Drive mechanism for rotatably coupling a system part or a machine part

Abstract

The invention relates to a drive mechanism (1) for rotatably coupling a first system part or machine part, preferably an assembly (A), to a base, pedestal or frame or to another system part or machine part, for example for rotary positioning during the processing of large workpieces or during the moving of loads, which drive mechanism comprises two ring-shaped connecting elements (3, 4) each having at least one planar connecting surface (5, 6) and fastening means (7, 8) that are arranged distributed in a crown shape therein and effect connection to different system parts or machine parts or the like, said two connecting elements (3, 4) being arranged concentrically with each other and radially one inside the other with a gap-shaped interspace (9) in which are disposed one or more rows of rolling elements (14, 15, 16), each row whereof rolls between two respective raceways (17, 18) on the two connecting elements (3, 4), thus enabling same to rotate relative to each other, at least one connecting surface (5, 6) and at least one raceway (17, 18) being formed by machining or shaping a common base body. The invention is characterized in that at least one fully circumferentially extending row of magnets (40) is arranged inside the gap (9) on one connecting element (3, 4) and at least one fully circumferentially extending row of coils (38) is arranged directly opposite said magnets on the other connecting element (4, 3). According to the invention, at least one fully circumferentially extending row of magnets is arranged inside the gap on one connecting element and at least one fully circumferentially extending row of coils is arranged directly opposite said magnets on the other connecting element.

Claims

1. A drive mechanism (1) for rotatably coupling a first system part or machine part, preferably an assembly (A), to a base, pedestal or frame or to a second system part or machine part, for example for rotary positioning during the machining of large workpieces or during the moving of loads, comprising two ring-shaped connecting elements (3, 4) each having at least one planar connecting surface (5, 6) and fastening means (7, 8) that are arranged distributed in a crown shape therein and effect connection to different system parts or machine parts or the like, said two connecting elements (3, 4) being arranged concentrically with each other and radially one inside the other with a gap-shaped interspace (9) in which are disposed one or more rows of rolling elements (14, 15, 16), each row whereof rolls between a respective two raceways (17, 18) on the two connecting elements (3, 4), thus enabling same to rotate relative to each other, at least one connecting surface (5, 6) and at least one raceway (17, 18) being formed by machining or shaping a common base body, characterized in that arranged inside the gap (9), on one connecting element (3, 4), is at least one fully circumferentially extending row of magnets (40) and, directly opposite thereto, on the other connecting element (4, 3), at least one fully circumferentially extending row of coils (38).

2. The drive mechanism (1) as in claim 1, characterized in that the gap (9) opens onto two different end sides of the drive mechanism (1).

3. The drive mechanism (1) as in claim 1, characterized in that the connecting surfaces (5, 6) of the two connecting elements (3, 4) are located on end sides of the drive mechanism (1) that face away from each other.

4. The drive mechanism (1) as in claim 1, characterized in that two connecting elements (3, 4) are braced directly against each other in the axial direction via at least one rolling element row (14) disposed between them, the respective raceway (17, 18) on each of the two connecting elements (3, 4) being formed, together with the respective planar connecting surface (5, 6), from a respective common base body.

5. The drive mechanism (1) as in claim 1, characterized in that provided on at least one connecting element (3, 4) is a ring-shaped collar (31) suitable for being clamped, preferably in an axial direction, between two brake shoes.

6. The drive mechanism (1) as in claim 1, characterized in that a plurality of magnets (40) are connected to one another, for example by a common support body (53), to form a common segment body.

7. The drive mechanism (1) as in claim 1, characterized in that the magnets (40) are arranged such that their respective magnetic north and south poles alternate with each other in the circumferential direction of the gap (9).

8. The drive mechanism (1) as in claim 1, characterized in that the magnets (40) are arranged in a plurality of approximately axially parallel rows, in such fashion that the magnetic north and south poles within a row are all oriented parallel to one another.

9. The drive mechanism (1) as in claim 8, characterized in that the rows of magnets (40) having the same magnetic orientation do not extend exactly parallel to the axis of rotation of the drive mechanism (1), but rather at a slight angle thereto, if appropriate in two different circumferential directions in different sections.

