β of 150 ° or less, in particular over a center angle β of 120 ° or less. In general, α + β = 360 °.

The region 22 of the lateral surface 20 which extends in an arc shape around the eccentric axis 23 has a smaller radius of curvature r in relation to the radius of curvature R of the lateral surface portion 21 bent around the main axis 11 of the rotary joint 1:

R> r.

These two arcuate portions 21, 22 of the gap 14 facing away from lateral surface 20 of the untoothed connection element 3 are connected by preferably straight stretched or flat lateral surface portions 24, 25th

With respect to a connecting line 26 between the two axes 11, 23, the two straight stretched or even flat lateral surface portions 24, 25 are mirror images of each other. That is, both converge toward each other along the connecting line 26, from the main axis of rotation 11 in the direction of the eccentric axis 23. In the transition regions to the respective subsequent, curved portions 21, 22, the straight or even lateral surface portions 24, 25 extend tangentially the center 11, 23 of the respective curved lateral surface portion 21, 22, so that the outer surface 20 is ideally free of steps or other discontinuities. However, it has a radial extension 27 towards the eccentric axis 23.

In this radial extension 27 of the untoothed connection element 3 is a chamber 28 for a gear 29, the teeth 30 mesh with the teeth 15 of the toothed connection element 2. From the chamber 28 extends a bore 31 or other, elongated recess along the eccentric axis 23 to an end face 6 of the untoothed connection element 3, preferably to the not serving as a terminal surface 7 end face 6 thereof. There are a plurality of annularly distributed around the eccentric axis 23 arranged holes, preferably provided with internal blind blind holes, to which a motor 32 is flanged, preferably such that its Abtiebswelle 33 extends concentrically to the eccentric axis 23. If the motor 32 is a geared motor, it would be mounted such that the output shaft of the transmission is concentric with the eccentric shaft 23. Either the output shaft 33 of the motor 32 itself or a shaft rotationally coupled thereto for extension extends through the bore 31 or through the other, elongate recess up to the chamber 28 for the gear 29.

The bore 31 or other, elongated recess opens approximately centrally in an upper or lower end face 34 of the chamber 28. The bore 31 or other, elongated recess passing through (output) shaft 33 does not terminate at the mouth to the chamber 28, but extends into and preferably nearly or completely therethrough.

In its, the chamber 28 traversing region 35, the lateral surface of the (driven) shaft 33 is not cylindrical, but is provided with preferably axially parallel elevations and / or depressions, for example with a star-shaped cross-section transverse to the eccentric axis 23rd

The gear 29 has in its hub 36 a recess 37, the inside of which is designed as a counterpart to the profiling of the chamber 28 traversing region 35 of the lateral surface of the (output) shaft 33, so that as a result of interlocking elevations and depressions a positive connection between the gear 29 and the (output) shaft 33 of the motor 32 is formed, which rotatably coupled the two parts together, so that the driving torque of the motor 32 can be transmitted to the gear 29. From there, the drive torque is transmitted to the toothing 15 of the toothed connection element 2 in order to rotate it and thus the machine or system part fixed thereto about the main axis of rotation 11.

In Fig. 1 are indicated by dashed lines possible developments of the invention. The outer, circular line is intended to indicate that the outer circumferential surface 20 of the radially outer, annular connecting element 3 can also be designed as a whole circular, in particular if the thickness of this outer connecting element 3 measured in the radial direction is greater than the diameter of a meshing with the teeth 15 gear 29 or the diameter of a chamber 28 for receiving the same. In such a case, it is possible with little effort to arrange a plurality of chambers 28 within such a dimensioned connection element 3, for receiving a corresponding number of gears 29, all of which at the same time with the toothing 15 mesh. In this way, the torque which can be introduced via the toothing 15 onto the toothed connection element 2 can be multiplied and thus increased to a considerable extent. Furthermore, these multiple chambers 28 can be arranged such that they each equal distances, so that their centers or possibly existing puncture points for the respective gears 29 driving axes 23 are offset from each other at the same center angles. In other words, in the case of two chambers 28, their centers preferably have intermediate angles of 180 °, in three chambers 28 the intermediate angles are respectively 120 °, and in the case of n chambers 28 their centers are each offset by an intermediate angle of 360 ° / n, so that Overall, a high degree of symmetry results and despite increased torques radial forces from the rolling elements 39, 40 can be kept away.

