Abstract:
The device comprises a) a rotor which can rotate or rotates about a rotational axis and b) at least one magnetic suspension bearing, in which the rotor can be or is mounted in a contactless manner and which comprises at least one super-conductive structure in addition to several permanent magnets, and c) a cooling device comprising at least one refrigeration head for cooling the super-conductive structure of the or each magnetic suspension bearing, whereby d) the rotor and each magnetic suspension bearing are arranged in a common gas chamber, which is surrounded by a gas-proof wall. The advantage of the device is that ice is prevented from forming on the magnetic suspension bearing.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application is based on and hereby claims priority to PCT Application No. PCT/DE01/03655 filed on 21 Sep. 2001 and German Application No. 100 49 821.3 filed on 9 Oct. 2000, the contents of which are hereby incorporated by reference. 
    
    
     BACKGROUND OF THE INVENTION 
     The invention relates to a device having at least one rotor which rotates or can rotate about a rotation axis, and having at least one magnetic bearing in which the rotor is borne or can be borne in a contactless manner. 
     U.S. Pat. No. 5,482,919 A discloses a device which has a rotor which can rotate about a rotation axis and has at least one superconducting winding (field coil) for an electric motor, and has a cryogenic cooler for cooling the superconducting winding. The superconducting winding may be formed from a known, metallic superconductor material (low-temperature superconductor) with a low critical temperature of T c , below 35 K, such as a niobium-tin alloy or a ceramic metal-oxide superconductor material (high-temperature superconductor) with a high critical temperature T c  above 35 K, such as bismuth strontium calcium copper oxide, an yttrium barium copper oxide or a mercury or thallium compound. The cryogenic cooler makes use of rapid expansion of a working fluid (which is compressed by a compressor) such as helium, neon, nitrogen, hydrogen or oxygen for cooling in thermodynamic cycles (processes) such as a Gifford-McMahon cycle, a Stirling cycle or a pulse tube cycle. The superconducting winding is thermally conductively connected to a cold head, which rotates with the rotor, of the cryogenic cooler via two or more annular supporting elements composed of a material with a high thermal conductivity coefficient, and which are connected via heat pipes or thermally conductive rods. In this way, heat is dissipated from the superconducting winding by thermal conduction through a solid body to the cold head. There is no need for a liquid coolant such as liquid helium or liquid nitrogen in this known cooling system, so that there is also no influence on the rotation of the rotor from a cold liquid. The compressor of the cryogenic cooler can rotate with the rotor or may be in a fixed position with respect to the rotor, and may be connected to the cold head via a rotating coupling. U.S. Pat. No. 5,482,919 A states nothing more with regard to the bearing of the rotor. 
     Magnetic bearings are generally known for bearings for rotors, and allow the rotors to be borne in a contactless bearing, which is thus free of wear. Both active magnetic bearings with electromagnets and position control as well as passive magnetic bearings with automatic position stabilization are known. 
     DE 44 36 831 C2 discloses a passive magnetic bearing for bearing a rotor shaft with respect to a stator, which has a first bearing part which is connected to the rotor shaft, and a second bearing part which is arranged on the stator and surrounds the first bearing part. One of the two bearing parts has a high-temperature superconductor. The other bearing part has an arrangement of permanent-magnet elements arranged alongside one another and composed of a neodymium (Nd), Iron (Fe) boron (B) alloy or of a samarium (Sm) cobalt (Co) alloy. Adjacent permanent-magnet elements are magnetized with opposite polarity to one another. When a position change occurs, the permanent-magnet elements induce shielding currents in the superconductor, as a result of field changes. The resultant forces may be repulsive or attractive, but are always directed such that they counteract the deflection from the nominal position. In contrast to known active magnetic bearings, an inherently stable bearing can be achieved in this case, and there is no need for a complex control system that is subject to defects. The intermediate spaces between in each case two permanent-magnet elements are filled with ferromagnetic material in order to concentrate the magnetic flux, which emerges from the permanent-magnet elements, on the side facing the other bearing part. This results in a high level of bearing stiffness (stability, robustness). The permanent-magnet elements together with the ferromagnetic intermediate elements may be arranged axially with respect to the rotor shaft axis one behind the other in the form of thin rings, or else may be axially elongated and arranged one behind the other in the circumferential direction. 
