Drive device for the rotatable coupling of a plant or machine part.

专利摘要:
The invention relates to a drive device (1) for rotatable coupling of a first plant or machine part, preferably an assembly, with a foundation, base, chassis, or a second plant or machine part, for example, for the rotatable positioning when processing large workpieces or when moving of loads, comprising two annular connection elements (3, 4) with at least one respective flat connection surface (5, 6) and arranged distributed in a ring-shaped fastening means for connection to different plant or machine parts, wherein the two connection elements (3, 4) concentric with each other and are arranged radially in one another with a gap-shaped intermediate space, wherein one or more rows of rolling elements (14, 15, 16) are arranged, each between two raceways (17, 18) on the two connection elements (3, 4) roll, so that the same are mutually rotatable, wherein at least one connection surface (5, 6) and at least one raceway (17, 18) are formed by machining or shaping in each case a common base body; is characteristic that within the gap (9) on a connection element (3, 4) at least one extending over the entire gap circumference series of magnets (40) is arranged, and this immediately opposite to the other connection element (4, 3) at least one all around extending row of coils (38).
公开号:CH709113B1
申请号:CH00937/15
申请日:2013-08-07
公开日:2018-07-13
发明作者:Frank Hubertus；Dietz Volker
申请人:Imo Holding Gmbh；
IPC主号:

专利说明:

The invention relates to a drive device for rotatable coupling of a plant or machine part with a foundation, base, chassis or other equipment or machine part, preferably for rotatable coupling of two mutually rotatable parts of a heavy load vehicle or even a construction machine, alternatively for rotatable positioning of large workpieces, comprising two annular connection elements with at least one flat connection surface and arranged in a circle distributed fasteners for connection to different plant or machine parts or the like., Wherein the two connection elements are concentric with each other and arranged radially with a gap-shaped gap, wherein one or more rows of rolling elements are arranged, which each roll between two raceways on the two connecting elements, so that they are mutually rotatable, wherein at least e a mating surface and at least one raceway by machining or shaping a common, i. one-piece body are formed.
PRIOR ART AND THE DISADVANTAGES For a rotatable coupling of a first plant or machine part with a foundation, pedestal, chassis or another plant or machine part, normally centerless large rolling bearings are used, which have a gap circumference of more than one meter, and their connection surfaces are determined by means of a plurality of annularly distributed fastening means on flat contact surfaces of the relevant plant or machine parts. Through the opening in the region of the center of such a drive device, cables, supply lines od. Like. Are performed. By forming or incorporating a pad and at least one track in a common body a degree of precision is achieved, whereby a precession movement can be completely avoided.
Frequently, there is the requirement, in addition to the rotatable coupling or leadership of two plant or machine parts to each other to be able to influence the rotational behavior itself, so the direction of rotation, speed or even angle. For this purpose, a rotationally fixed coupling with a drive motor is required. For this purpose, one of the annular connection elements is generally provided with an all-round toothing, with which a pinion or a worm meshes, which in turn is arranged on the output shaft of the drive motor. The disadvantage of this arrangement is in a mostly limited positioning accuracy due to a hardly avoidable game between the all-round teeth on the one hand and a meshing pinion or a worm on the other.
In particular, prevails in a variety of currently common ships, vehicles or heavy trucks and / or construction machines, the problem that such (heavy) vehicles or (construction) machines, although due to a entrained with the vehicle or with the machine drive Although they are movable or mobile themselves, the respective enormous (heavy-duty) vehicle or construction machine require a very high drive power Pantr./achsr for the movement of each drive unit, for example, each wheel and / or each chain drive ,
The same applies to the movement of the on or on this vehicle or heavy vehicle and / or on or on this existing arrangements: Are such arrangements, such as an antenna tower or a carriage or an excavator or a lifting arm or a lifting platform / lift or a person's pulpit or a telescopic boom or a ladder rotary platform, designed to be rotatable or pivotable, it is often necessary a very high drive power Panwachsr for the movement of such arrangements.
In particular, those mentioned above (heavy duty) vehicles and / or construction machinery, which are not operated in waters or on seas, to: - underground tunneling machines, - multi-axis driven heavy-duty cranes with a mass between 801 (tons) and 20001 (tonnes), - special vehicles with a mass of> 501, - chassis for slow moving bucket wheel excavators and / or harbor and ship cranes with a total mass of between 35001 and 18 5001, or - lifting and handling equipment with a total mass between 3001 to 50001.
In practice, so far this drive unit (s) (wheels and / or chains or the like.) Of the aforementioned (heavy-load) vehicles and / or construction machines by means of drive-strong internal combustion engines, especially by the very widespread in practice Diesel engines, set in motion.
The same applies to many of the aforementioned rotatable or pivotal arrangements, for example, for a large slewing crane or an antenna tower or a heavy carriage or a massive excavator or a lifting arm or a highly expansive dimensioned lifting platform / lift od. Like.
This in-motion displacement of the drive unit (s) or the rotatable or pivotable arrangement (s) is usually not directly, but by a switchable transmission, which with the / on the vehicle located internal combustion engine (s), is mechanically coupled. Without such a transmission, the transmission of power from the internal combustion engine to the drive device (s) or to the rotatable / pivotable arrangement as a rule according to the current state of the art is hardly possible.