A corresponding arrangement is possible if the radially outer connection element 3 is toothed and the chambers 28 are incorporated for receiving gear teeth meshing with the toothing 15 in the radially inner connection element 2. In such a case, the radially inner connecting element 2 can possibly also be designed with a radial thickness that is equal to or greater than the diameter of a toothed gear meshing with the toothing or the diameter of a chamber for accommodating the same. Then, the radially inner circumferential surface 57 may be designed completely cylindrical. Also, in this case, a plurality of chambers 28 may be provided within the inner connection element 2, preferably such that at n chambers 28 whose centers are each offset by an intermediate angle of 360 n against each other. The features just described are almost all embodiments of the rotary joint 1 according to the invention; V; 1 ";1"'together. For example, the top view of the rotary joints V, 1 "and / or 1"'can largely correspond to the plan view of FIG. 1 shown in FIG.

In all embodiments, multiple drive motors 32 may be used to increase drive torque. In this case, a plurality of radial extensions 27 of the untoothed connection element 3 may be provided or the relevant, annular connection element 2, 3 has a sufficient radial thickness extension. If necessary, with two drive motors 32, such radial extensions 27 may be arranged diametrically opposite each other, three extensions 27 for a total of three drive motors 32 would be offset by 120 °, four extensions 27 would preferentially intersect at right angles on the beams of two in the main axis of rotation 11 Lines 26, 38 are located, etc.

In the case of two radial extensions 27, the arcuate section 21 of the lateral surface 20 reduces to two short sections in the region of the straight line 38. With three or four radial extensions 27, these arcuate sections 21 become shorter or completely omitted, so that the arcuate sections 22 of adjacent extensions 27 in the limiting case, even directly by straight straight sections 24, 25 may be connected to each other.

In addition to the features described above, which are common to many embodiments, there are other design features which may be different from case to case:

This relates, on the one hand, to the configuration of the bearing in the region of the gap 14. This may in each case have one or more rows of rolling elements 39, 40, 41, as shown in FIGS. 2 to 5.

This may be thrust bearings or angular contact bearings as in the rows of rolling elements 39, 40, and / or radial bearings as in the row of rolling elements 41 and / or four-point bearing as in the Wälzkörperreihen 39 ', 40'; 39 ";39"', 40 "'.

Further, the rolling elements 39-41; 39 ', 40'; 39 ", 39" ', 40 "' of at least one row may be spherical, and / or roll-shaped, and / or barrel-shaped, and / or tapered, and / or needle-shaped.

The raceways for one or more rows of rolling elements 39-41; 39 ', 40'; 39 ", 39" ', 40 "' are preferably formed directly in the respective connecting body 2, 3 or in an annular part thereof." Furthermore, the cross-section of the raceways to the cross-section or to the shape of the rolling elements 39-41, 39 '. , 40 ', 39 "; 39 "', 40'" adapted to each achieve an optimal osculation. As can be seen Figs. 2 and 4, the all-round toothing 15; 15 "on a relative to the other, the gap 14 facing lateral surface 12, 12" raised area, in particular on an all-round collar 42 or flange 43 may be formed. On the other hand, one or both flanks of such a federal 42 or flange 43 also serve as a raceway (s) for one or more rows of rolling elements 39, 40, as shown in particular in Fig. 2, but could also be realized in other embodiments For example, in the rotary joint 1 "of FIG. 4.

However, such an exposed position of the toothing 15 requires; 15 "at a radially to the gap 14, 14" projecting collar 42 or flange 43, a subdivision of the respective untoothed connection element 3; 3 '; 3 "along at least one separating surface 44, 45, 45 ', 45", in particular along at least one main plane in the region of the collar 42 or flange 43, since otherwise the toothed connection element 2 having the all-round elevation; 2 '; 2 "not in an all-round, preferably groove-shaped or throat-shaped recess 46, 36 ', 46" at the gap 14; 14 '; 14 "facing Mantelelfäche 13; 13 '; 13 "of the untoothed connection element 3, 3 ', 3" can be applied into it.