     In a refinement of this known magnetic bearing, the permanent magnets are provided in a hollow-cylindrical arrangement on the inner bearing part, and the superconductor is arranged as a hollow-cylindrical structure on the inside of a hollow-cylindrical supporting body for the outer bearing part. Cooling channels are formed in the supporting body for passing liquid nitrogen through in order to cool the superconductor. 
     In another refinement according to DE 44 36 831 C2, the high-temperature superconductor on the inner bearing part is arranged on the rotor shaft, with a coolant channel being provided for the liquid nitrogen in the rotor shaft, in order to cool the high-temperature superconductor. This embodiment with a cold rotor body is proposed as part of a generator or of a motor with a cryogenic normally conductive or superconducting winding. 
     The document U.S. Pat. No. 5,214,981 A discloses a device for storing energy. This device has a rotating flywheel which has permanent magnets (which interact with stationary electromagnets) on its circumference for power transmission. The flywheel is borne in each case one magnetic bearing on opposite sides via two rotor shafts. In one embodiment (FIG.  1 ), one or more permanent magnets are provided in a cylindrical arrangement at each of the ends of the two rotor shafts. These ends project as first bearing parts into in each case one superconductor, in the form of a pot, as the second bearing part for the respective magnetic bearing. For cooling, the superconductors are each arranged in a cold bath of liquid nitrogen. In another embodiment (FIG.  3 ), each rotor shaft has a recess as the first magnetic bearing part on its end face facing away from the flywheel, with this recess being clad with a superconductor. The superconductor is cooled exclusively by the thermal radiation from the superconductor to the vacuum vessel, which is kept in a liquid bath filled with liquid nitrogen. Furthermore, the magnetic bearings have cylindrical second bearing parts, whose ends project into the recesses in the rotor shafts and have one or more permanent magnets in a cylindrical arrangement. The flywheel is enclosed together with the two magnetic bearings in a vacuum vessel which is evacuated to a pressure of less than 10 −4  Torr, in order to avoid friction of the rotating parts and the energy losses associated with such friction. The bearing gaps of the two magnetic bearings form continuous connections between the adjacent evacuated areas of the vacuum vessel. 
     JP 04370417 A and the associated abstract from Patent Abstracts of Japan disclose a further device for storing energy by a flywheel which is borne in two magnetic bearings and is arranged together with the magnetic bearings in a common evacuated vacuum chamber. Each magnetic bearing has a central permanent-magnet ring on the flywheel and two superconductor rings at an axial distance from it, which are arranged on stationary supporting disks, through which liquid coolant flows. 
     Finally, DE 197 10 501 A1 discloses an electrical machine having a stator with a polyphase winding for producing a rotating magnetic field, and with a rotor which rotates with the rotating field. The stator has a magnetic return path yoke, which forms a housing for the rotor. The rotor has a shaft which is passed through an opening, which is not sealed, in the housing and magnetic return path yoke. The rotor is composed entirely, or at least on its outside, of a high-temperature superconductor. Magnetic bearings for contactless bearing of the rotor are formed by the superconductor and by annular permanent magnets which are provided at two points. In order to cool the superconductor on the rotor, the entire machine is designed to have a small physical size and is operated completely in a cryogenic bath formed from liquid nitrogen. 
     Owing to the contactless bearing, the known magnetic bearings always have a continuous bearing gap, and gas and vapor can thus pass through them between the two sides which are connected by the bearing gap. Environmental air and moisture contained in it can thus enter the bearing gap, or can reach the rotor through the bearing gap. This results in the risk of the air humidity freezing on the cold components of the magnetic bearing or else of the rotor, if this is cooled, with such icing resulting in a restriction to operation, or even in damage to the magnetic bearing. Furthermore, the cooling processes with liquid coolant (cryogenic medium), in general liquid nitrogen, which are used exclusively for the superconductors of the described magnetic bearing according to the related art, are generally also subject to sealing problems in the region of the sensitive magnetic bearings, in addition to the problem of any moisture that has entered freezing on the cryogenic medium supply lines that are required, once again increasing the risk of icing or of other malfunctions of the magnetic bearing. 
     SUMMARY OF THE INVENTION 
     One aspect of the invention is based on the object of protecting the magnetic bearing or magnetic bearings for bearing of a rotor against such adverse effects on operation or damage. 
     The device accordingly has a rotor which rotates or can rotate about a rotation axis and at least one magnetic bearing, in which the rotor is borne or can be borne in a contactless manner (or without wear), and which has at least one superconductor (or: a superconducting structure). 