Disadvantageously, it is always intrinsic to internal combustion engines, that the aufbringbare drive torque is a function of engine speed, the maximum drive torque, as opposed to electric motors, is always reached only from speeds of about n> 500 1 / min or higher. (Note: In the case of the above-mentioned electric motors of common design, a very high drive torque according to the current state of the art is already achieved in a very low rpm range.) [0011] The larger and heavier the (heavy-duty) vehicle and / or the construction machine is, then the higher the holding torque, which must be overcome by the drive torque of the internal combustion engine in order to achieve the in-motion displacement of the drive unit (s) or the rotatable / pivotable arrangement (s). In practice, this means that the internal combustion engine aboard the aforementioned vehicle and / or aboard the construction machine consumes more fuel VT the more drive work has to be performed. The more drive work is done, the greater the recoverable drive torque.
In general:
where the fuel consumption VT is proportional to the drive work done as follows:
This fuel consumption is often regarded as disadvantageous, since in particular also in the so-called. Idle the internal combustion engine fuel is consumed, i. E. even if the drive unit (s) or the rotatable / pivotable (s) arrangement (s) temporarily need not be set in motion (must).
As the aforementioned vehicles and / or construction machines, especially underground tunneling machines, harbor and ship cranes, bucket wheel excavator, od. Like. Naturally, however, a large part of their service are indeed in use, but do not have to travel long distances, works / n the internal combustion engine (s) actually a big time in so-called. Idle. This causes costs and reduces the service life of this internal combustion engine (s). An actual demand-oriented drive of the drive unit (s) or the rotatable / pivotable arrangement (s), in particular with high drive torque in the low speed range, such as by suitable electric motor components, is in fact not today in large and heavy vehicles, heavy vehicles and / or construction machinery given nationwide.
Another disadvantage is simply the fact that in most cases, the aforementioned switchable transmission is required, which is mechanically coupled to the / on the vehicle internal combustion engine (s). This additional (mechanical) transmission component is often not integrated into the internal combustion engine, but must be purchased separately and cost-generating.
OBJECT AND DESCRIPTION OF THE INVENTION From the disadvantages of the described prior art results the problem initiating the invention of creating or further developing a drive device of the generic type such that influencing of rotational variables such as direction of rotation, speed and / or angle is as immediate and instantaneous as possible is possible and thus separate mechanical transmission component (s) are dispensable.
It is also an object of the invention to provide a drive device without internal combustion engines with a high torque at low speeds. The invention should be used as broadband as possible, i. not only in stationary machines but also on (heavy duty) vehicles and / or (construction) machines.
The invention according to claim 1 or claim 22 solves the problem by arranged in a generic drive device according to the preamble of claim 1 within the gap-shaped gap on a connection element at least one extending along the relevant connection element around the rotation axis series of magnets is, and this immediately opposite to the other connection element at least one extending around the rotation axis series of coils.
In this way, the drive itself is distributed annularly and integrated directly into the pivot bearing. This integration of drive and pivot bearing eliminates the need for a mechanical gearbox in the powertrain and, as a result, there is no gearbox clearance. In addition, thereby lacks a wear-prone coupling, so that the maintenance of the drive device is simplified accordingly. Another aspect is that it also reduces the number of external parts which could be damaged by, for example, collisions. Furthermore, space is saved. A distributed over the gap circumference initiation of torque can be considered almost ideal, ie free of axial or radial forces, while, for example, a selective introduction by means of a toothing engaging on a pinion or just such a screw in addition to the torque for lack of symmetry generally also a directed horizontal force brings with it, whereby the rolling elements are additionally stressed. Furthermore, a large number of coils and magnets can be arranged along the circumference of a gap in a centerless large roller bearing, so that on the one hand at a given power density results in a good cooling effect and on the other hand a great smoothness can be achieved.
It has proven to be favorable that the gap opens at two different end faces of the drive device. As a result, the drive device is subdivided into an external connection element and into an internal connection element. By partially overlapping in the radial direction, an axially extending pressure line can be constructed for the deformation-free transmission of axial compressive forces.
Furthermore, it is recommended that the connection surfaces of the two connection elements are located on opposite end faces of the drive device. On the one hand this facilitates the assembly between two adjacent or superimposed machine or system parts; On the other hand, in such case with approximately vertical arrangement of the axis of rotation, the weight of the load-bearing machine part can be transmitted as an axial compressive force between the two connection surfaces.
It is also possible that two connection elements are supported directly on each other via at least one intermediate row of rolling bearings in the axial direction, wherein the respective career is formed together with the respective flat pad from one common body on both connecting elements. As a result, the arrangement receives a maximum rigidity against the transmission of axial compressive forces, so that the support of large axial loads is easily possible.
In the context of a preferred embodiment may be provided at least one connecting element, an annular collar, which is adapted to be clamped by two brake shoes in a preferably axial direction. This measure makes it possible, after precise adjustment of a plant or machine part to be rotated to fix the relevant position by means of a brake, so that even with high forces or torques acting - for example, in the processing of large, annular workpieces - the maintenance of the desired position is ensured ,
In a preferred embodiment, a plurality of magnets are connected to one another to a common segment body, for example, by a common carrier body as a connecting plate od. Like. Thereby, on the one hand, the assembly can be prepared and facilitated. In addition, such magnetic segment body od easily with the help of templates od. Like. Make with a high repeatability, which is important for the geometric parallel alignment of the magnets, but also with regard to a constant distance to the respective gap wall or to the opposite row of coils.