If the all-round toothing 15; 15 "of the toothed connection element 2, 2" - as indicated in FIGS. 2 and 4 - is arranged on an exposed collar 42 or flange 43, so there is the meshing gear 29; 29 "at just this height, and thus also that gear 29; 29" receiving chamber 28; Preferably, in such a case, a two or more parts of the untoothed connecting element 3, 3 "can be separated from each other by main plane 44, 45; 45 "in the region of the chamber 28, 28", in particular with an upper and / or lower end side of the same. Preferably, the radial extension (s) 27 are (are); 27; 27 "integrally formed with the part of the untoothed connecting element 3, 3 ', 3" that surrounds the rotational axis 11 in an annular manner. Is the untoothed connection element 3; 3 '; 3 "for mounting a collar 42 or flange 43 on the toothed connection element 2, 2 ', 2" along one or more parting surfaces 44, 45; 45 '; Divided 45 "or main planes, so is the radial (s) extension (s) correspondingly subdivided or along just these separation surfaces 44, 45, 45 ', 45" or main planes.

Merhrere parts of the untoothed connection element 3; 3 '; 3 "can be fixed to each other, for example screwed together, as shown in Fig. 4 by the screw 47.

On the other hand, missing to the gap 14 '; 14 '' projecting collar 42 or flange 43, so under certain circumstances no subdivision of the untoothed connection element according to a main plane is required for assembly in such a case would (n) also one or (more) radial extension (s) 27, 27 ', 27th "; 27 "'not be divided, as can be seen in Fig. 5. As can be seen from FIGS. 2, 3 and 5, in a rotary joint 1; 1 '; 1 ";1"'with a plurality of rows of rolling elements 39, 40, 41; 39 ', 40'; 39 '", 40"' the gearing 15; 15 '; 15 "'are preferably arranged between two rows of rolling elements 39, 40, 41' 39 ', 40', 39"', 40 "'. As a result, the rows of rolling elements 39, 40, 41; 39 ', 40';39"'can be arranged. , 40 "'are spaced apart from each other, without the height of the rotary joint 1, 1', 1"; 1 "'would have to be increased.

Is there the toothing 15; 15 "at an exposed area, and is therefore in any case the untoothed connection element 3, 3" divided, so the teeth 15; 15 "are arranged as a raised, straight teeth on the free radial end face of the relevant, collar or flange-like elevation 42, 43, so that the assembly is neither impaired nor impossible.

On the other hand, if the toothing 15 '; 15 "'in the region of the gap 14'; 14" 'is not arranged on a raised collar 42 or flange 43, the untoothed connection element 3'; 3 "'can not be divided, as can be seen in Fig. 5. In such a case, the teeth 15', 15" 'in the gap 14'; 12 "'of the toothed connection element 2'; 2 "'incorporated, in particular milled.

A toothing 15; 15 '; For example, 15 ", 15" 'may be made with a milling cutter having an approximately elongated shape similar to the circumferential shape of a worm gear worm gear. Since the teeth of the toothing 15; 15 '; 15 ", 15" 'do not have to be inclined, since they do not mesh with a worm, but with one or more gears 29; 29 '; 29 "; 29" ', such a milling tool need not have a pitch like a worm gear; Rather, the blades can be arranged in a circle around the cutter axis.

A straight toothing 15; 15 "on an exposed part, ie on a collar 42 or on a flange 43, can by feeding a milling tool parallel to the axis of rotation 11 of the toothed or toothed connection element 2; The same technique can also be used if, as shown in Fig. 5, the area to be toothed is raised, at least at an area adjacent to the axial direction, in relation to the adjoining lateral surface 12 '' of the gap 14 '' In the latter case, however, a milling cutter for producing the toothing 15 "'may not be pulled through, but has to travel back in the axial direction or in the radial direction out of the teeth 15; in both cases remains at the turning point of the milling cutter a circular arc-shaped portion of the recess between adjacent teeth, as shown in Fig. 5.

If, on the other hand, a toothing 15 'is to be incorporated into a region of the lateral surface 12' facing the gap 14 ', a radial advancement of the milling tool perpendicular to the axis of rotation 11 of the toothed connection element 2' is to be recommended, so that the in Fig. 3 illustrated tooth geometry. The geometry of the gear 29; 29 '; 29 "; 29" 'is the tooth geometry of the toothing 15; 15 '; 15 "; 15" '. That is, in a straight toothing 15; 5 ", 15" '- preferably at an at least one side raised region of the lateral surface 12; 12 ", 12" '- is just such a toothing on the gear 29; 29 "; 29" '.

