DK180487B1 - Swivel connection - Google Patents

Abstract

The invention relates to a rotary connection with two annular connecting elements for connection to a machine or plant part, a chassis or foundation, which during the formation of a gap is arranged concentrically all around each other, where on the two annular connecting elements, if over surface areas facing at the gap, is at least one raceway along which a series of roller bodies roll so that the two annular connecting elements can be rotated towards each other about a major axis of rotation of the pivot connection, and where at least one of the first annular connecting elements on its surface area facing the slot is a circumferential toothing with which a gear engages teeth, the axis of rotation of which is parallel to the major axis of rotation of the rotary joint and which is received and / or located in another of the annular connecting elements, the circumferential toothing of the first annular connecting element with at least one of its roller coasters bodies which roll along it are produced by machining and / or shaping a first main part, in particular by preferably machining machining of the same, and at least one chamber for receiving a gear which engages with the toothing, and / or at least one bore or a bearing or a bearing recess for the axis of rotation of a gear which engages toothed with the toothing in another annular connecting element or a part thereof together with at least one of its raceways for roller bodies rolling along it are made by machining; and / or shaping another main part, in particular by preferably machining the same.

Description

The invention relates to a rotary connection with two annular connecting elements for connection to a machine or plant part, a chassis or foundation, which during the formation of a gap is arranged all the way around concentrically in relation to each other, where on the surface areas facing the slot of the two annular connecting elements, there is at least one raceway along which a series of roller bodies roll, so that the two annular connecting elements can be rotated towards each other about a major axis of rotation of the pivot connection, and where at least one first of the annular connecting elements on its surface area facing the slot is a circumferential toothing with which a gear engages teeth, the axis of rotation of which is parallel to the major axis of rotation of the pivot joint and which is received and / or arranged in another of the annular connecting elements.

WO 9725553 describes a rotary connection with two annular concentric mounting elements which form a gap to be mounted on a machine part, a plant part, a chassis or a foundation. The two annular elements have on the surface facing the space, roller grooves with a number of rollers which can roll, so that the two annular elements can rotate relative to each other about a main center axis. On the surface of one of the annular elements, an annular gear ring is arranged which engages with a gear wheel. The axis of the gear is parallel to the main axis and is placed in the second annular element in a connecting chamber open towards the space and contains the gear. The chamber is closed to the external environment. Swivel connections are often driven by a worm, so this results in the structure of a worm gear. However, these devices have a number of disadvantages: Worm gears have an extremely large gear ratio, and with an increasing diameter of the toothed annular connecting element to be driven by the worm, this ratio increases constantly because a worm gear speed-ratio ratio Us with a the single-ended screw is located at Us = na: ns = 1: za, where z indicates the number of teeth of the toothed connection element. This reduces it

DK 180487 B1 2 speed that can be achieved on the ring gear to be adjusted, extremely. If e.g. a foot of a wing in a wind farm has a diameter of 3 m, then its extent is approx. 9.42 m. At a total tooth width of e.g. 2 cm there is along such a extent no less than za = 471 teeth. | this case is Us = 1: 471 = 0.002. If the screw is driven by a motor with a maximum speed of nsmax = 600 rpm = 10 rpm, then the maximum speed Nrmax on the wing bearing itself would be A, max = Ns, max * Us = 10 o /SEC. * 0.002 = 0.02 rpm. This means that a single revolution would require approx. 50 seconds.

This might seem a bit like adjusting the wing bearing of a wind turbine. Wind power plants, which are becoming ever larger, mean that the wings move through different air layers above the earth during one revolution, where the wing tips, for example, move at heights between 50 m and 200 m. Good rules therefore try to create an optimal wing angle for the different wind speeds at different heights above the ground. In addition, it is important as far as possible to create a regulatory equalization in the event of sudden gusts of wind to protect the wing bearings, which are already heavily loaded, against overloads.

Therefore, if, as a result of such applications, when using rotary connections where the connecting elements have a large diameter, an optimal gear ratio will be obtained, then single-screw worm gear is unsuitable for this purpose. Multi-run carpentry, however, requires an oblique toothing on connecting elements, which requires a great deal of work to manufacture.

The invention is therefore based on a device in which a gear wheel is used instead of a screw. This means that there are significantly better options for setting the exchange ratio. | in this case, the following applies to the gear ratio: Uz = na: nz = zz: za, where za is the number of teeth of the toothed connecting element and zz is the number of teeth engaging the tooth-engaging gear. A gear with a ring diameter of approx. In this connection, 6.4 cm results in a circumference of 20 cm. and with a tooth width of 2 cm. in a tooth number zz pa zz = 10. For the above example of a tooth ring with 471 teeth, the gear ratio at Uz = zz: za = 10: 471 = 0.02. A maximum engine speed of

DK 180487 B1 3 Ns, max = 600 rpm = 10 rpm. results in a maximum speed of Nr, max on the wing bearing itself at Namax = Nzmax * Uz = 10 rpm. * 0.02 = 0.2 rpm.

This means that a single revolution would only require approx. 5 seconds.

In addition, a gear wheel with shorter bearing distances can achieve a higher speed than a worm.

Of course, a wing bearing will usually never perform a complete revolution.

It depends much more on the speed that can be achieved in the short term, which is significantly lower on a worm gear than a gear drive.

Incidentally, a worm gear is almost or completely self-locking and is therefore suitable for many applications where a flexible response to unforeseen external influencing (disturbing) forces, such as. gusts of wind, etc. are necessary.

In the case of a worm gear, such external (interfering) forces are completely absorbed by the worm bearing, which can destroy it.

Precisely for this reason, a dynamic change of a worm shaft speed should also be limited as far as possible, because a sudden start due to inertia or other braking moments could also result in an overload of the worm bearing or even of the worm thread itself.

This disadvantage is not found with gear drives, because all gears engage with each other due to a lack of self-locking and can dodge to a suitable direction of rotation and therefore there is no risk of the parts of the drive being overloaded.

Thus, assuming pivot joints driven by sprockets or gears, attempts have already been made to surround the radially outer connecting member with an external toothing and to place the drive motor of a tooth engaging spike on the inner ring via a projecting flange. udad.

However, this usually does not result in a sufficient encapsulation of the gear and the toothing.

In addition, the mounting flange protrudes beyond the outer ring on one of its two front sides, so that it is not possible to attach the outer ring to the front side in question, which further limits the design possibilities.

According to the invention, therefore, a device is preferred in which the toothing engagement between a circumferential toothing of a connecting element and a

DK 180487 B1 4 tooth-engaging gears take place immediately in the gap area between both connecting elements. This means that the driving gear in question can be arranged in an annular connecting element and immediately propels the other connecting element forward. It is therefore not necessary for a flange connected to the inner connecting element to grip around the outer connecting element on one side. In addition, it is possible to place the gear wheel inside a chamber which is open only towards the slot on one side, where the toothing engagement with the second connecting element takes place, and against the shaft of the drive motor on the other side, from which the driving force originates, which however, it is otherwise closed externally. One opening can e.g. sealed with seals all the way around, which are arranged at the slit mouths in the area at the upper and lower front sides of the swivel connection, the second opening by flanging, or otherwise fastening the drive motor, if necessary. with an inlaid seal. Thus, such a device is a completely encapsulated drive, especially because possibly. existing (roller) bearings in the movable drive parts, namely the toothed connecting element on one side and the tooth-engaging gear wheel on the other side, are completely integrated in the drive. This also makes it possible to obtain an improved precision, especially if the gear wheel is placed immediately inside the toothless connecting element and no effort is made to place the drive shaft of a flanged drive motor in a remote position. By placing the gear on the non-toothed connecting element, there is no lateral tolerance, as when flanging a motor which, due to the considerable space between mounting eyes on the one hand and these piercing screws on the other hand, is associated with relatively large inaccuracies. .