10. The drive mechanism (1) as in claim 1, characterized in that the coils (38) are fastened to core bodies (42) which in turn are fastened, preferably tightly screwed, to a circumferential surface (37) in the region of the gap (9).

11. The drive mechanism (1) as in claim 10, characterized in that the gap section (10) receiving the rolling elements (13, 15, 16) is offset in the axial direction, i.e. in the direction of the axis of rotation (2), from the gap section (11) receiving the magnets (40) and coils (38).

12. The drive mechanism (1) as in claim 10, characterized in that the gap section (10) receiving the rolling elements (14, 15, 16) is separated by a fully circumferential seal (24) from the gap section (11) receiving the magnets (40) and coils (38).

13. The drive mechanism (1) as in claim 1, characterized in that a plurality of coils (38) are united to form a common segment, particularly by being mounted on a common segment body (42).

14. The drive mechanism (1) as in claim 1, characterized in that the interconnection of adjacent coils (38) or coil segments (43) takes place on the back side (47) of that section (34) of the particular connecting element (3, 4) which carries the coils (38) or in the region of a mouth of the gap (9).

15. The drive mechanism (1) as in claim 14, characterized in that the contacting of the coils (38) takes place via bores in that section (34) of the particular connecting element (3, 4) which carries them or in the region of a mouth of the gap (9).

16. The drive mechanism (1) as in claim 1, characterized in that a plurality of coils (38) are connected in series.

17. The drive mechanism (1) as in claim 1, characterized in that three strings (ft S, T) of coils (38) are provided, corresponding to a three-phase system.

18. The drive mechanism (1) as in claim 17, characterized in that in each string (ft S, T), ten coils (38) or more are connected in series, for example respectively twenty coils (38) or more, preferably thirty coils (38) or more, particularly forty coils (38) or more.

19. The drive mechanism (1) as in claim 17, characterized in that the strings (ft S, T) are connected at one end (48) in a star or a delta configuration.

20. The drive mechanism (1) as in claim 17, characterized in that the strings (ft S, T) are supplied on the input side by a current converter, particularly by a three-phase current converter or a three-phase current inverter.

21. The drive mechanism (1) as in claim 1, characterized by a rotation angle sensor, for example in the form of an incremental encoder.

22. A ship, vehicle or heavy-duty vehicle and/or construction machine, for example a heavy-duty crane or mobile crane or bucket-wheel excavator or port/ship crane or tunneling machine or (special) lifting machine, comprising at least one drive mechanism (1) as set forth in claim 1, wherein such drive mechanism (1) can set in motion or drive in rotation at least one set of wheels and/or chains, particularly replacing a mechanical steering gear(s).

23. The ship, vehicle or heavy-duty vehicle and/or construction machine as in claim 22, wherein such a drive mechanism (1) can set in motion or drive in rotation at least one preferably horizontally or vertically rotatable or pivotable assembly (A), said assembly (A) being embodied, for example, as an antenna tower or as a gun carriage or as an excavator arm or as a lifting arm or as a boom lift/platform lift or as an operator's cab or as a telescopic boom or as a rotating ladder platform, ideally even as the boring head of a tunneling machine.

24. The ship, vehicle or heavy-duty vehicle and/or construction machine as in claim 23, characterized in that at least one pivotable assembly (A) allows itself to be placed directly, for example in abutment or in a flange-like manner, against at least one connecting element (3, 4) and is fastenable to the drive mechanism by fastening means (7, 8), preferably screw connections, arranged distributed in a crown shape, wherein the axis of rotation (2) of the particular drive mechanism (1) and the center axis or axis of rotation of the assembly (A) overlap or, ideally, are aligned on a common axis.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Further features, details, advantages and effects based on the invention will become apparent from the following description of a preferred embodiment of the invention and by reference to the drawing. Therein:

(2) FIG. 1 shows a drive mechanism according to the invention in a plan view of an end side;

(3) FIG. 2 is a section through FIG. 1 along line II-II, schematically indicating on the left side of the drawing an assembly (A) fastened by fastening means (8).