The magnets should be arranged such that alternating magnetic north and south poles each other in the circumferential direction.
It has been proven that the magnets are arranged in several, approximately paraxial rows, such that the magnetic north and south poles are aligned within a row all parallel to each other.
The rows do not have to run exactly parallel to the axis of rotation of the drive device, but in a preferred embodiment may be slightly oblique, possibly in different sections in two different circumferential directions.
The coils may be attached to cores, which in turn are attached to a peripheral surface in the region of the gap, preferably screwed.
Further advantages can be achieved in that the rolling body receiving the gap portion is offset from the magnets and coils receiving gap portion in the axial direction.
By the rolling elements receiving gap portion of which the magnets and coils receiving gap portion is separated by an all-round seal, on the one hand the lubricant, which is located in the storage section and should ensure good lubrication of the rolling elements, where the magnets and coils in the radial direction facing each other, kept away, so that where lubrication is completely unnecessary, no braking torque is generated, but the two connection elements can move past each other without friction.
If several coils are interconnected to a common segment body, the assembly can be simplified insofar as not all coils must be individually bolted to the relevant connection element.
The interconnection of the coils can be done on the back of the coil-carrying portion of the respective connection element or in the region of an opening of the gap.
Furthermore, the contacting of the coils can be effected via bores in the supporting this section of the respective connection element or in the region of an opening of the gap.
Several coils should be connected in series to one or more strings. This has the advantage that all coils of a strand are traversed by a current of the same amplitude, thus causing exactly the same magnetization. Thus, the drive power is distributed evenly over all coils of a strand.
There may be provided three strands of coils, corresponding to a three-phase system. When driven with currents sinusoidal amplitude and respective electrical offset of two phases by 120 ° or 240 ° has a
Three-phase system has the advantage of a temporally completely constant power flow. This has a favorable effect in the context of the invention on the synchronous characteristics of such a driven roller bearing.
It is possible that per strand 10 coils or more are connected in series, for example, each 20 coils or more, preferably 30 coils or more, in particular 40 coils or more. The larger the number of coils, the better the synchronization. When driven at the same frequency, a more or even high-pole machine runs slower than a single-pole or low-pole machine, but can be controlled with a much higher degree of precision.
Preferably, the strands are connected at one end in a star or triangle. In the first case, the phase voltages correspond to the phase voltages of a feeding three-phase system, in the latter case the chained voltages. Since the chained voltages are higher than the phase voltages, the drive power can be varied in this way.
At their other end, the strands should be fed by a power converter, in particular by a three-phase inverter or a three-phase inverter. If the current and / or voltage values output by it are sinusoidal, the drive power can be controlled or regulated with maximum precision. On the other hand, a block operation is possible instead of sinusoidal current or voltage signals, the individual phase voltages are only switched on or off. Also, an intermediate stage is conceivable, wherein the phase voltages or currents are not given sinusoidal, but in one or more stages, for example, 0 volts, ± Vz Un, ± UN, or 0 volts, ± 1/3 UN, ± 2/3 UN , ± UN, etc., or a corresponding, stepped current control.
The invention can be further supplemented by a rotation angle sensor, for example in the form of an incremental encoder. This could scan, for example, along a peripheral surface of the drive device mounted incremental graduations to obtain information about the exact rotational angular position of the device concerned. Depending on the accuracy of the incremental graduation, the control can therefore be provided with a correspondingly high precision. It should be noted that in some applications, the precision of a position control is of great importance, while other parameters such as the dynamics or the developable torque on the other hand in the background, such as in machining equipment for the integration of a gearing in large sprockets, where Milling a tooth gap of the supported with a drive device according to the invention and driven machining table must be driven by exactly one tooth pitch so that after a complete revolution, the last tooth gap to the very first tooth gap exactly the same distance as all other tooth gaps with each other. If a drive device used in this case is provided with a braking device which brakes the machining table together with the workpiece fixed thereon during the actual milling process, no special torque is required to maintain high precision.
Preferred application brings the teaching of the invention when selbiger use on a ship, a vehicle or heavy vehicle and / or on or on a construction machine. In practice, for example, heavy-duty cranes or mobile cranes, bucket wheel excavators or harbor / ship cranes or loading hoists, or even tunneling machines, have emerged as particularly practical applications. In this case, at least one drive device is in use, for example, to set at least one drive unit, preferably a group of wheels and / or chains, in motion or to drive in rotation.
This application is advantageous, in particular, because in the ideal case, the hitherto necessary mechanical steering gear can be completely replaced by the invention.
The present invention can also be used to set in motion or rotate any type of large and / or heavy arrangements: these types of arrangements can be towers or carriages, but also excavator arms or lifting arms / lifting platform / Lifting platforms or even swiveling cabs of cranes, from which the crane operator observes and controls the work.
Likewise, by means of the invention, telescopic booms or ladder rotary platforms, in a particularly advantageous embodiment, can even drive drill heads of tunneling machines or tunnel boring machines. All these latter applications are common in that the respective rotatable or pivotable arrangement can be directly, for example, abutting surface or flange, create at least one of the connection elements of the invention and can be fastened by means of annularly distributed fastening means, preferably screw, to the drive device. As a rule, the axis of rotation of the respective drive device is then aligned with the center or rotation axis of the arrangement.