It is a further object of the invention to provide at least one chamber for receiving a tooth-engaging gear and / or at least one bore or a bearing or one bearing recess for the axis of rotation of a tooth-engaging gear in another annular connecting member or part thereof together with at least one of its raceways in the roller for the roller rolling along it, or together with several or all of its raceways in the slot for the roller bodies rolling along them, are made by machining and / or shaping a common, preferably toothless body, especially at preferably

DK 180487 B1 Chip machining of the same. This results in a precise adjustment of the gear wheel, which is arranged inside the chamber, in relation to the bearing for the second, toothed connecting element, and thus also in relation to the toothing, which is arranged on the connecting element in question. Thus, a high precision of the interlocking tooth-engaging teeth on the toothed connecting element on the one hand and on the tooth-engaging gear on the other hand can be ensured, as this can otherwise typically only be achieved within a completely encapsulated drive.

With the further development of the invention it is possible that the circumferential toothing on the first annular connecting element together with at least one of its raceways in the gap for roller bodies which roll along it, or together with several or all of its raceways in the gap for roller bodies rolling along them are made by machining and / or shaping a first main part, particularly preferably by machining the same. With such a measure, the placement is made even more precise, because separate running tracks completely disappear.

It is within the scope of the invention that the toothed connecting element and / or the gear-engaging gear therewith is inclined and / or straight-toothed. Such toothing can be manufactured at minimal cost, but has a uniform torque transfer when realizing an involute toothing. In the case of several bearings or rows of roller bodies, it is usually desired to place them in the axial direction as far apart as possible. On the other hand, a swivel joint should often be as low as possible between both its front sides. To meet these requirements, the circumferential toothing on the first or toothed, annular connecting element can be placed between two raceways for each a series of roller bodies.

In particular, if the toothing of the toothed connecting element is located between two rows of roller bodies, the drive shaft of a gear engaging the tooth with the toothing must be radially as far out as possible. To meet this requirement, recommend

The invention that the circumferential toothing on the first or toothed, annular connecting element is located in an area on the same connecting element opposite an adjacent raceway in the radial direction. Thus, the gear wheel - and thus also its drive shaft - is displaced radially outwards in relation to the bearing or roller bodies, where the drive shaft can be passed without collision at the bearing. One possibility of carrying out the above-mentioned idea is that the circumferential toothing on the first or toothed, annular connecting element is located on a front side of a circumferential collar, the flanks of which are designed as raceways for each of a number of roller bodies. In this way, the various interfaces on such a collar can all be used in a particularly optimized manner: its flanks are particularly suitable for the transmission of axial forces between the connecting elements, namely via roller bodies rolling along them, while the front side as a particularly exposed surface is suitable for initiating torques, namely via the tooth flanks of a row of teeth arranged all around.

In order for a connecting element with a circumferential collar, e.g. can be positioned and mounted within a second connecting element so as to grip the collar of both its flanks, the invention recommends that the second or toothed connecting element is subdivided into two rings which lie on top of each other and which abut each other along a joint or interface. These sub-rings can therefore be temporarily removed from each other for mounting and then reassembled around the collar.

This allows the second or toothless connecting element to have an approximately C-shaped cross-section with a groove-shaped recess all the way around the gap area. This depression area can e.g. a collar or other, protrude all the way around the toothed element engaging.

Other advantages are that the chamber is located in the second or non-toothed connecting element at the level of a groove-shaped depression in the area of the cladding surface, which faces the gap, and is open towards it. Thus, a gear,

DK 180487 B1 7 located inside this chamber, positioned in immediate contact with a toothing in a collar engaging the notch-shaped recess.

The chamber in the second or toothless connecting element should be open in radial direction, related to the axis of rotation of the gear, towards the gap along a first center angle α, e.g. along a first center angle α> 60 °, preferably along a first center angle α> 75 °, especially along a first center angle α> 90%. This opening should be large enough to make room for the toothing engagement between the tip wheel or gear and the toothing of the toothed connecting element.

If the toothed ring is not subdivided, the tip wheel or gear must also be inserted into the chamber through this opening before the assembly with the toothed connecting element.

On the other hand, the chamber in the second or non-toothed connecting element in radial direction, related to the axis of rotation of the gear, along at least one second center angle B should be limited by a preferably rotationally symmetrical cladding surface, e.g. along a second center angle B> 120 ”, preferably along a second center angle B> 150 °, in particular along a second center angle B> 180 °. This cladding surface encapsulates the chamber and thus the entire drive, so that dust and dirt particles on the one hand are kept away and a lubricant on the other hand is retained in the area of the drive.

The invention can be further developed so that the rotationally symmetrical area of the chamber cladding surface in areas has the shape of the cladding surface of a hollow cylinder, a hollow barrel, or a hollow cap.

While the course of the cladding surface of the chamber is predetermined by the rotational symmetry of the tip wheel or gear surrounding it, the shape of the cross-section passing through this cladding surface can be adapted to the gear or tip wheel surrounding this cladding surface.

Thus, a gear made of a cylindrical body may be surrounded by a hollow cylindrical cladding surface, a gear made of a spherical or cap-shaped body, the longitudinal vault corresponding to the circumferential vault may be surrounded of a hollow cap-shaped cladding surface, and a gear wheel with a casing slightly curved in its axial direction, where it

DK 180487 B1 8 longitudinal vault does not correspond to the circumferential vault of a hollow barrel-shaped cladding surface. Preferably, the cladding surface of the chamber in the second or non-toothed connecting element in radial direction, related to the axis of rotation of the gear, follows a straight course along at least one other center angle region y, e.g. from the edges of the opening of the chamber to the slot and to the beginning of the rotationally symmetrical restraining surface. Theoretically, the rotationally symmetrical cladding surface section could extend to the edge side opening in the chamber, so that: a + B = 360 °. | in this case, however, the opening is almost always less than 180 °, so that a gear wheel cannot be inserted into the chamber through this opening. Such a design with a + B = 360 ° can therefore at best be realized with an toothed connecting element which is subdivided into sub-rings. For other types of construction, at least one transition area is required so that the opening is large enough to be able to guide a gear or tip wheel into the chamber. A substantially symmetrical arrangement of the chamber is obtained with an opening large enough for mounting a gear if the chamber in the second or non-toothed connecting element in the radial direction, related to the axis of rotation of the gear, is limited by flat surfaces along at least a third center angle y1 and a fourth center angle y2 e.g. along a third center angle y1> 15 ° and along a fourth center angle y2> 15 °, preferably along a third center angle y1> 30 ° and along a fourth center angle y2> 30 °, in particular along a third center angle y1> 45 ° ° and along a fourth center angle y2> 45 °. | in this case the following applies: a + B + y1 + y2 = 360 °. A typical dimensioning would e.g. be: a = 90%; B = 180%; y1 = y2 = 45 °. Then the two planar surfaces would also be parallel to each other and together with the upper and lower side of the chamber would form a shaft with a square cross-section through which a gear wheel can be pushed to its preferred position.