(4) FIG. 3 shows detail III from FIG. 2 in an enlarged representation, but without an installed drive mechanism;

(5) FIG. 4 is a perspective view of the cross section according to FIG. 3 after the installation of the drive mechanism, viewed from an approximately tangential direction;

(6) FIG. 5 shows approximately the same detail as FIG. 4, also in perspective representation, but viewed from an approximately axial direction;

(7) FIG. 6 is a view of the inner side of the outer connecting element, partially broken away; and

(8) FIG. 7 is a circuit diagram for the electrical contacting of the individual coil segments.

(9) FIG. 8a illustrates one possible application of the inventive mechanism to driving a set of wheels, replacing a mechanical steering gear(s).

(10) FIG. 8b shows a second possible application of the inventive mechanism to driving a rotatable assembly (A), where said assembly constitutes the upper portion of a rotatable tower on a vehicle (ship).

(11) FIG. 9a shows a third possible application of the inventive mechanism to driving a rotatable assembly (A), where said assembly constitutes the upper portion of a rotatable tower on a large construction crane (port crane/construction machine).

(12) FIG. 9b shows a third possible application of the inventive mechanism to driving a rotatable assembly (A), where said assembly constitutes the upper portion, pivotably or rotatably implemented, of a large bucket-wheel excavator (construction machine).

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

(13) As can be appreciated from FIG. 1, the drive mechanism 1 according to the invention for rotatably coupling two system parts or machine parts or the like has a ring-shaped structure and is rotationally symmetrical to a center axis 2 of said ring structure.

(14) An essential element of the drive mechanism 1 is two ring-shaped, substantially planar connecting elements 3, 4.

(15) Each of these connecting elements 3, 4 is provided with at least one respective planar connecting surface 5, 6 together with fastening means 7, 8, arranged distributed in a crown shape therein and provided for connection to different system parts or machine parts or the like. These fastening means are preferably bores for receiving fastening screws, for example internally threaded blind bores or through-bores. The connecting surfaces 5, 6 of the two connecting elements 3, 4 are preferably located on oppositely disposed end sides of the drive mechanism 1, i.e., for example, one at the top and one at the bottom as depicted in FIG. 3.

(16) The two connecting elements 3, 4 are arranged concentrically with the common center point 2, through which passes—perpendicularly to the main plane of the connecting elements 3, 4—the axis of rotation 2 about which the two connecting elements are able to rotate relative to each other.

(17) In addition, the two connecting elements 3, 4 are arranged radially one inside the other; in the example illustrated, connecting element 3 is radially inside the central opening of the other connecting element 4.

(18) Between the two connecting elements 3, 4 there is a gap-shaped interspace 9 that is divided essentially into two sections, specifically into a bearing section 10 and a drive section 11.

(19) The width of the gap 9 is dimensioned such that the mutually facing surfaces 12, 13 of the two connecting elements 3, 4 are farther apart from each other in the drive section 11 than in the bearing section 10, with the result that more space is left in the drive section 11 than in the bearing section 10, at least as long as no additional parts are received therein.

(20) As can be understood from FIG. 3, disposed in the bearing section 10 are one or more rows of rolling elements 14, 15, 16, each row whereof rolls between a respective two raceways 17, 18 on the two connecting elements 3, 4, thus enabling same to rotate relative to each other.

(21) In the illustrated example, there is a plurality of rows of rolling elements 14, 15 with a large pressure angle or contact angle α of more than 45°, for example 60° or more, preferably 75° or more, particularly approximately 90°, and at least one row of rolling elements 16 with a small pressure angle or contact angle α of less than 45°, for example 30° or less, preferably 15° or less, particularly approximately 0°. The pressure angle or contact angle α is measured in this case between the radial or main plane and the line of the pressure acting on a rolling element. The radial or main plane of the drive mechanism 1 is intersected perpendicularly by the axis of rotation 2.

(22) Said rolling elements 14, 15 with a large pressure angle or contact angle α are responsible for the parallel alignment of the main planes of the two ring-shaped connecting elements 3, 4. In the example shown, there are two rows of such rolling elements 14 for transmitting axial pressure forces between the connecting surfaces 5, 6 on opposite end sides of the drive mechanism 1, while one row of such rolling elements 15 serves to transmit axial pressure forces between these connecting surfaces 5, 6.