In a further advantageous embodiment of the invention selbige is suitable to be used as a pivot bearing in beverage bottle machines, in particular bottling and / or stretch blow molding machines for the production of PET plastic bottles. In this case, the drive device is firmly connected to a rotatable arrangement, in particular screwed, for example, which can accommodate or hold a variety of beverage bottles. The direct and immediate, i. Gearless, electronic controllability of the invention has the advantage of accurate positioning of the annular held or recorded bottles. It has proven to be particularly advantageous that in the context of this embodiment toothed ball slewing rings are used: rolling elements are balls, and at least one of the rings of the invention is toothed, in particular helical teeth.
In another embodiment of the invention selbige is suitable to act as electrically driven directly or directly driven cable or cable drum. In this case, the drive device is fixedly connected to a rotatable arrangement, in particular screwed, which is designed annular or cylindrical and is surrounded along a lateral surface of this annular or cylindrical shape of strand-like, but largely flexible, cable or cable material. Upon electrical actuation of the terminal box of the invention, the drive is set in rotating motion, and the cable or cable can thereby either, depending on the polarity of the drive, be unwound or rolled up.
Further features, details, advantages and effects on the basis of the invention will become apparent from the following description of a preferred embodiment of the invention and from the drawings. Hereby shows:
1 shows an inventive drive device in a plan view of an end face.
FIG. 2 is a section through FIG. 1 along the line II-II; FIG. schematically indicating on the left side of the drawing an attachment (8) mounted arrangement (A);
3 shows the detail III of Figure 2 in an enlarged view, but without built-drive device.
Fig. 4 is a perspective view of the sectional surface of Figure 3, after installation of the drive device, seen from an approximately tangential direction ..;
FIG. 5 shows approximately the same detail as FIG. 4, also in a perspective illustration, but seen from an approximately axial direction; FIG.
6 is a view on the inside of the outer connection element, partially broken away. such as
Fig. 7 is a circuit diagram for the electrical contacting of the individual coil segments.
Fig. 8a an application of the inventive device for driving a group of wheels, replacing a mechanical (s) steering gear.
Fig. 8b shows a second application of the inventive device for driving a rotatable assembly (A), this arrangement represents the upper part of a rotatable tower on a vehicle (ship).
Fig. 9a, a third application of the inventive device for driving a rotatable assembly (A), this arrangement represents the upper part of a rotatable tower on a large construction crane (port crane / construction machine).
9b shows a third possible application of the device according to the invention for driving a rotatable arrangement (A), this arrangement representing the upper part, pivotable or rotatable, of a large bucket wheel excavator (construction machine).
As can be seen Fig. 1, the inventive drive device 1 for rotatable coupling of two plant or machine parts od. Like. An annular structure and is rotationally symmetrical to a central axis 2 of this ring structure.
An essential part of the drive device 1 are two annular, substantially planar connection elements 3, 4th
Each of these connection elements 3, 4 has at least one respective planar connection surface 5, 6 together with fixing means 7, 8 distributed in a ring-shaped manner for connection to different equipment or machine parts or the like. These attachment means are preferably bores for Mounting of mounting screws, for example, with blind holes or through holes provided with an internal thread. Preferably, connection surfaces 5, 6 of the two connection elements 3, 4 are located on mutually opposite end faces of the drive device 1, that is, once, for example, in FIG. 3, once at the bottom.
Both connection elements 3, 4 are arranged concentrically to the common center 2, through which-perpendicular to the main plane of the connection elements 3, 4 - the axis of rotation 2 runs, around which the two connection elements can rotate against each other.
Furthermore, the two connection elements 3, 4 are arranged radially in one another; In the example shown, the connection element 3 is located radially inside the central recess of the other connection element 4.
Between two connection elements 3, 4 there is a gap-shaped intermediate space 9, which is subdivided essentially into two sections, namely into a bearing section 10 and into a drive section 11.
The width of the gap 9 is dimensioned such that in the drive section 11, the facing surfaces 12, 13 of both connection elements 3, 4 are further apart than in the bearing section 10, so that more space remains in the drive section 11 than in the Bearing 10, at least as long as there are no other parts added.
As can be seen Fig. 3, one or more rows of rolling elements 14,15,16 are arranged in the bearing portion 10, which roll between two raceways 17, 18 at the two connection elements 3, 4, so that the same against each other rotatable are.
In the example shown, there are several rows of rolling elements 14, 15 with a large pressure angle or support angle a of more than 45 °, for example 60 ° or more, preferably 75 ° or more, in particular about 90 °, and at least one row of rolling elements 16 with a small pressure angle or support angle α of less than 45 °, for example 30 ° or less, preferably 15 ° or less, in particular about 0 °. In this case, the pressure or support angle a between the radial or main plane and the line of the pressure acting on a rolling element is measured. The radial or main plane of the drive device 1 is penetrated vertically by the rotation axis 2.
In this case, the rolling elements 14, 15 take over with large pressure or support angle α parallel alignment of the main planes of the two annular connection elements 3, 4. In the example shown, there are two rows of such rolling elements 14 for the transmission of axial compressive forces between the pads 5, 6 at opposite end faces of the drive device 1, while a number of such rolling elements 15 of the transmission of axial compressive forces between these pads 5, 6 is used.
To achieve this, one of the two connection elements 3, 4 - in the example shown, the radially inner connection element 3 - a circular, radially to the other connection element 4, 3 projecting collar 19 of approximately rectangular cross-section on, - by the gap 9 spaced - is encompassed by the other connection element 4.