To allow for subsequent mounting and disassembly of the gear in and out of the chamber without separating the toothless connecting element, there should be from the chamber opening in the area of the gap to the area of the chamber facing away

From this opening, however at least to a bore or another opening for a drive shaft for the gear, be a shaft whose free height in the whole area is always equal to or greater than a maximum cross-section through the gear to be mounted or dismounted along its axis of rotation or axis of rotation. The sides of this shaft can eventually merge into the adjacent surfaces of the chamber without kinks or steps, especially in their upper and lower side on one side and in a concave arched cladding surface area on the other side. If a gear is to be mounted or dismounted through such a shaft, the shaft must admittedly be wider than the gear cross-section in question along its axis of rotation or rotation, but not smaller than the gear cross-section in question. A further preferred design provision prescribes that the chamber in the second or toothed connecting element is delimited in the axial direction by a planar upper side and a flat lower side which is parallel thereto. Preferably, these planar surfaces extend parallel to a major plane of the bearing through which the major axis of rotation of the pivot joint passes vertically. On these, the drive shaft of the gear wheel then passes vertically. Thus, the main plane of the gear wheel which engages with the toothing on the toothed connecting element is also given in advance, and thus the gear wheel can rotate contactlessly and thus easily inside the chamber.

| the area at the top and / or bottom of the chamber there should be a bearing for a shaft that drives the gear. This / these bearing (s) are located in the immediate vicinity of the gear so that it is guided optimally. This / these bearing (s) takes over all forces and tilting moments that affect the gear wheel, except for a torque that must be initiated on the toothed connecting element. Precisely this is provided on the other side of a drive motor and is transmitted immediately to the gear wheel via the drive shaft without any kind of relative displacement of the same, and is initiated as desired on the toothed connecting element.

A bearing optimized for this purpose for a shaft that drives the gear is designed as a radial bearing. A radial bearing ensures that there is no radial relative movement between the gear and the non-toothed connecting element, and in case of a precise positioning between the two connecting elements, the axis of rotation of the gear

DK 180487 B1 10 or its drive shaft thus also a defined, constant distance to the main axis of rotation of the bearing and thus also in relation to the toothing of the toothed connecting element. There are thus constantly optimal conditions for the toothing intervention, which i.a. results in an intended long life of the device according to the invention.

In order to make room for the chamber according to the invention, the second or toothless connecting element has a thickening on its cladding surface which faces away from the gap, in the area of the chamber, in the form of a radial extension. Maximum radial thickness extent of the non-toothed connecting element Dmax In this area of thickness can be assessed by the diameter d of the gear received in the chamber, the minimum radial thickness extent of the non-toothed connecting element Dmin elsewhere, and the wall thickness of the chamber housing W in its maximum extent Dmax range according to the following condition: Dmax> d + W - Dmin, or according to the stricter condition: Dmax> d + W.

Within the framework of a preferred embodiment, an opening or bore for receiving a drive shaft for the gear which engages with the toothing extends to a flat outer surface of the second or non-toothed connecting element so that a torque can be initiated. in the drive shaft outside the swivel joint. Because it is not normally possible to initiate a torque without dissipating a torque in the opposite direction in the toothless connecting element of the rotary connection, or in a machine or plant part connected thereto, a chassis or foundation, according to the invention there must be one or more means for attaching a drive motor housing in the area at the mouth of the opening or bore to a drive shaft for the gear which engages toothed with the toothing, in a planar outer surface of the second or non-toothed connecting element, e.g. one or more

DK 180487 B1 11 mounting holes, which are preferably distributed as a ring around the mouth. By attaching and especially screwing on a motor housing, its stator is fixed and the rotor can provide the desired torque.

Within the scope of a preferred embodiment of the invention, the planar outer surface of the second or non-toothed connecting element opposite the mouth of the opening or bore for a drive shaft for the gear which engages with the toothing is designed as its connecting surface for lay against a machine or plant part, a chassis or foundation to be connected. Thus, on this front side for mechanical connection to a machine or plant part, a chassis or foundation, there must not be a drive motor, and therefore there is sufficient space at that place for the machine or plant part in question, etc. The connection to a machine or plant part, a chassis or foundation to be connected, is made possible by the presence of mounting means in the flat connecting surface of the second or non-toothed connecting element, preferably mounting holes, in particular blind holes with internal threads distributed as a ring around the the main axis of rotation of the j-joint. If the axial length of such blind holes is shorter than the distance between the chamber and the connecting surface of the non-toothed connecting element, there may be such screw connections or bores at regular intervals along the entire circumference, i.e. also in the chamber area, or by the caused, radial thickening of the toothless connecting element.

If the connecting surface of the second or toothed connecting element is shaped so that it is elevated relative to the adjacent front side of the first connecting element in the axial direction, then it is by an attachment to a flat mounting surface on a machine or plant part, a chassis or foundation ensured that the toothed connecting element does not roam along the mounting surface.

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

DK 180487 B1 12 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 grease.

It ensures an optimal lubrication of the roller bodies that roll between the raceways on the two connecting elements, and an optimization of the toothing engagement, and possibly. also for lubricating integrated bearings in a drive shaft for the gear.

Within the scope of a first form of carrying out the invention, the circumferential toothing is arranged on the inner and / or concave arched cladding surface of the radially outer connecting element.

This means that the first toothed connecting element is arranged radially inside the second non-toothed connecting element with the chamber (s) for receiving the gears which engage in the toothing.

In such a construction, drive motors which are coupled to the gears which engage with the circumferential toothing are easily accessible from the outside.

In addition, it is also possible for the circumferential toothing to be arranged on the outer and / or convexly vaulted cladding surface of the radial inner connecting element. | in this case, the first toothed connecting element is located radially outside the second non-toothed connecting element with the chamber (s) of the gears engaging the toothing.

Such a device has the advantage that drive motors which are coupled to the gears which engage with the circumferential toothing are accommodated inside the rotary connection or a machine or plant part connected thereto, so that they are protected against external influences. .

Finally, it is in accordance with the idea / theory of the invention that several chambers open to the slot each receive a gear which engages with the toothing in the second non-toothed, annular connecting element, or at least an annular part of the same , is incorporated or molded in, preferably evenly distributed over the extent of the toothing, i.e. staggered relative to each other at the same intermediate angles.

By means of such a device, the torque to be provided by the rotary joint can be multiplied, and in addition

DK 180487 B1 13 an increased symmetry of the torque introduction can thus be achieved, ie. without radial force components being developed elsewhere on the bearing due to the torque introduction.