In a longitudinal or axial direction, ie parallel to the main axis of rotation 11, arcuate tooth geometry of the toothing 15 ', as this is caused by a radial feed of the milling tool and can be seen in Fig. 3, a meshing gear 29' should have a corresponding , Preferably have dome-shaped tooth geometry. This could be milled out of a ball, for example, after an upper and lower cap have been separated from this, sawed off, for example. As long as a gear 29; 29 '; 29 ";29"'is not yet attached to the relevant shaft 33, it has inside the chamber 28; 28 '; 28 ";28"'clearance and may within the same of the gap 14; 14 '; 14 ", 14 '" are temporarily moved away to the two annular connection elements 2, 3; 2 ', 3'; 2 ", 3"; 2 "', 3"' to assemble. For this purpose, the chamber 28; 28 '; 28 ";28"'will be a bit more generous.

In embodiments of a rotary joint 1 according to the invention; 1 '; 1 "with in the region of the chamber 28, 28 ', 28" along a separating surface 44, 45; 45 '; 45 "or main plane divided into several rings, untoothed connection element 3, 3 ', 3", the gear 29; 29 '; 29 "are applied from a front-side, ie upper or lower-side opening into the chamber 28, 28 ', 28", which is created by removing an upper or lower part ring. In such case, the geometry of the chamber 28; 28 '; 28 "in the region of its opening to the gap 14, 14 ', 14" limited only by the requirement that neither the teeth 15; 15 '; 15 "nor the gear 29, 29 ', 29" may scratch somewhere.

However, if a subdivision of the untoothed connection element 3 "'for the assembly is not required and actually not provided, as in particular in the embodiment of a rotary joint 1" shown in Fig. 5, the gear 29 "' of the gap facing the opening used in the chamber 28 "'. For this purpose, the gap of the opening facing the chamber 28 "'must be equal to or greater than a vertical section through the relevant gear 29' 'along its axis of rotation 23'".

For this purpose, it is recommended that a shell-side inner surface 48 "'of the chamber 28"' follows a rotationally symmetric course, at most along a center angle γ about the eccentric axis of rotation 23 "'of the gear 29"' of γ = 180 °, in particular a cylindrical or In the remainder of the gap 14 "'facing region, ie within a center angle of 360 ° - Y, the curved portion of Innemmantelfläche 48"' adjacent sections either follow each other parallel courses or diverging to the gap 14 "'out even even from each other.

Figs. 3 and 5 show - representative of all figures, because a corresponding configuration can in all embodiments of a rotary joint 1 according to the invention; 1 '; 1 ", 1" 'be provided - that with the gear 29; 29 '; 29 "; 29" 'non-rotatably coupled shaft 33; 33 '; 33 "; 33" 'in the untoothed connection element 3; 3 '; 3 ", 3" 'can be mounted, in particular by means of one or more roller bearings 49, 50; 49 "', 50"'.

For storage of a gear 29; 29 '; 29 "; 29" 'in the untoothed connection element 3; 3 '; 3 "'may be provided in the latter at least one bearing recess 51, preferably in the region of the chamber 28; 28 '; 28 ", 28" ', in particular on one or both end faces of the chamber 28; 28 '; 28 "; 28" ', in particular on its upper side 52 and / or underside 53. Preferably, the local, annular bearing recesses 51; 51 "'concentric with the eccentric axis 23; 23'; 23"; 23 "'of the bore 31; 31'; 31"; 31 "'.