At the connection surface 5 of the collar 19 supporting connecting element 3, 4 is a raceway 17 for the row (s) of axial compressive forces transmitted rolling elements 14 are arranged in Fig. 3 at the top 20 of the collar 19, while at the opposite side of the collar 19 - in Fig. 3 on the underside 21 - a raceway for the row (s) of axial tensile forces transmitted rolling elements 15 is provided.
The rolling elements 16 with a small pressure or support angle a run along a track 17 on the end face 22 of the collar 19 along.
All these rows of rolling elements 14, 15,16 find their respective other track 18 on the inside of a collar 19 surrounding, all-round recess 23 of the other connecting element 4, third
The illustrated embodiment has roller-shaped rolling elements 14,15,16; however, this is not mandatory; other Wälzkörpergeometrien are conceivable, for example, spherical rolling elements 14, 15, 16. Of course, different rows of rolling elements 14, 15, 16 also have different Wälzkörpergeometrien.
The bearing portion 10 of the gap 6 is on both sides - ie beyond the innermost row of rolling elements 14 on the one hand and outside the outermost row of rolling elements 15 on the other hand - sealed by at least one per-round sealing element 24, 25 and can thereby with a lubricant - preferably with grease - Be filled, which is prevented by the sealing elements 24, 25 on the one hand escape and on the other hand, to get into the drive section 11.
In order to avoid problems in assembling the drive device 1, which is the federal government 19 encompassing recess 23 having connecting element 3, 4 in a plane parallel to Lagerhaupt- or radial plane in the region of the recess 23 divided into a pad 6 having ring 26 and a releasably fixed thereto ring 27. Preferably, this compound is arranged distributed by a wreath, parallel to the bearing axis of rotation 2 screws 28 which engage in aligned holes 29, 30 in these two rings 26, 27 and are screwed tight therein. Preferably, a number of holes 29 are designed as an internally threaded blind holes for this purpose, the other holes, however, as through holes.
In the illustrated embodiment, the pad 6 having the ring 26 has a larger cross section than the fixed thereto ring 27. This is mainly due to the lower height of the latter. However, one of the two rings 26, 27 - in the example shown, the connection surface 6 of the respective connection element 3, 4 opposite ring 27 - have a radial extension in the form of a round collar 31 on its side facing away from the gap 9 lateral surface 32. This collar 31 has approximately the shape of a brake disc and can be encompassed axially by brake shoes to brace the relevant connection element 3, 4.
A braking device may be particularly useful if - as the invention further provides - the inventive drive device 1 is part of a clamping device for a workpiece to be machined. The braking device may then be tightened during a machining step - that is, while a tool is engaged - while being released for rotational adjustment and adjustment.
For the rotatable positioning of large workpieces a rotary device 1 according to the invention can be installed in a rotatable rotary table, in particular in a horizontal orientation below the table surface and parallel to that. The table or platen would then be placed on top of the highest pad 6 and bolted while the brake is anchored to the foundation or chassis of the processing machine.
As can further be seen in FIG. 3, an approximately axial, ie vertical, line can be found in section through the drive device 1, which extends between the two connection surfaces 5, 6 and thereby passes through the pressure rolling elements 14. The rotating device 1 is thus designed to be maximally stiff with respect to axial compressive forces.
Furthermore, one of the two raceways 17, 18 is formed for the pressure rolling elements 14 by machining or shaping of a base body, wherein also the connection surface 5, 6 of the relevant connection element 3, 4 is incorporated or formed.
3 further shows, the collar 19 having the connecting element 3, 4 is divided into two rings 33, 34. One of these - in the embodiment of FIG. 3, the lower ring 33 - carries the pad. 5 of the relevant connection element 3, 4 and the collar 19, and substantially limits the bearing portion 10 of the gap 9, while the drive portion 11 of the gap 9 is mainly limited by the other ring 34, at least in the radial direction. Both rings 33, 34 are connected by means of several, distributed in a ring-shaped arranged fasteners firmly together. This connection can preferably be formed analogously to the connection between the two rings 26, 27, that is, by means of screws screwed into one another in aligned bores.
3, the drive section 11 of the bearing gap 9 has a greater width B than the bearing section 10, so that there find the drive devices still to be installed sufficient space. The width B of the drive section 11 may for example be of the order of a few centimeters, for example between 1 cm and 20 cm, preferably between 2 cm and 15 cm, in particular between 5 cm and 12 cm. The height of the drive section 11 flanking ring 34 corresponds approximately to the axial extent of the drive section 11 of the bearing gap 9. The resulting, axially parallel height extension H of the drive section 11 is preferably greater than its radial width. It may also be of the order of a few centimeters, for example between 2 cm and 40 cm, preferably between 5 cm and 30 cm, in particular between 10 cm and 25 cm.
Optionally, the two rings 33, 34 may be centered on one another, for example by the ring 33 forming the bearing portion 10 of the gap 9 having a groove 35 completely running around its circumference, wherein the adjacent area of the other ring 34 can be fitted exactly ,
The upper end face 36 of the drive section 11 of the gap 9 bounding ring 34 of a connecting element 3 terminates below the formed in the region of that end face 36 pad 6 of the other connection element 4, ie in the axial direction before or within the same.
The installation in the drive section 11 of the gap 9 is divided into two separate units: While at an edge 37 of this drive section 11 electric coils 38 are fixed, 39 magnets 40 are attached to the opposite edge.