Other features, details, advantages and effects based on the invention will become apparent from the following description of a preferred embodiment of the invention and of the drawings. Here shows: FIG. 1 is a top view of a rotary joint according to the invention; FIG. 2 is an section through the rotary connection according to FIG. 1 along line II - II: FIG. 3 is a view corresponding to FIG. 2, of another embodiment of the invention with disassembled drive motor; FIG. 4 is a view corresponding to FIG. 3, of a modified form of carrying out the invention; and FIG. 5 is a view corresponding to FIG. 3, which is also a modified form of embodiment of the invention. The swivel connection 1 in fig. 1 is intended to be used as an adjustable winch bearing for a wind farm, but can also be used for other uses. The same applies to the forms of rotary connections 1 'constructed according to the same basic principle according to fig. 3 and 1 "according to Fig. 4, but which in special characteristics differ from them. In Fig. 1 the annular device or device without center is recognized. As can be clearly recognized in Fig. 2, rotary connection 1 primarily comprises two annular connecting elements 2, 3, each having at least one, preferably each in particular two planar front sides 4, 5, 6, 7, of which at least one is a connecting surface

4. 7, for connection to a machine or system part, a chassis, foundation or similar.

DK 180487 B1 14 To make such a connection possible, there are several mounting holes 8, 9 in each connection surface 4, 7, which are distributed in a ring. As can further be seen from FIG. 2, these may be open bores 8, or blind holes 9 with internal thread 10. In these holes, screws may be inserted and / or anchored, which also pass through bores or other openings in the machine or plant part in question, chassis or foundation and thus attaches the relevant connecting element 2, 3 to it / it.

From fig. 2, it further appears that a preferred connecting surface 4, 7 is elevated relative to the adjacent front surface of the second connecting element 2, 3.

Both connecting elements 2, 3 are arranged radially in each other, concentrically to a common central axis 11, which runs vertically through the ring main plane or the surfaces on the front sides 4, 5, 6, 7.

Between the cladding surfaces 12, 13 facing each other on both connecting elements 2, 3, there is a gap 14 which prevents an immediate contact between the two connecting elements 2, 3.

To ensure that the slot 14 is evenly wide all the way round, roller bodies 39, 40, 41 roll within the slot 14.

In addition, it can be recognized that a first connecting element 2 - in the illustrated example of the embodiment the radial interior, which, however, is by no means absolutely necessary, but could just as well be the radial exterior - has a circular geometry, ideally seen with one - except for the mounting holes 8 - unchanged cross-section along its entire circumference.

This first connecting element 2 has in the area at its cladding surface 12 facing the slot 14 a circumferential toothing 15. The toothed connecting element 2 thus has a circular geometry, ideally with a cross section 16, the outer circumference of which is formed by the two fronts 4, 5, the cladding surface

DK 180487 B1 15 12 facing the slot 14 and the cladding surface 17 facing away from the slot 14 do not change along the circumference about the axis of rotation 11. As further appears from fig. 1, the second connecting element 13 - in the illustrated example of the embodiment has the radially outer, which however is by no means obligatory, but could just as well be the radially inner - has a geometry that deviates from the ideal circular shape, ie. . with a cross section 19 changing along the circumference about the axis of rotation 11.

This is shown to the extent that the course of the cladding surface 20 facing away from the gap 14 on the toothless connecting element 2 is composed of several different sections: In a first region 21 extending via a center angle α about the axis of rotation 11 pa 180 ° or more, preferably via a center angle α of 210 ° or more, in particular via a center angle α of 240 ° or more, the surface of the circumference has a rotationally symmetrical design, and this location follows e.g. a cylinder surface. | another area 22 has the cladding surface 20 also have a rotationally symmetrical design, e.g. a configuration as a cylinder surface concentric with an axis 23 arranged parallel to but eccentric with respect to the major axis of rotation 11. This region extends via a center angle B about the eccentric axis 23 of 180 ° or less, preferably via a center angle B of 150 ° or less, in particular via a center angle B of 120 ”or less. In general, the following applies: a + B = 360%. The area 22 of the cladding surface 22, which extends arcuately around the eccentric axis 23, has a smaller radius of curvature r relative to the radius of curvature R of the curved cladding surface section 21 about the main axis 11 of the rotary joint 1:

DK 180487 B1 16 R> r. These two arcuate sections 21, 22 on the cladding surface 20 facing away from the gap 14 on the toothless connecting element 3 are connected to preferably cladding surface sections 24, 25 which run straight and stretched or which are planar. With respect to a connecting line 26 between the two axes 11, 23, the two straight-stretched or even flat cladding surface sections 24, 25 are mirror-inverted relative to each other. Ie. that both converge relative to each other along the connecting line 26 from the major axis of rotation 11 towards the eccentric axis 23. | the transition areas of the adjoining curved sections 21, 22 extend the straight or even planar cladding surface sections 24, 25 tangentially to the center point 11, 23 of the respective curved cladding surface sections 21, 22, so that the outer cladding surface 20 is ideally free of steps or other discontinuities. However, it has a radial extension 27 in the direction of the eccentric axis 23. | this radial extension 27 on the non-toothed connecting element 3 has a chamber 28 for a gear wheel 29, the teeth 30 of which engage with the toothing 15 on the toothed connecting element 2.

From the chamber 28 a bore 31 or another elongate opening extends along the eccentric axis 23 to a front side 6 of the toothless connection element 3, preferably to the front side 6 of the same, which is not used as connection surface 7.

At this location there are several bores distributed as a ring around the eccentric axis 23, preferably blind holes with internal threads on which a motor 32 can be flanged, preferably in such a way that its output shaft 33 extends concentrically to the eccentric axis. 23. If the motor 32 is a gear motor, it would be fixed so that the output shaft of the gear extends concentrically to the eccentric axis 23.

DK 180487 B1 17 Either the output shaft 33 of the motor 32 itself, or a shaft which is non-rotatably connected thereto for extension, extends through the bore 31, or through another elongate opening, to the chamber 28 of the gear 29.

The bore 31, or another elongate opening, opens out approx. in the middle of the front side 34 at the top or bottom of the chamber 28. The (exit) shaft 33, which passes through the respective bore 31, or another elongate opening, does not, however, end at the mouth of the chamber 28, but extends into it and preferably almost or completely through it.

| its area 35 passing through the chamber 28, the cladding surface of the (exit) shaft 33 is not cylindrical, but is provided with elevations and / or depressions which are preferably parallel to the axis, e.g. with a star-shaped cross-section across the eccentric axis 23.

The gear wheel 29 has in its hub 36 an opening 37, the inner side of which is formed as a counterpart to the profiling in the area of the cladding surface of the (output) shaft 33 which passes through the chamber 28, so that as a result of elevations and depressions which interlocking, a molding is formed between the gear 29 and the (output) shaft 33 of the motor 32, which connects the two parts so that they cannot be rotated so that the drive torque of the motor 32 can be transferred to the gear 29. From here the drive torque is transferred to the toothed toothing element 2 of the connecting element 2 for rotating it and thus the machine or abutment part attached thereto about the main axis of rotation 11. In fig. 1, possible further developments of the invention are indicated by dashed lines. The outer circular line should indicate that the outer cladding surface 20 of the radially outer annular connecting member 3 may also be circularly formed overall, especially if the thickness measured in the radial direction of this outer connecting member 3 is larger than the diameter of a gear 29 engaging teeth with the toothing 15, or the diameter of a chamber 28 for receiving the same. | in such a case it is possible to place with a small effort

180 1807 B1 18 several chambers 28 inside such a dimensioned connecting element 3 for receiving a suitable number of gears 29, all of which engage in tooth engagement with the toothing 15 simultaneously.