This can lead to the area of the mouth of the bore 31; 31 '; 31 ";31"'into the chamber 28; 28 '; 28 ", 28"'an additional groove 54 is provided for receiving a ball or roller bearing 49; 49 "'whose outer ring in the groove 54, 54''is pressed while its inner ring is screwed onto the shaft 33 in question or shrunk. Also in the area of the mouth of the bore 31; 31 '; 31 ";31"'into the chamber 28; 28 '; 28 ";28"'opposite end face 53; 53 '' may be provided an additional groove 51, 51 '', also for receiving a ball or roller bearing 50; 50 "', whose outer ring is pressed into the groove 51, 51"', while its inner ring on a front, by the gear 29; 29 '; 29 "'inserted region of the respective shaft 33 is geschrobenft or shrunk. FIG. 4 shows a further development of a rotary joint 1 "according to the invention, in which an end plate 55 in the region of an end face of the chamber 28" is screwed tightly to the actual body 56 of the untoothed connecting element 3 "which accommodates the chamber 28" by means of screws 47 distributed in a circle ,

The rotary joint 1 "'of Figure 5, however, is for a one-piece construction of both connecting elements 2'"; For this purpose, the gap follows 14 "'a gradual change in the axial direction course. 5, the gap 14 "'has its maximum diameter, larger than in a central, axial region where the toothing 15"' is located the gap 14 "'in the area shown in Fig. 5 below - so at the height of the local rolling element 40"' - its minimum diameter, smaller than in the central, axial region with the teeth 15 "'. Thus, if the two connection elements 2 "', 3"' are pushed into one another in the axial direction such that the section of the outer connection element 3 "'with the maximum inner diameter is pushed forward into the section of the inner connection element 2"' with a minimal outer diameter, then relevant, annular connection elements 2 "', 3"' assembled without subdivision and without risk of collision and finally retracted into each other with optimum centering.

So that none of the two connection elements 2 '"; 3"' has to be subdivided, all the drive gears 29 "'are connected before the assembly of the

Connection elements 2 "', 3"' inserted into their chambers 28 "', which can be done by the relevant, the gap 14"' facing opening in the lateral surface of the chamber 28 "'forth Her facilitated such a Zusammenfgen by a straight , line-shaped course of the free tooth edges, as can be seen in Fig. 5.

In the last-mentioned example as well as in all other embodiments of a rotary joint 1 according to the invention; 1 '; 1 ";1"'is the respective gap 14; 14 '; 4 ", 14"'sealed by in the region of each end-side mouth, in particular by at least one all-round running sealing element.

Furthermore, in the region of a flanged or otherwise fixed motor 32, a seal may also be provided, in particular between a mounting surface 6 provided for this purpose; 6 '; 6 "'and the adjacent contact surface of the motor flange.

Finally, in the case of subdivision planes 44, 45; 45 '; 45 "seals can be provided.

By all these measures, the cavity within the gap 14; 14 '; 14 "; 14" 'and the chamber 28 communicating therewith; 28 '; 28 "; 28" 'and possibly a bore 31 communicating therewith; 31 '; 31 "; 31" 'completely encapsulated and may be wholly or partially filled with a lubricant, in particular with grease.

Since both the intermeshing teeth 15; 15 '; 15 ", 15"'and gears 29; 29 '; 29 ";29"', on the one hand, and those bearing rolling elements 39-41; 39 ', 40'; 39 ";39"', 40 "' and the roller bearings 49, 50; 49 '", 50 "' are thus completely encapsulated for the relevant motor or gear shaft 33, the rotary joint 1, 1 ', 1 according to the invention "; 1 '' to a closed gearbox.This means that a permanent and consistent lubrication is ensured and also a precise guidance or storage of the intermeshing parts, so that a long life expectancy can be achieved.

LIST OF REFERENCE NUMBERS

Rotary joint 26 connecting line

Connection element 27 extension

Connection element 28 chamber

Front side, connection surface 29 Gear

Front side 30 teeth

Front side 31 bore

Front side, connection surface 32 Motor

Mounting hole 33 Output shaft

Mounting hole 34 front side

Internal thread 35 area

Central axis, axis of rotation 36 hub

Lateral surface 37 recess

Lateral surface 38 Straight

Gap 39 rolling elements

Gearing 40 rolling elements

Cross section 41 rolling elements

Lateral surface 42 collar

Outer circumference 43 flange

Cross section 44 separating surface

Lateral surface 45 separating surface first region 46 groove-shaped depression second region 47 screw