(23) To achieve this, one of the two connecting elements 3, 4—in the example shown, the radially inwardly disposed connecting element 3—has a fully circumferentially extending collar 19 of approximately rectangular cross section that protrudes radially to the other connecting element 4, 3 and is embraced—spaced by the gap 9—by the other connecting element 4.

(24) A raceway 17 for the row(s) of rolling elements 14 transmitting axial pressure forces is disposed on the connecting surface 5 of the connecting element 3, 4 carrying the collar 19—in FIG. 3, on the top side 20 of the collar 19—while a raceway for the row(s) of rolling elements 15 transmitting axial tensile forces is provided on the opposite side of the collar 19—in FIG. 3, on its bottom side 21.

(25) The rolling elements 16 having a small pressure angle or contact angle α roll along a raceway 17 on the end side 22 of the collar 19.

(26) All these rows of rolling elements 14, 15, 16 have their respective other raceway 18 on the inner side of a fully circumferentially extending depression 23 surrounding the collar 19 and disposed on the respective other connecting element 4, 3.

(27) The illustrated embodiment has roller-shaped rolling elements 14, 15, 16, but this is not mandatory; other rolling element geometries may be contemplated, for example spherical rolling elements 14, 15, 16. Naturally, different rows of rolling elements 14, 15, 16 can also have different rolling element geometries.

(28) The bearing section 10 of the gap 6 is sealed on each side—i.e., beyond the innermost rolling element row 14, on the one side, and outside of the outermost rolling element row 15, on the other side—by at least one respective fully circumferentially extending sealing element 24, 25, and can thus be filled with a lubricant—preferably with grease—which the sealing elements 24, 25 prevent from leaking out, on the one side, and from getting into the drive section 11, on the other side.

(29) To avoid problems during the assembly of the drive mechanism 1, the connecting element 3, 4 that has the depression 23 embracing the collar 19 is divided in the region of the depression 23, in a plane parallel to the main or radial plane of the bearing, into a ring 26 provided with connecting surface 6 and a ring 27 detachably fixed thereto. This connection is preferably made by means of screws 28 that are arranged distributed in a crown shape and extend parallel to the axis of rotation 2 of the bearing, and that engage in mutually aligned bores 29, 30 in said two rings 26, 27 and are tightly screwed therein. One row of bores 29 provided for this purpose is preferably embodied as internally threaded blind bores, while the other bores are embodied as through bores.

(30) In the illustrated embodiment, the ring 26 comprising connecting surface 6 has a larger cross section than ring 27 fixed thereto. This is due primarily to the smaller height of the latter. However, one of the two rings 26, 27—in the illustrated example, the ring 27 opposite the connecting surface 6 of the particular connecting element 3, 4—can have a radial extension in the form of a fully circumferential collar 31 on its jacket surface 32 facing away from the gap 9. This collar 31 has approximately the shape of a brake disk and can be embraced axially by brake shoes to fixedly brake the particular connecting element 3, 4.

(31) A braking device can be useful in particular when—as the invention further provides—the inventive drive mechanism 1 is part of a clamping jig for a workpiece that is to be machined. The braking device can then be tightened during a machining step—i.e., while a workpiece is engaged—whereas it is released for rotational adjustment and calibration.

(32) For the rotary positioning of large workpieces, a rotating mechanism 1 according to the invention can be installed in a round rotary table, particularly in a horizontal orientation below and parallel to the table surface. The table plate or support plate would then be placed on top of the highest connecting surface 6 and screwed down tight, while the brake is anchored to the base or frame of the machine tool.

(33) As can further be seen from FIG. 3, the section through the drive mechanism 1 reveals an approximately axial, i.e. vertical, line that extends between the two connecting surfaces 5, 6 and passes through the pressure/rolling elements 14. The rotating mechanism 1 thus is designed to have maximal rigidity to axial pressure forces.

(34) Furthermore, a respective one of the two raceways 17, 18 for the pressure/rolling elements 14 is formed by machining or shaping a base body, into which the connecting surface 5, 6 of the particular connecting element 3, 4 is also incorporated or shaped.