Thus, the torque that can be initiated via the toothing 15 to the toothed connecting element 2 can be multiplied and thus increased to a considerable extent.

In addition, these several chambers 28 can be placed so that they have the same distance, so that their centers or possibly existing breakthrough points to the respective axes 23 driving the respective gears 29 are displaced at the same center angles relative to each other.

In other words, if there are two chambers 28, their centers are preferably an intermediate angle of 180 °, at three chambers 28 the intermediate angle is every 120 °, and at n chambers 28 their centers are offset by an intermediate angle of 360 ° / nine each other, so that this results in a high degree of symmetry and that radial forces can be kept away from the roller bodies 29, 40 despite elevated torques. A similar device is possible if the radially outer connecting element 3 is toothed and the chambers 28 to contain gears 29 , which engages in tooth with the toothing 15, is incorporated in the radially inner connecting element 2. Thus, the radially inner connecting element 2 can possibly is made with such a radial thickness equal to or greater than the diameter of a gear 29 which engages with the toothing 15, or the diameter of a chamber 28 for receiving the same.

Then the radially inner cladding surface 57 can be formed completely cylindrical. | in this case there may also be several chambers 28 inside the inner connecting element 2, preferably in such a way that at n chambers 28 their centers are offset relative to each other by an intermediate angle of 360 ° / n.

The features just described are common to almost all forms of the rotary joint 1; 1; 1 ”; 1 ”” according to the invention.

Eg. the view of the rotary connections 1 ', 1 ”and / or 1” ”seen from above can largely correspond to the view in fig. 1 seen from above.

DK 180487 B1 19 For all types of design, several drive motors 32 can be used to increase the drive torque. In this case, there may be several radial extensions 27 of the non-toothed connecting element 3, or the annular connecting element 2, 3 in question has a sufficient radial thickness dimension. If necessary, such radial extensions 27 by two drive motors 32 can be arranged diametrically relative to each other using two drive motors 32, three extensions 27 for a total of three drive motors 32 would e.g. be offset 120 ”relative to each other, four extensions 27 would preferably lie on the beams of two straight lines 26, 38 intersecting at a right angle in the major axis of rotation, etc.

With two radial extensions 27, the arcuate section 21 on the cladding surface 20 is reduced to two short sections in the area of the straight lines 38. At three or four radial extensions 27, these arcuate sections 21 are further shortened or disappear altogether, so that the arcuate areas 22 on adjacent extensions 27 in special cases may even be connected directly to each other by means of completely straight stretched sections 24,

25. In addition to the above-mentioned many types of embodiments with common characteristics, there are additional construction characteristics which in each case may be designed differently: This relates firstly to the design of the bearing in the area of the gap 14. It may have one or more rows of roller bodies 39 , 40, 41, as shown in FIG. 2 to 5.

These can be axial bearings or inclined ball bearings, as with the roller body rows 39, 40, and / or radial bearings, as with roller body rows 41 and / or four-point bearings, as with the roller body rows 39 ', 40'; 39 ”; 39 ”, 40”.

In addition, the roller bodies 39-41 may; 39 ', 40'; 39 ”; 39 ”, 40” be spherical in at least one row, and / or roll-shaped, and / or barrel-shaped, and / or conically shaped, and / or needle-shaped.

DK 180487 B1 20 The tracks for one or more rows of roller bodies 39-41; 39 ', 40'; 39 ”; 39 ”, 40” are preferably immediately molded into the relevant connecting body 2, 3, or into an annular part of the same. In addition, the cross-sections of the raceways are adapted to the roller bodies 39-41; 39 ', 40'; 39 ”; 39 ”, 40” ”cross section or design to achieve optimal oscillation.

As can be seen from FIG. 2 and 4, the circumferential toothing 15; 15 'be formed in an area opposite the rest of the cladding surface 12; 12 "facing the slot 14, in particular on a circumferential collar 42 or flange 43.

On the other hand, one or both flanks of such a collar 42 or flange 43 can also be used as a raceway (s) for one or more rows of roller bodies 39, 40, which are shown in particular in fig. 2, but which could also be realized by other types of embodiments, e.g. by rotary connection 1 "according to Fig. 4.

Such an exposed location of the toothing 15; 15 ”on a radial towards the slot 14; 14 ”protruding collar 42 or flange 43, however, requires a subdivision of the toothed connection element 3 in question; 3 '; 3 ”along at least one interface 44, 45; 45 '; 45 ”, in particular along at least one main plane in the area of the collar 42 or the flange 43, otherwise the toothed connecting element 2 may; 2; 2 ”with a circumferential elevation is not inserted into a circumferential, preferably groove-shaped or kel-shaped recess 46; 36 "; 46" on the cladding surface 13; 13; 13 "on the non-toothed connecting element 3; 3 '; 3" facing the slot 14; 14'; 14 ".

If the circumferential toothing 15; 15 ”on the toothed connecting element 2; 2 ”- as indicated in fig. 2 and 4 - is arranged on an exposed collar 42 or flange 43, then the gear wheel 29 is located; 29 ”, which engages with the tooth with it, at this very height, and thus also the chamber 28; 28 ”containing the gear 29 in question; 29 ”.

Preferably in such a case there may be a main plane 44, 45; 45 ”in the area of the chamber 28; 28 ”, which separates two or more parts of the tooth

DK 180487 B1 21 connecting element 3; 3 ”apart, especially flush with a front side at the top and / or bottom of the same. Preferably, the radial extension (s) are 27; 27; 27 ”formed in one piece with the toothless connecting element 3; 3 '; 3 ”annular part surrounding the axis of rotation 11. If the toothed connecting element 3; 3 '; 3 ”is a lower part for mounting a collar 42 or flange 43 on the toothed connecting element 2; 2; 2 ”along one or more interfaces 44, 45; 45 '; 45 ”or master planes, then the radial extension (s) are also subdivided correspondingly or along these very interfaces 44, 45; 45 '; 45 ”or master plans. Several parts of the toothless connecting element 3; 3 '; 3 ”can be attached to each other, e.g. screwed together as shown in fig. 4 by means of the screw 47.

If, on the other hand, a collar 42 or flange 43 projecting towards the slot 14 'is missing; 14 ”, then a subdivision of the toothless connecting element in accordance with a main plan may not be necessary for the installation. Thus, one or more radial extension (s) 27; 27 '; 27 ”; 27 ”” should also not be subdivided, as shown in fig. 5. As can be seen from FIG. 2, 3 and 5, the toothing 15; 15 '; 15 ”preferably be arranged between two rows of roller bodies 39, 40, 41; 39 ', 40'; 39 ”, 40” ”by a swivel joint 1; 1 '; 1 ”; 1 ”with several rows of roller bodies 39, 40, 41; 39 ', 40'; 397, 40 ”. Therefore, the roller body rows 39, 40, 41; 39 ', 40'; 39 ", 40" are placed at a distance from each other without having to increase the pivot connection 1; 1 °; 1 ”; 1”. "As a result still subdivided, the toothing 15; 15" can be placed as a raised, straight toothing on the free radial front of the relevant collar or flange-like elevation 42, 43, so that the mounting is neither affected nor impossible.