Eccentric axis 48 inner surface

Lateral surface section 49 Rolling bearings

Lateral surface section 50 Rolling bearings Bearing recess, groove top

bottom

groove

End plate

corpus

lateral surface

circular arc section

Claims

claims

Rotary connection (1, 1 ', 1 ", 1"') with two annular connection elements (2, 3) concentrically arranged to form a gap (14) running concentrically around each other for connection to a respective machine part, chassis or foundation, wherein on the two annular connecting elements (2,3) at their the gap (14) facing surface regions (12,13) each have at least one raceway, whereupon each roll a number of rolling elements (39,40,41), so that the both ring-shaped connection elements (2, 3) can be rotated relative to one another about a main axis of rotation (11) of the rotary connection (1, 1 ', 1 ", 1"'), and at least a first of the annular connection elements (2, 3) its surface region (12) facing the gap (14) is provided with an all-round toothing, whereby at least one toothed wheel (29) meshes with its axis of rotation (23) parallel to the main axis of rotation (11) of the rotary joint (1; '; 1 "; 1"') and in a second de R annular connecting elements (2,3) is received and / or stored, characterized by at least one to the gap (14) open toward the chamber (28) for receiving a toothing (15) meshing gear (29) in the second , untoothed, annular connection element (3) or in at least one annular part of the same is incorporated or molded and with respect to the environment of the rotary joint (1, 1 ', 1 ", 1"') is completed.

A rotary joint (1; 1 '; 1 "; 1"') according to claim 1, characterized in that the all-round toothing (15) of the first toothed annular connecting element (2) together with at least one of its raceways for rolling along it Rolling elements (39,40,41) is made by machining and / or shaping a first body, in particular by preferably machining the same.

A rotary joint (1; 1 ', 1 ", 1"') according to claim 1 or 2, characterized in that at least one chamber (28) open towards the gap (14) for receiving a toothed wheel (15) meshing with the toothing (15). 29) in a second, untoothed, annular connection element (3) or a part thereof, together with at least one of its raceways for rolling elements rolling along it (39, 40, 41), is machined and / or formed by a second base body, in particular by preferably machining the same.

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that the toothed connecting element (2) and / or the gear meshing therewith (29) is end-toothed and / or straight-toothed.

Rotary connection (1; 1 ', 1 ", 1"') according to any one of the preceding claims, characterized in that the all-round toothing (15) of the first annular connection element (2) between two raceways for each row of rolling elements (39 , 40,41).

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that the all-round toothing (15) of the first annular connection element (2) on a relative to an adjacent track in the radial direction raised region (42; 43) of the same connection element (2) is located.

Rotary connection (1; 1 '; 1 ";1'") according to one of the preceding claims, characterized in that the all-round toothing (15) of the first annular connection element (2) is located on an end face of a circular collar (42), whose flanks are designed as raceways for each row of rolling elements (39,40).

8. Rotary connection (1, 1 ', 1', 1 '') according to one of the preceding claims, characterized in that the second, untoothed connecting element (3) is subdivided into two superimposed rings, which along a joint (44,45 ).

9. Rotary connection (1, 1 ', 1 ", V") according to one of the preceding claims, characterized in that the second connection element (3) has an approximately C-shaped cross-section (19) with an all-round, groove-shaped recess (46 ) in the region of the gap (14).

10. Rotary connection (1, 1 ', 1', 1 '') according to claim 9, characterized in that the chamber (28) in the second connection element (3) at the level of the groove-shaped recess (46) and is located towards this is open. 11. A rotary joint (1; 1 ', 1', 1 '') according to any one of the preceding claims, characterized in that the chamber (28) in the second connection element (3) in the radial direction, with respect to the axis of rotation (23) of gear (29) received therein, is open towards the gap (14) along a first center angle δ, for example along a first center angle δ> 60 °, preferably along a first

Center angle δ> 75 °, in particular along a first center angle δ> 90 °.

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that the chamber (28) in the second connection element (3) in the radial direction, with respect to the axis of rotation (23) of the received therein Gear wheel (29) along at least a second center angle ε of a rotationally symmetrical lateral surface (48) is limited, for example, along a second center angle ε> 120 °, preferably along a second center angle ε> 150 °, in particular along a second center angle ε> 180 ° ,

13. Rotary connection according to claim 12, characterized in that the rotationally symmetrical region of the lateral surface (48) of the chamber (28) follows the shape of the lateral surface of a hollow cylinder, a hollow barrel or a hollow dome.