(35) As can further be seen from FIG. 3, the connecting element 3, 4 comprising the collar 19 is also divided into two rings 33, 34. One of them—in the embodiment shown in FIG. 3, the lower ring 33—bears the connecting surface 5 of the particular connecting element 3, 4 and the collar 19 and essentially bounds the bearing section 10 of the gap 9, whereas the drive section 11 of the gap 9 is bounded primarily by the other ring 34, at least in the radial direction. The two rings 33, 34 are fixedly connected to each other by a plurality of fastening means arranged distributed in a crown shape. This connection can preferably be embodied similarly to the connection between the two rings 26, 27, i.e., via screws that are turned in mutually aligned bores.

(36) As can further be seen from FIG. 3, the drive section 11 of the bearing gap 9 has a greater width W than the bearing section 10, to leave sufficient space for the yet-to-be-installed drive mechanism. The width W of the drive section 11 can be, for example, on the order of a few centimeters, for example between 1 cm and 20 cm, preferably between 2 cm and 15 cm, particularly between 5 cm and 12 cm.

(37) The height of the ring 34 flanking the drive section 11 in this case is approximately equal to the axial extent of the drive section 11 of the bearing gap 9. The resulting height extent H of the drive section 11 parallel to the axis is preferably greater than its radial width. It can also be on the order of a few centimeters, for example between 2 cm and 40 cm, preferably between 5 cm and 30 cm, particularly between 10 cm and 25 cm.

(38) Where appropriate, the two rings 33, 34 can be centered on each other, for example in that the ring 33 forming the bearing section 10 of the gap 9 has a fully circumferential channel 35 into which the adjoining region of the other ring 34 can be exactly fitted.

(39) The upper, free end side 36 of the ring 34 bounding the drive section 11 of the gap 9 terminates below the connecting surface 6 formed at that end side, i.e., in front of it in the axial direction or within it.

(40) The assembly installed in the drive section 11 of the gap 9 is divided into two mutually separate constructional units:

(41) Whereas electrical coils 38 are fastened to one flank 37 of said drive section 11, magnets 40 are fastened to the opposite flank 39.

(42) A multiplicity of coils 39 are arranged one after another in the circumferential direction of the gap 9. So that they can be supplied from a three-phase electrical current system, i.e., for example having three phases R, S, T, their number should be divisible by 3.

(43) Since the diameter of that flank 37 of the drive section 11 of the bearing gap 9 which carries the coils is preferably greater than 1 meter, preferably 2 meters or larger, particularly 3 meters or more, this flank 37 consequently has a circumference C on the order of 3 meters or more, preferably of 6 meters or more, particularly of 9 meters of more.

(44) With such a large circumferential length, there would be no difficulty arranging a larger number n of coils 38 successively in a row, for example 60 coils 38 or more, preferably 90 coils 38 or more, particularly 120 coils 38 or more.

(45) The coils used for this purpose are preferably thin coils 38 having a height h parallel to the axis that is greater than their azimuthal extent a in the circumferential direction. If they are tightly spaced, the following requirement results:
H>h>a=C/n=D.Math.π/n.

(46) The height H of the flank 37 parallel to the axis is greater than its circumference C divided by the number n of coils 38.

(47) The cross section of the wire used for the coil winding should be chosen to be large enough to permit currents I in the range of 1,000 A or more.

(48) Preferably, a plurality of coils 38 are connected in series in each case, preferably to form three strings R, S, T. Every third coil 38 in this case is assigned to a common string R, S, T and the respective two intervening ones to the other two strings R, S, T. This interconnection can take place, for example, in the region of the respective adjoining mouth of the gap 9.

(49) In this way, a plurality of adjacent coils—for example 12, 15 or 18—can be connected to one another to form segments 41, which are illustrated in FIG. 7. Such segments 41 can then be installed or removed together.

(50) One or more coils 38 preferably rest on a core body or segment body 42, preferably made of a magnetically soft material. The coils 38 can be wound separately therefrom and then slid onto the core body or bodies 42. These core bodies 42 are then fastened—preferably screwed, by a plurality of radial screws—to the designated flank 37 of a connecting element 3, 4 in the region of the drive gap 11.