DK 180487 B1 22 If the toothing 15 '; 15 ”on the other side in the area of the gap 14 '; 14 ”is not mounted on a raised collar 42 or flange 43, the toothed connecting element 3 'needs; 3 ”” also not to be subdivided, as shown in fig.

5. | in such a case, the toothing 15 '; 15 ”in the cladding surface 12 '; 12 ”” on the toothed connecting element 2 '; 2 ”facing the column 14 '; 14 ° ”, be incorporated, especially milled in. A toothing 15; 15 '; 15 ”; 15 ”can e.g. manufactured with a cutter shaped approximately the length of a worm in a worm gear. Because the teeth of the toothing 15; 15; 15 ”; 15 ”must not run obliquely because they do not engage the teeth with a screw, but with one or more gears 29; 29 '; 29 ”; 29 ”, such a milling tool should not have a pitch like a worm gear. On the contrary, the inserts can be arranged circularly around the milling axis.

A straight tooth 15; 15 ”on an exposed part, ie. on a collar 42 or on a flange 43, can be obtained by advancing a milling tool parallel to the axis of rotation 11 on the toothed connecting element, or on the connecting element to be toothed 2; 2 ”. The same technique can also be used if - as shown in fig. 5 - the area to be toothed is at least elevated on an adjacent area in the axial direction opposite the adjacent cladding surface 12 "on the slot 14", although this is not the case on the opposite adjacent cladding surface 12 "on column 14 ”. | in the latter case, however, a cutter for making the toothing 15 ”” must not be pulled through, but must move back in the axial direction again, or in the radial direction out of the toothing 15. | in both cases, at the turning point of the cutter, a circular arcuate section of the recess between adjacent teeth remains, as shown in fig. 5. If, on the other hand, a toothing 15 'is to be incorporated in an area of the cladding surface 12' facing the slot 14 'which is not raised on both sides, a radial advance of the milling tool vertically to the axis of rotation 11 on the toothed connecting element, or on the connecting element to be toothed 2 ', so as to obtain the tooth geometry shown in fig. 3.

DK 180487 B1 23 Gear 29; 29 '; 29 ”; 29 ”geometry must be adapted to the toothing 15; 15 '; 15 ”; 15 ”geometry. Ie. that by a straight toothing 15; 15 ”; 15 ”- preferably in an area of the cladding surface 12; 12 ”; 12 ”, which is at least elevated on one side - must be a corresponding toothing on the gear 29; 29 ”; 29 ”. If the toothing 15 'has an arcuate tooth geometry in the longitudinal direction or in the axial direction, i.e. parallel to the main axis of rotation 11, as caused by a radial advance of the milling tool and as seen in fig. 3, a gear 29 'which engages therewith must have a corresponding, preferably cap-shaped tooth geometry. It could, for example. milled out of a ball after a jacket at the top and bottom has been removed from it, e.g. sawn off.

As long as a gear 29 has not yet been set; 29 '; 29 ”; 29 ”” on the shaft 33 in question, it has clearance inside the chamber 28; 28 '; 28 ”; 28 '”and can be temporarily moved away from the slot 14 within the same; 14 '; 14 ”: 14” ”to set the two annular connecting elements 2, 3; 2, 3 '; 2 ", 3": 2 ", 3" together. For this purpose, the chamber 28; 28 '; 28 "; 28" "can be dimensioned a little abundantly.

In the case of embodiments of a rotary joint 1; 1 '; 1 ”with one in the area of chamber 28; 28 '; 28 ”along a divider 44, 45; 45 '; 45 ”or a main plane un toothed connecting element 3; 3 '; 3 ”, which is subdivided into several rings, the gear wheel 29; 29 ”; 29 ”is inserted into the chamber 28; 28 '; 28 ”from an opening on the front, ie. an opening on the top or bottom, which occurs by removing a split ring on the top or bottom. Thus, the chamber 28; 28 '; 28 ”geometry in the area at its opening towards the slot 14; 14 '; 14 ”limited only by the requirement that neither the toothing 15; 15 '; 15 ”or gear 29; 29 '; 29 ”may roam against anywhere.

If a subdivision of the toothless connecting element 3 ”is not necessary for the assembly and in fact is not planned either, as in particular in the form of making a rotary connection 1” shown in fig. 5, then the gear 29 ”must be inserted into the chamber 28” from the opening facing the slot. For this purpose

DK 180487 B1 24, the opening of the chamber 28 "facing the slot 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 an inner surface 48 ”” in the chamber 28 ”on the cladding side at most along a center angle y about the eccentric axis of rotation 23" on the gear 29 ”at y = 180 ° follow a rotationally symmetrical course, in particular a cylindrical or capillary course, namely in the area facing away from the slit 14 "". | the rest of the area facing the slit 14 ", ie within a center angle of 360" - y, they should to it on it curved area on the inner cladding surface 48 "" adjacent sections either follow parallel courses in relation to each other, or towards the gap 14 "" even diverge from each other.

FIG. 3 and 5 show - and represent all figures, for there may be a corresponding design of all kinds of execution of a rotary connection 1; 1 °; 1 ”; 1 ”” according to the invention - that it with the gear 29; 29; 29 ”; 29 ”coupled shaft 33; 33 '; 33 ”: 33” ”that cannot be rotated may be located in the toothed connecting element 3; 3; 3 ”; 3 ”, in particular by means of one or more roller bearings 49, 50; 49 ”, 50”.

For positioning a gear 29; 29 '; 29 ”; 29 ”” | the toothed connection element 3; 3); 3 ”; 3 "" there may be at least one bearing recess 51 in the latter, preferably in the area of the chamber 28; 28 "; 28"; 28 ", especially on one or both front sides of the chamber 28; 28 '; 28"; 28 ", especially on its upper side 52 and / or lower side 53. Preferably the annular bearing recesses 51; 51" "At this point concentric with the eccentric axis 23; 23 '; 23"; 23 "" in the bore 31; 31'; 31 "; 31.

This may cause an extra hollow 54 in the area at the mouth of the bore 31; 31 '; 31 ”; 31 ”” in chamber 28; 28 '; 28 ”; 28 ”for receiving a ball or roller bearing 49; 49 ”, the outer ring of which is pressed into the hollow 54; 54 ° ”while screwing or tightening its inner ring on the shaft 33 in question. Also in the area of the front 53; 53 ”” opposite the bore of the bore 31; 31 '; 31 ”; 31 ”in chamber 28; 28 '; 28 ”: 28” ”there may be an extra hollow 51; 51 ”,

DK 180487 B1 25 also for receiving a ball or roller bearing 50; 50 ”, the outer ring of which is pressed into the hollow 51; 51 ””, while its inner ring is screwed or tightened in an area at the front of that shaft 33, where the gear 29; 29; 29 ”; 29 ”goes through.