In this case, a plurality of coils 39 are arranged one behind the other in the circumferential direction of the gap 9. In order to be able to feed these from an electrical three-phase system, that is, for example, with the three phases R, S, T, their number should be divisible by 3.
Since the diameter of the coil carrying the edge 37 of the drive portion 11 of the bearing gap 9 is preferably greater than 1 meter, preferably 2 meters or larger, in particular 3 meters or more, resulting in a circumference U of this edge 37 in the order of 3 meters or more, preferably 6 meters or more, in particular 9 meters or more.
On such a large circumferential length, it is not difficult to line up a larger number n of coils 38, for example 60 coils 38 or more, preferably 90 coils 38 or more, in particular 120 coils 38 or more.
Preferably elongated coils 38 are used, the axis-parallel height h is greater than their azimuthal extent a in the circumferential direction. If they are placed close to each other, the following requirement arises:
The axis-parallel height H of the flank 37 is greater than the circumference U, divided by the number n of the coils 38.
The cross section of the wire used for the coil winding should be chosen large enough to allow currents I in the range of 1000 A or above.
Preferably, in each case a plurality of coils 38 are connected in series, preferably to three strands R, S, T. In this case, each third coil 38 is assigned to a common strand R, S, T, the two intervening in each case the other two strands R, S, T. This interconnection can be done, for example, in each case in the region of the adjacent mouth of the gap 9.
In this way, a plurality of adjacent coils - for example, 12, 15 or 18 - interconnect to segments 41, which are shown in Fig. 7. Such segments 41 can then be integrated or removed together.
Preferably, one or more coils 38 are seated on a core or segment body 42, preferably of a soft magnetic material. The coils 38 may be wound separately therefrom and then slid onto the core body 42. These core bodies 42 are then fastened to the flank 37 of a connecting element 3, 4 provided in the region of the drive gap 11, preferably by means of a plurality of radial screws. To immovably hold the coils 38, they should be encompassed by the / the core or segment bodies 42 gap side. In order to achieve this, the radial extent of the core or segment body 42, which is related to the bearing axis of rotation 2, is greater than the relevant dimension of the coils 38, and these are formed in grooves and / or groove-shaped depressions on the surface of the core facing away from the gap 9. or segment body 42 used. In the case of core bodies 42 for holding individual coils 38, a groove running around the edge is sufficient for this purpose; Segment body 42 for a plurality of coils 38, however, should in any case have groove-shaped recesses in the inner region.
After fixing all core or segment body 42 together with the electric coils 38, these coil segments 43 are electrically connected to each other, in particular each three-phase, i. E. forming three strands R, S, T, as can be seen in FIG.
As can be seen from Fig. 4, should axial connecting holes 44 for receiving connecting bolts for the connection of the two rings 33, 34 with respect to the radial connecting holes 45 for receiving connecting screws for fastening the core or segment body 42 to the gap flank 37 offset in azimuthal direction against each other. To ensure a consistent, such offset, the number bi of the axial connection bores 44 and the number b2 of the radial connection bores 45 should be integer multiples or divisors of the number n of electric coils 38:
where Q is the set of rational numbers. Ideally, bi = b2 = n.
The terminals 46 to individual coil segments 43-or at least the first and last coil segment 43 of a strand - can over the free end face 36 of the drive section 37 delimiting gap region 9 away or through holes in the ring 34 through to the coil 38 opposite lateral surface 47 out of this ring 34 and connected there with each other or with a supply voltage.
Preferably, the strands R, S, T are connected at one end 48 in star or delta, while the other end is contactable with a supply voltage, for example in a terminal box 49. There, all strands 48, R, S, T be placed so that the choice between star and delta connection as well as the choice of the phase sequence or direction of rotation is left to the user.
The supply of the various strands R, S, T is preferably carried out via a power converter, inverter or inverter, in particular with approximately sinusoidally modeled output current and / or output voltage. A feeding converter, inverter or converter can be controlled by a speed controller. In order to approach a given position precisely, it is recommended to provide a position controller.
In order to make the supply of the supply lines to the coils 38 mechanically torsionally, it is recommended that the electric coils 38 carrying connection element 3, 4 to fix non-rotatably on a chassis or foundation. The power converter can also be placed at or near it.
In the following, therefore, the equipped with electric coils 38 connecting element 3, 4 will be referred to as a stator, and consequently the contrast rotatable connection element 4, 3 as a rotor. In the illustration according to FIG. 3, therefore, the radially inner connection element 3 is the stator and the outer element 4 surrounding the rotor.
For a control - speed or position control - can be arranged at an exposed point of the rotatable rotor connection element 3, 4, a rotary or position sensor.
The invention recommends, for detecting the rotation angle on the outer end face 50 of the collar 31 on the rotor connection element 3, 4 to arrange an incremental row, for example, stick, which can be scanned by an incremental encoder to detect the respective rotational position with high accuracy can.
For detecting the rotation angle, two scanning devices can be used, which are offset by approximately 90 ° relative to a period of the incremental row in the circumferential direction, so that the order of the incoming pulses on the direction of rotation of the rotor connection element 3, 4 are closed can.
If the drive device is required to perform well, a large amount of heat in the stator 3, 4 may result. In order to avoid overheating, including, for example, the insulation of the winding could suffer, a cooling of the stator 3, 4 may be provided. For this purpose, two lines 51, 52, in particular tubes, can be laid on the lateral surface 47 of the stator 3, 4 opposite the coils 38, in which case a coolant can circulate.