(51) To hold the coils 38 immovably in place, they should be embraced on the gap side by the core body or bodies or the segment body or bodies 42. To achieve this, the radial extent, referred to the bearing rotation axis 2, of the core bodies or segment bodies 42 is greater than the relevant dimension of the coils 38, and the latter are inserted in channels and/or groove-shaped depressions on the surface of the core bodies or segment bodies 42 facing away from the gap 9. In the case of core bodies 42 intended to hold individual coils 38, a channel running around the edge will suffice for this purpose; segment bodies 42 for a plurality of coils 38, however, should always have groove-shaped depressions in the inner region.

(52) After all the core or segment bodies 42, including the electrical coils 38, have been fixed in place, these coil segments 43 are electrically connected to one another, particularly respectively in a three-phase manner, i.e., so as to form three strings R, S, T, as can be seen in FIG. 7.

(53) As can be understood from FIG. 4, axial connecting bores 44 for receiving connection screws for interconnecting the two rings 33, 34 should be offset in an azimuthal direction from the radial connecting bores 45 for receiving connecting screws for fastening the core bodies or segment bodies 42 to the gap flank 37. To ensure a constant such offset, the number b.sub.1 of axial connecting bores 44 and the number b.sub.2 of radial connecting bores 45 should be whole multiples or fractions of the number n of electrical coils 38:
b.sub.1=k.sub.1.Math.n, where k.sub.1εQ;
b.sub.2=k.sub.2.Math.n, where k.sub.2εQ.

(54) In the ideal case, it might be that b.sub.1=b.sub.2=n.

(55) The terminal connections 46 to individual coil segments 43—or at least to the first and last coil segment 43 in a string—can be routed past the free end side 36 of the gap region 9 bounding the drive section 37 or through bores in the ring 34 to that jacket surface 47 of said ring 34 which is disposed opposite the coils 38, and can there be connected to one another or to a supply voltage.

(56) The strings R, S, T are preferably connected at one end 48 in a star or a delta configuration, while the respective other end is contactable with a supply voltage, for example in a terminal box 49. All the string ends 48, R, S, T can be terminated there, so that the choice between star and delta connection and the choice of phase sequence or direction of rotation is left up to the user.

(57) The power supply to the various strings R, S, T is preferably effected via a current converter, a three-phase converter or an inverter, particularly with an approximately sinusoidally modeled output current and/or output voltage.

(58) A supplying current converter, three-phase converter or inverter can be controlled by a rotation speed regulator. To make it possible to reach a specified position precisely, it is advisable to provide a position regulator.

(59) To route the supply lines to the coils 38 without mechanical twisting, it is advisable for the connecting element 3, 4 carrying the electrical coils 38 to be non-rotatably fastened to a frame or base. The current converter can also be placed adjacent thereto or in the vicinity thereof.

(60) The connecting element 3, 4 equipped with the electrical coils 38 will therefore be designated the stator in the following discussion, and the connecting element 4, 3 that is rotatable with respect to it will accordingly be designated the rotor. In the representation of FIG. 3, therefore, the radially inwardly disposed connecting element 3 is the stator and the connecting element 4 outwardly surrounding it is the rotor.

(61) For regulation—of rotation speed or of position—a rotation or position sensor can be disposed at an exposed location on the rotatable rotor/connecting element 3, 4.

(62) For rotation angle detection, the invention recommends arranging, for example gluing, an incremental sequence on the outwardly disposed end side 50 of the collar 31 on the rotor/connecting element 3, 4, which incremental sequence can be scanned by an incremental encoder to detect the current rotation position with high accuracy.

(63) The function of rotation angle detection can be performed by two scanning devices offset from each other in the circumferential direction by approximately 90°, referred to a period of the incremental sequence, such that conclusions regarding the direction of rotation of the rotor/connecting element 3, 4 can be drawn from the sequence of the arriving pulses.