In FIG. 4, a further development of a rotary connection 1 ”according to the invention can be recognized, in which a closing plate 55 in the area at a front side of the chamber 28” by means of screws 47 distributed as a ring 47, is screwed onto the non-toothed connecting element 3 “actual body containing chamber 28”.

The swivel connection 1 '”according to fig. 5, on the other hand, is optimized for an undivided construction of both connecting elements 2 ”; 3 ". For this purpose, the gap 14" follows a course in the axial direction, which changes stepwise. In the area in Fig. 5, which is at the top - i.e. at the level of the row of roller bodies 39 ", this slot - has the gap 14" its maximum diameter, which is larger than in a central, axial area where the toothing is located 15 ". On the other hand, the gap has 14" in the area shown at the bottom of Fig. 5 - ie on height with the row of roller bodies 40 ”this place - its minimum diameter which is smaller than the central axial area with the toothing 15”. If the two connecting elements 2 ”; 3” ”are then pushed into each other in the axial direction so that the section of the outer connecting element 3 "with a maximum inner diameter at the front is pushed into the section of the inner connecting element 2" with a minimum outer diameter, then the relevant, annular connecting elements 2 "; 3" without subdivision and without risk of a collision joined and under optimal centering to last run into each other. In order that neither of the two connecting elements 2 ° ”; 3 ”need to be subdivided, all driving gears 29” are inserted into their chambers 28 '”before the connecting elements 2”; 3 ”is joined, which can be done from the opening in question in the cladding surface of the chamber 28” ”facing the slot 14” ”. Such a joining is also made easier if the free tooth edges have a straight, linear course, as can be seen in fig. 5.

DK 180487 B1 26 | the latter example and as with all other forms of making a rotary joint 1; 1 '; 1 ”; 1 ”according to the invention, the slot in question is 14; 14 '; 14 ”: 14” sealed in the area at each mouth on the front side, in particular by means of at least one circumferential sealing element.

In addition, there may also be a seal in the area of a flanged, or otherwise attached motor 32, in particular between a mounting surface 6 intended for this; 6 ”; 6 ”” and the contact surface on the motor flange. Finally, there may also be seals in case of subdivision levels 44, 45: 45: 45 ”, Using all these measures, the cavity inside the slot 14 is; 14 ': 14 "; 14 ”and the thus communicating chamber 28; 28 '; 28 ”; 28 ”and possibly a bore 31; 31 '; 31 ”; 31 ”” associated with this, completely encapsulated and may be wholly or partly filled with a lubricant, in particular with grease. Because both the teeth 15; 15 '; 15 ”; 15 ”, which engage teeth with each other and the gears 29; 29 '; 29 ”; 29 ”on one side and the roller bodies 39-41; 39 ', 40'; 39%: 39 ”. 40 ”” and the roller bearings 49, 50; 49 ”, 50” until the relevant motor or gear shaft 33 is thus completely encapsulated, the swivel connection 1 rotates; 1; 1 ”; 1 ”” according to the invention is a closed drive. This means that a constant and uniform lubrication is ensured and also a precise guidance or placement of the parts that engage with each other, so that a long expected service life can be achieved.

DK 180487 B1 27 Reference list 1 Swivel connection 26 Connection line 2 Connecting element 27 - Extension 3 Connecting element 28> Chamber 4 Front side, connecting surface 29 - Gears Front side 30 - Teeth 6 Front side 31 Drilling 7 Front side, connecting surface 34 Front mounting 32 Motor 8 Mounting side Internal thread 35> Area 11 Center axis, axis of rotation 36 Hub 12 Cladding surface 37 - Opening 13 Cladding surface 38 - Straight line 14 Slot 39 Rolling body - Toothing 40 Rolling body 16 Cross section 41 Rolling body 17 - Cladding surface 42 Collar 18 - Outer circumference 43 Flange surface 19 Flange surface 19 Flange surface 45 Interface 21 first area 46 - groove-shaped recess 22 => second area 47 - Screw 23> Eccentric axis 48 -> Inner surface 24 Cladding surface section 49 - Rolling bearing Cladding surface section 50 - Rolling bearing

DK 180487 B1 28 51 Bearing recess, hollow shaft 52 Upper side 53 Lower side 54 Hollow joint 55 Closing plate 56 - Body 5 / - Cladding surface 58 - Circular arcuate section

Claims (31)