Such lines 51, 52 can already take care of themselves by their thermal contact with the respective lateral surface 47 for cooling. In order to intensify the cooling effect, it can also be provided that within the connecting element 3, 4, that is within the coils 38 bearing ring 34, cooling holes are provided which connect two cooling lines 51,52 at regular circumferential intervals, so that the coolant is guided not only on the stator 3, 4, but downright through this.
The magnets 40, which are fixed to the flanks 39 of the drive section 11 opposite the coils 38, can be seen in FIG.
The magnets 40 can be initially connected to each other in segments to prepare and simplify the assembly, so that not all magnets 40 must be individually attached to the flank 39.
For segmental connection of a plurality of magnets 40, these are first on comparatively thin, flat carrier bodies 53, preferably sheets, attached, in particular glued. Preferably, the carrier body 53 made of soft iron.
These support bodies 53 together with the magnets 40 fastened or glued thereto are then fixed to the flank 39 in the region of the drive section 11 of the rotor connection element 3, 4, in particular screwed on, preferably by means of radial screws.
The magnets 40 are permanent magnets, preferably hard magnetic, preferably with a particularly high pole thickness. Due to their high pole strength, magnets with lanthanoid components have proven to be particularly useful, such as samarium-cobalt or neodymium magnets or magnets made of NdFeB, an alloy of neodymium, iron and boron. If the requirements are limited to the achievable nominal torque and / or Due to the size and number of poles of the machine, the nominal torque is not critical, however, should also be sufficient ferrite magnets.
The magnets 40 are relatively small and have a platelet or cuboid shape. They are glued in large numbers on the relevant support body 53.
Since the dimensions of such a magnet 40 are smaller than the axial extent of the coils 38, a plurality of magnets 40 are stacked one above the other mostly in the axial direction, each having the same polarity direction, ie each with a gap 9 facing north magnetic pole, or with each pointing to the gap 9 magnetic south pole.
In the azimuthal direction or in the circumferential direction along the gap 9 adjacent magnets 40 preferably have different polarity directions, ie, in addition to a magnet 40 or an axial row of magnets with each of the gap 9 facing north magnetic pole is a magnet 40 or an axial magnet row each with the gap 9 facing, magnetic south pole. Furthermore, the invention recommends not to align the axial rows of the same direction polarized magnet 40 exactly parallel to the axial direction, but slightly beveled, or in a slightly angled shape with an opening angle of slightly less than 180 °, ie for example with an opening angle of 175 ° or less, preferably with an opening angle of 170 ° or less. By such a slight inclination, the expression of magnetic poles in the circumferential direction is easily "sanded", whereby the synchronization of the electrically driven drive device 1 improves.
List of Reference Numerals: [0104] 1 Drive device 2 Rotation axis 3 Connection element 4 Connection element 5 Connection surface 6 Connection surface 7 Attachment means 8 Attachment means 9 Slit 10 Supporting section 11 Drive section 12 Surface (in FIG. 3) 13 Surface (in FIG. 3) 14 Rolling elements 15 Rolling elements 16 Rolling elements 17 Race 18 raceway 19 collar (in FIG. 3) 20 upper side 21 underside 23 recess 24 sealing element 25 sealing element 26 ring 27 ring 28 screw 29 bore 30 bore 31 collar 32 lateral surface 33 ring 34 ring 35 groove 36 end face 37 flank 38 electric coil 39 flank 40 Permanent magnet 41 Segment 42 Core body 43 Coil segment 44 Connecting bore 45 Connecting bore 46 Connections

权利要求:
Claims (24)
[1]
47 lateral surface 48 end 49 terminal boxes 50 end face 51 line 52 line 53 support body A arrangement (rotatable) Patent claims
A drive device (1), whereby a first part of a plant or a machine can be rotatably coupled to a second part or a foundation or a pedestal or a chassis of the installation or the machine about a rotation axis (2), comprising two annular connection elements (3 , 4) with at least one respective flat connection surface (5, 6) and distributed along a circle arranged fastening means (7, 8) for connection to the one annular connection element (3, 4) to the first part of the plant or machine on the one hand and to Connection of the other annular connection element (4, 3) with the second part or the foundation or the base or the chassis of the plant or the machine on the other hand, wherein the two connection elements (3, 4) are arranged concentrically to each other and radially into one another with a gap-shaped gap (9) between the two connection elements (3, 4), wherein in the gap-shaped intermediate space (9) one or more Rei hen of rolling elements (14, 15, 16) are arranged, which in each case between two raceways (17, 18) on the two connection elements (3, 4) roll, so that the connection elements (3, 4) against each other are rotatable, wherein at least one Connecting surface (5, 6) and at least one raceway (17, 18) are formed by original shaping or subsequent processing of a common base body, characterized in that within the gap-shaped intermediate space (9) on a connecting element (3, 4) at least one along of the respective connection element (3, 4) is arranged around the axis of rotation extending series of magnets (40), and this immediately opposite to the other connection element (4, 3) at least one completely extending row of coils (38).
[2]
2. Drive device (1) according to claim 1, characterized in that the gap (9) opens at two different end faces of the drive device (1).
[3]
3. Drive device (1) according to claim 1 or 2, characterized in that the connection surfaces (5,6) of the two connection elements (3, 4) are located on opposite end faces of the drive device (1).