(64) Should the drive mechanism be required to furnish high outputs, this may result in high heat generation in the stator 3, 4. To prevent overheating, which, for example, could compromise the insulation of the winding, a cooling arrangement can be provided for the stator 3, 4. For this purpose, two lines 51, 52, particularly pipes, in which a coolant can circulate, can be laid on that jacket surface 47 of the stator 3, 4 which is opposite the coils 38.

(65) Such lines 51, 52 can provide cooling in and of themselves, by virtue of their thermal contact with the particular jacket surface 47. To intensify the cooling effect, it can also be provided that inside the connecting element 3, 4, i.e., inside the ring 34 carrying the coils 38, cooling bores are provided that connect two cooling lines 51, 52 at regular circumferential intervals, so the coolant is conveyed not only along the stator 3, 4, but also right through it.

(66) The magnets 40 that are fixed to that flank 39 of the drive section 11 which is opposite the coils 38 can be recognized in FIG. 6.

(67) To prepare for and simplify assembly, the magnets 40 can also be connected segmentally to one another right from the start, so the magnets 40 do not all have to be fastened to the flank 39 individually.

(68) To segmentally connect a plurality of magnets 40, the latter are first fastened, preferably glued, to relatively thin, flat support elements 53, preferably metal sheets. The support elements 53 preferably consist of soft iron.

(69) These support elements 53, together with the magnets 40 fastened or glued thereto, are then fixed—particularly screwed, preferably by means of radial screws—to the flank 39 in the region of the drive section 11 of the rotor/connecting element 3, 4.

(70) The magnets 40 are permanent magnets and are preferably magnetically hard, preferably with a particularly high pole strength. Magnets with rare-earth components have proven particularly useful due to their high pole strength; examples include samarium/cobalt or neodymium magnets or magnets made of NdFeB, an alloy of neodymium, iron and boron. If the requirements with regard to the achievable nominal torque are modest and/or the nominal torque is not critical due to the design size and number of poles of the machine, ferrite magnets may also be sufficient.

(71) The magnets 40 are relatively small and have the shape of a small plate or disk or are square. A large number of them are glued to the particular support element 53.

(72) Since the dimensions of such a magnet 40 are smaller than the axial extent of the coils 38, a plurality of magnets 40 having the same direction of polarity are usually placed one on top of the other in the axial direction, i.e., respectively either with a north magnetic pole facing the gap 9 or with a south magnetic pole directed toward the gap 9.

(73) In the azimuthal direction or in the circumferential direction along the gap 9, adjacent magnets 40 preferably have different directions of polarity, i.e., next to a magnet 40 or an axial row of magnets whose north magnetic pole faces the gap 9 is a magnet 40 or an axial row of magnets whose south magnetic pole faces the gap 9.

(74) The invention further recommends that the axial rows of magnets 40 polarized in the same respective direction not be oriented exactly parallel to the axial direction, but instead at a slight angle thereto, or in a slight > shape with an opening angle of approximately less than 180°, i.e., for example with an opening angle of 175° or less, preferably with an opening angle of 170° or less. A slight tilt of this kind causes the manifestation of the magnetic poles in the circumferential direction to be “slurred” slightly, thus improving the synchronization of the electrically driven rolling bearing 1.

(75) TABLE-US-00001 List of reference characters: 1 Drive mechanism 2 Axis of rotation 3 Connecting element 4 Connecting element 5 Connecting surface 6 Connecting surface 7 Fastening means 8 Fastening means 9 Gap 10 Bearing section 11 Drive section 12 Gap surface 13 Gap surface 14 Rolling element 15 Rolling element 16 Rolling element 17 Raceway 18 Raceway 19 Collar 20 Top side 21 Bottom side 22 End side 23 Depression 24 Sealing element 25 Sealing element 26 Ring 27 Ring 28 Screw 29 Bore 30 Bore 31 Collar 32 Jacket surface 33 Ring 34 Ring 35 Channel 36 Free end side 37 Flank 38 Electrical coil 39 Flank 40 Permanent magnet 41 Segment 42 Core body 43 Coil segment 44 Connecting bore 45 Connecting bore 46 Terminal connections 47 Jacket surface 48 End 49 Terminal box 50 End side 51 Line 52 Line 53 Support element A Assembly (rotatable)