14. A rotary joint (1, 1 ', 1', 1 '' ') according to any one of the preceding claims, characterized in that the chamber (28) in the second connection element (3) in the radial direction, with respect to the axis of rotation (23) of gearwheel (29) received therein follows a straight course along at least one further center angle range ζ, for example from the edges of the opening of the chamber (28) to the gap (14) until the beginning of the rotationally symmetrical boundary surface.

15. Rotary connection (1; 1 ', 1 ", 1"') according to claim 14, characterized in that the chamber (28) in the second connection element (3) in radial

Direction, based on the axis of rotation (23) of the gear (29) received therein along at least a third center angle ζι and a fourth center angle ζ _{2 is} bounded by mutually parallel, flat surfaces, for example, along a third center angle ζ-ι> 15 ° and along a fourth center angle ζ ₂ >

15 °, preferably along a third center angle ζι> 30 ° and along a fourth center angle ζ ₂ > 30 °, in particular along a third center angle ζι> 45 ° and along a fourth center angle ζ ₂ > 45 °.

16. Rotary connection (1; 1 ', 1', 1 '') according to one of the preceding claims, characterized in that the chamber (28) in the second connection element (3) in the axial direction of a flat upper side (52) and a to parallel, flat bottom (53) is limited.

17. Rotary connection (1, 1 ', 1', 1 '') according to one of the preceding claims, characterized in that in the region of the upper side (52) and / or the Bottom (53) of the chamber (28) has a bearing (49,50) for a gear (29) driving shaft (33) is provided.

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that at least one bearing (49, 50) for a shaft driving the gear wheel is designed as a radial bearing.

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that the second connection element (3) has a jacket surface (20) facing away from the gap (14) in the region of the chamber (28) Thickening in the form of a radial extension (27).

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that a recess or bore (31) for receiving a drive shaft (33) for the gear meshing with the toothing (15) ( 29) extends to a flat outer surface (6) of the second connection element (3).

Rotary connection (1; 1 ', 1 ", 1"') according to claim 20, characterized in that in the region of the mouth of the recess or bore (31) for receiving a drive shaft (33) for the meshing with the toothing (15) gear (29) in a flat outer surface (6) of the second connection element (3) one or more means for fixing the housing of a drive motor (32) are provided, for example one or more, preferably annularly distributed around the mouth mounting holes.

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that the mouth of the recess or bore (31) for receiving a drive shaft (33) for meshing with the toothing (15) Gear (29) opposite, flat outer surface (7) of the second connection element (3) as its Pad is formed, to rest on a machine or plant part, chassis or foundation to be connected.

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that fastening means are provided in the flat connection surface (7) of the second connection element (3) for connection to a machine or installation part to be connected, Chassis or foundation, preferably around the main axis of rotation (11) of the rotary joint (1; 1 '; 1 "; 1"') distributed annularly arranged mounting holes (9), in particular with internal thread (10) provided blind holes (9).

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that the connection surface (7) of the second connection element (3) with respect to the adjacent end face (5) of the first connection element (2) in axial Direction is formed sublime.

Rotary connection (1; 1 ', 1 ", 1"') according to one of the preceding claims, characterized in that the gap (14) in the region of its mouths in the region of the top and bottom of the rotary joint (1; 1 '; ; 1 "') is sealed.

Rotary connection (1; 1 ', 1 ", 1"') according to claim 25, characterized in that the gap (14) in the sealed area is completely or partially filled with a lubricant, preferably with lubricating grease.

27. Rotary connection (1, 1 ', 1', 1 '') according to one of the preceding claims, characterized in that the all-round toothing (15) on the inner and / or concavely curved lateral surface (13) of the radially outer connection element (3) is arranged.

28. Rotary connection (1, 1 ', 1', 1 '') according to one of claims 1 to 26, characterized in that the all-round toothing (15) on the at outer and / or convexly curved jacket surface (12) of the radially inner connection element (2) is arranged.

29. Rotary connection (1; 1 ', 1', 1 '') according to one of the preceding claims, characterized in that a plurality of chambers (28), each open towards the gap (14), for receiving one each with the toothing (15 ) meshing gear (29) in the second, untoothed, annular connection element (3) or in at least one annular part thereof or are formed, preferably at equidistant intervals over the circumference of the toothing (15) distributed, ie offset from each other at equal intermediate angles ,

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