[4]
4. Drive device (1) according to one of claims 1 to 3, characterized in that two connection elements (3, 4) via at least one intermediate rolling bearing row (14) in the axial direction are supported directly on each other, wherein at both connecting elements (3, 4) the respective raceway (17, 18) is formed together with the relevant, planar connecting surface (5, 6) each from a common base body.
[5]
5. Drive device (1) according to one of the preceding claims, characterized in that at least one connecting element (3,4), an annular collar (31) is provided, which is adapted to be clamped by two brake shoes in a preferably axial direction.
[6]
6. Drive device (1) according to one of the preceding claims, characterized in that a plurality of magnets (40) are interconnected to a common segment body, for example by a common carrier body (53).
[7]
7. Drive device (1) according to one of the preceding claims, characterized in that the magnets (40) are arranged such that in the circumferential direction of the gap (9) alternating north and south magnetic poles each other.
[8]
8. Drive device (1) according to one of the preceding claims, characterized in that the magnets (40) are arranged in a plurality of rows, such that the orientations of the magnetic polarities of the magnets (40) within a row are all aligned parallel to each other.
[9]
9. Drive device (1) according to claim 8, characterized in that the rows of magnets (40) extend with the same magnetic orientation obliquely to the axis of rotation (2) of the drive device (1).
[10]
10. Drive device (1) according to one of the preceding claims, characterized in that the coils (38) are fastened to core bodies (42), which in turn are fixed to a peripheral surface (37) in the region of the gap (9), preferably screwed.
[11]
11. Drive device (1) according to one of the preceding claims, characterized in that the rolling elements (13, 15, 16) receiving gap portion (10) relative to the magnets (40) and coils (38) receiving the gap portion (11) in the axial Direction, ie in the direction of the axis of rotation (2), is offset.
[12]
12. Drive device (1) according to one of the preceding claims, characterized in that the rolling elements (14, 15, 16) receiving the gap portion (10) of the magnets (40) and coils (38) receiving gap portion (11) by a round running seal (24) is separated.
[13]
13. Drive device (1) according to one of the preceding claims, characterized in that a plurality of coils (38) are combined with each other to form a common segment, in particular by mounting on a common segment body (42).
[14]
14. Drive device (1) according to one of the preceding claims, characterized by an interconnection of adjacent coils (38) or coil segments (43) on the rear side (47) of the coil (38) carrying portion (34) of the respective connection element (3, 4th ) or in the region of an opening of the gap (9).
[15]
15. Drive device (1) according to one of the preceding claims, characterized in that the contacting of the coils (38) via holes in which this carrying portion (34) of the respective connection element (3, 4) or in the region of an orifice of the gap ( 9).
[16]
16. Drive device (1) according to one of the preceding claims, characterized in that a plurality of coils (38) are connected in series.
[17]
17. Drive device (1) according to one of the preceding claims, characterized in that three strands (R, S, T) of coils (38) are provided, corresponding to a three-phase system.
[18]
18. Drive device (1) according to one of the preceding claims, characterized in that per strand (R, S, T) at least ten coils (38) are connected in series, for example, at least twenty coils (38), preferably at least thirty coils ( 38), in particular at least forty coils (38).
[19]
19. Drive device (1) according to one of the preceding claims, characterized in that the strands (R, S, T) are connected at one end (48) in a star or delta.
[20]
20. Drive device (1) according to one of the preceding claims, characterized in that the strands (R, S, T) are fed on the input side of a power converter, in particular of a three-phase inverter or a three-phase inverter.
[21]
21. Drive device (1) according to one of the preceding claims, characterized by a rotation angle sensor in the drive device (1), for example in the form of an incremental encoder.
[22]
22. Use of a drive device (1) according to one of the preceding claims for driving a group of wheels and / or chains in a ship, or in a vehicle or heavy vehicle and / or in a construction machine, such as a heavy crane or mobile crane or bucket wheel or harbor ship crane or in a tunneling machine or hoist or special hoist.
[23]
23. Use of a drive device (1) according to claim 22 for driving a group of wheels and / or chains of a preferably horizontal or vertical, rotatable or pivotable arrangement (A), in particular designed as an antenna tower or as a carriage or as an excavator or a lifting arm or a lifting platform / platform, or as a guide pulley or as a telescopic boom or as a turning platform, ideally even as a boring head of a tunneling machine, comprising at least one drive device (1) according to one of claims 1 to 21, wherein the drive device (1) which can set at least one arrangement (A) in motion or driving in rotation.
[24]
24. Use of a drive device (1) according to claim 23, characterized in that the at least one pivotable arrangement (A) directly, for example, abutting surface or flange, on at least one connection element (3, 4), create and distributed by means of a ring-shaped arranged fasteners (7, 8), preferably screw connections, can be fastened, with the axis of rotation (2) of the drive device (1) and the axis of rotation of the arrangement (A) being superposed or, ideally, being aligned on a common axis.

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BR112015015725A2|2017-07-11|

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WO2014101910A2|2014-07-03|

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JP2016503282A|2016-02-01|

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US20150364968A1|2015-12-17|

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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DE201210025600|DE102012025600A1|2012-12-31|2012-12-31|Device for the rotatable coupling of two plant or machine parts|

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PCT/DE2013/000448|WO2014101910A2|2012-12-31|2013-08-07|Drive mechanism for rotatably coupling a system part or a machine part|

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