DK 180487 B1 1 Patentkrav Swivel connection (1; 17; 17; 1 "') with at least one, preferably at least two gears (29) and two annular connecting elements (2, 3), which are arranged to form a circumferential slot (14) concentric with each other, for connection to each a machine or plant part, a chassis or foundation, where on the two annular connecting elements (2, 3) on the surface areas (12, 13) facing their slot (14) , is at least one raceway along which a series of roller bodies (39,40,41) roll so that the two annular connecting elements (2,3) can be rotated towards each other about a main axis of rotation (11) on the rotary connection (11:11) , and wherein at least a first of the annular connecting elements (2,3) on whose surface area (12) facing the slot (14) is a circumferential toothing (15), with which at least one gear (29) engages in teeth, if pivot axis (23) is parallel to the main axis of rotation (11) of the pivot joint (1; 1 '; 1 ”; 1” ”) and is received and / or located in a different that of the annular connecting elements (2, 3), wherein at least one chamber (28) is open towards the slot (14) for receiving a gear (29) which engages with the toothing (15) incorporated, or molded into the second non-toothed, annular connecting element (2), or in at least one annular part of the same, and which is enclosed against the surroundings of the rotary connection (1; 1; 1 ”; 1” 7), characterized by the circumferential toothing (15 ) on the first annular connecting element (2) is located on a front side of a circumferential collar (42), the flanks of which are designed as raceways for each a series of roller bodies (39, 40). Swivel connection (1; 1; 1 ”; 1 '”) according to one of the preceding claims, characterized in that the toothed connecting element (2) and / or the gear wheel (29) which engages with it, is obliquely toothed and / or straight-toothed. Swivel connection (1: 1 '; 1 ”: 1” ”) according to one of the preceding claims, characterized in that the circumferential toothing (15) on the first annular connecting element (2) is located between two raceways for each a series of roller bodies (39,40,41). DK 180487 B1 2 Swivel connection (1; 1 ': 1 ”: 1” ”) according to one of the preceding claims, characterized in that the circumferential toothing (15) of the first annular connecting element (2) is located in an area (42; 43) in radial direction opposite an adjacent raceway on the same connecting element (2). Swivel connection (1: 1 '; 1 ”: 1” ”) according to one of the preceding claims, characterized in that the second non-toothed connecting element (3) is subdivided into two rings lying one above the other, which abut. each other along a joint (44,45). Swivel connection (1; 1; 1 ”: 1” ”) according to one of the preceding claims, characterized in that the second connecting element (3) has an approximately C-shaped cross section (19) with a circumferential, groove-shaped recess ( 46) in the area of the gap (14). Swivel connection (1; 1 ': 1 ”: 1” ”) according to claim 6, characterized in that the chamber (28), the second connecting element (2) being located at the level of the groove-shaped recess (46) and is open to this. Swivel connection (1: 1 '; 1 ”: 1” ”) according to one of the preceding claims, characterized in that the chamber (28) in the second connecting element (3) in radial direction, related to the gear wheel accommodated therein ( 29) axis of rotation (23) along a first center angle 5 is open towards the slot (14), e.g. along a first center angle 5> 60 °, preferably along a first center angle 5> 75 °, in particular along a first center angle 5> 90 °. Swivel connection (1; 1; 1 ”; 1 '”) according to one of the preceding claims, characterized in that the chamber (28) in the second connecting element (3) in radial direction, related to the gear wheel (29 accommodated therein) axis of rotation (23) along at least one other center angle € is bounded by a rotationally symmetrical bearing surface (48), e.g. along a second center angle €> 120 °, preferably along a second center angle c> 150%, especially along a second center angle €> 180 °. DK 180487 B1 3 Swivel connection (1; 1 ';: 1 ”: 1” ”) according to claim 9, characterized in that the rotationally symmetrical area of the cladding surface (48) of the chamber (28) has the same shape as a cladding surface of a hollow cylinder , a hollow barrel or a hollow cap. Swivel connection (1; 1; 1 ”; 1 '”) according to one of the preceding claims, characterized in that the chamber (28) in the second connecting element (2) in radial direction, related to the gear wheel (29 accommodated therein) ) axis of rotation (23), along at least one additional center angle range €, follows a straight course, e.g. from the edges of the opening of the chamber (28) to the slot (14) to the beginning of the rotationally symmetrical restraining surface. Swivel connection (1; 1; 1 ”; 1” ”) according to claim 11, characterized in that the chamber (28) in the second connecting element (3) in the radial direction, related to the axis of rotation (29) of the gear wheel (29) accommodated therein 23), along at least a third center angle {1 and a fourth center angle (2, bounded by parallel, planar surfaces relative to each other, eg along a third center angle {1> 15 ° and along a fourth center angle) angle (2> 15 °, preferably along a third center angle {1> 30 ”and along a fourth center angle € 2> 30 °, especially along a third center angle {1> 45 ° and along a fourth center angle {2> 45 °. Swivel connection (1; 1: 1 ”: 1” ”) according to one of the preceding claims, characterized in that the chamber (28) in the second connecting element (3) is delimited in the axial direction by a flat upper side (52) and a parallel, flat underside (53). Swivel connection (1; 1; 1 ”; 1 '”) according to one of the preceding claims, characterized in that in the area at the upper side (52) and / or lower side (53) of the chamber (28) there is a bearing ( 49, 50) to a shaft (33) driving the gear (29). Swivel 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 is designed as a radial bearing. DK 180487 B1 4 Swivel joint (1; 1: 1 ”: 1” ”) according to one of the preceding claims, characterized in that the second connecting element (3) on its cladding surface (20) facing away from the slot (14), in the area of the chamber (28) has a thickening in the form of a radial extension (27). Swivel connection (1; 1: 1 ”: 1” ”) according to one of the preceding claims, characterized in that an opening or bore (31) for receiving a drive shaft (33) for the gear (29) which moves in tooth engagement with the toothing (15), extends to a flat outer surface (6) of the second connecting element (3). Swivel connection (1; 1; 1 ”; 1” ”) according to claim 17, characterized in that in the area at the mouth of the opening or bore (31) of the gear (29) which engages with the toothing (15) ), in a planar outer surface (6) of the second connecting element (3), is one or more means for attaching the housing to a drive motor (32), e.g. one or more mounting holes, preferably distributed as a ring around the mouth. Swivel connection (1; 1: 1 ”: 1” ”) according to one of the preceding claims, characterized in that the flat outer surface (7) of the second connecting element (3) opposite the mouth of the opening or bore (31) for receiving a drive shaft (33) for the gear wheel (29) which engages with the toothing (15) is designed as its connecting surface, for abutting against a machine or plant part, a chassis or foundation to be connected. Swivel connection (1; 1; 1 ”; 1” ”) according to one of the preceding claims, characterized in that there are mounting means in the flat connection surface (7) on the second connection element (3) for connection to a machine or plant part, a chassis or foundation to be connected, preferably mounting holes (9) distributed as a ring around the main axis of rotation (11) of the swivel connection (1; 1; 1 ”; 1 '”), in particular blind holes (9) with internal thread (10). Swivel connection (1; 1 ': 1 ”: 1” ”) according to one of the preceding claims, characterized in that the connecting surface (7) of the second connecting element (3) faces the adjacent DK 180487 B1 front side (5) of the first connection element (2) in the axial direction is designed to be raised. Swivel connection (1; 1 ': 1 ”: 1” ”) according to one of the preceding claims, characterized in that the slot (14) is sealed in the area at its mouths in the area at the top and bottom of the rotary joint (1; 1 '; 1 ”; 1). Swivel connection (1; 1: 1 ”; 1” ”) according to claim 22, characterized in that the gap (14) in the sealed area is completely or partially filled with a lubricant, preferably with grease. Swivel joint (1; 1 ': 1 ”: 1” ”) according to one of the preceding claims, characterized in that the circumferential toothing (15) is arranged on the inner and / or concave arched cladding surface (13) on the radially external connecting element (3). Swivel joint (1; 1; 1 ”; 1” ”) according to one of Claims 1 to 23, characterized in that the circumferential toothing (15) is arranged on the outer and / or convexly arched cladding surface (12) on the radially inner connecting element (2). Swivel connection (1; 1; 1 ”; 1 '”) according to one of the preceding claims, characterized in that several chambers (28), which are open towards the slot (14), each receive a gear wheel (14). 29) which engage in tooth engagement with the toothing (15) is incorporated or molded into the second non-toothed annular connecting element (3), or in at least one annular part of the same, preferably evenly distributed over the circumference of the toothing (15), i.e. staggered relative to each other at the same intermediate angles. Manufacturing method for manufacturing a rotary joint (1; 1; 1 ”; 1” ”) according to claim 1, characterized in that the circumferential toothing (15) on the first toothed, annular connecting element (2) together with at least one of its raceways for roller bodies (39, 40, 41) rolling along it are made by machining and / or shaping a first main part, in particular by preferably machining the same. DK 180487 B1 6 Manufacturing method for manufacturing a rotary joint (1; 1; 1 ”; 1” ”) according to claim 1, wherein at least one chamber (28) open to the slot (14) for receiving a gear (29) , which engages the tooth (15) in another non-toothed, annular connecting element (2), or a part of the same, together with at least one of its raceways for roller bodies (39, 40, 41) rolling along it, produced by the working and / or shaping of another main part, in particular by preferably machining of the same. Swivel connection (1; 1 ': 1 ”: 1” ”) according to one of Claims 1 to 26, characterized in that the outer cladding surface 20 is designed in a circular manner. Swivel connection (1; 1 '; 1 ”: 1” ”) according to one of Claims 1 to 26, characterized in that the gear wheel (29) is integrated in the drive. Swivel connection (1; 1; 1 ”: 1” ”) according to one of Claims 1 to 26, characterized in that the drive is an encapsulated drive.