     The rotor is arranged together with the associated magnetic bearing or bearings in a common gas area (or gas-filled chamber), which is surrounded by a gastight wall. The rotor and magnetic bearings are thus, in other words, located in the same gas atmosphere, which is separated and shielded from the environmental air by the wall through which gas cannot pass. These measures result in the bearing gap of each magnetic bearing being filled with the gas with which the gas area is filled, and being protected by the gas area wall against the ingress of environmental moisture. Furthermore, pressure fluctuations, for example as a result of gas losses, can be tolerated within certain limits, since they affect all the components in the gas area in the same way. 
     As a further measure, a cooling device having at least one cold head, which is thermally coupled to the superconductor and dissipates heat from the superconductor mainly by thermal conduction as the heat transfer mechanism, is now provided for cooling the superconductor of the magnetic bearing or of each magnetic bearing. The use, as proposed, of a cold head (which in principle is known per se) for indirect cooling of the magnetic bearing is a considerably simpler solution in terms of design and handling than the direct cooling, as provided in the related art, via a liquid cooling medium. A cold head can easily be fitted to the magnetic bearing as a connecting piece for heat transmission. Furthermore, the use of one or more cold heads ensures deliberate cooling of the superconductor in the magnetic bearing and avoids the problems of the emergence (which can never entirely be avoided) of cryogenic liquid and the uncontrolled thermal conditions that result from this, with the risk of icing of the magnetic bearings as a result of freezing of residual moisture in the gas atmosphere or of moisture contained in the evaporated cryogenic medium. 
     The cooling device for cooling the cold head and hence for indirect cooling of the magnetic bearing or bearings preferably has a cryogenic cooler system which is operated in particular electrically and does not require the handling of cryogenic liquid gases in conjunction with the cold head. Different cold heads may in each case be connected to a dedicated cryogenic coolant, or else in any desired combinations to shared cryogenic coolers. Each cold head is preferably guided from the outside in a direction running essentially at right angles to the rotation axis to the superconducting structure of the magnetic bearing. 
     The magnetic bearing or bearings of the device generally has or have at least one inner bearing part and at least one outer bearing part, with the outer bearing part surrounding the inner bearing part and with a bearing gap, which runs around the rotation axis, being formed between the two bearing parts, and one of the two bearing parts is connected or can be connected to the rotor, in particular to its rotor shaft. 
     One of the two bearing parts of the magnetic bearing now preferably has at least one permanent magnet, while the other bearing part has the superconducting structure, which interact electromagnetically (by induction) with the permanent magnet or permanent magnets such that the bearing gap between the inner bearing part and the outer bearing part is formed or maintained. Where there are two or more permanent magnets, these are generally arranged alongside one another, in particular axially one behind the other with respect to the rotation axis and preferably in each case surround the rotation axis in a shape that is closed all round, in particular in the form of a ring, or else alongside one another in an arrangement which surrounds the rotation axis. The permanent magnet or magnets in one advantageous refinement surrounds or surround the rotation axis in a closed (all round) form, preferably in the form of a ring. The ring cross section may in this case in particular be circular, in the form of a disk or rectangular, corresponding to a hollow-cylindrical or toroidal ring shape. The ring longitudinal section at right angles to the rotation axis may thus, in particular, be in the form of a circular ring. Immediately adjacent permanent magnets are preferably magnetized with essentially opposite polarity to one another, at least on average, over domains which may be present. 
     One advantageous development of the magnetic bearing is characterized in that a flux concentrating element is in each case arranged between at least two of the permanent magnets, and/or a flux concentrating element is in each case arranged on the outside of the outer permanent magnets in the axial direction. Each flux concentrating element is used for conducting the magnetic flux of the permanent magnets and, in general, also for concentrating and amplifying it in the bearing gap and, for this purpose, is at least partially composed of a magnetically permeable material, in particular of a ferromagnetic material, for example iron (Fe). 
     The superconducting structure preferably surrounds the rotating axis in a closed form, in particular in the form of a ring, and/or essentially has a cylindrical shape, at least on the side facing the bearing gap. Furthermore, it is advantageous for the superconducting structure to be arranged on the side of the bearing part facing the bearing gap, in order to achieve good coupling efficiency. 
     In general, at least one cold head is in each case provided for each magnetic bearing, for cooling the superconducting structures and, expediently, the permanent magnets as well, in order to achieve a highercoercivity field strength. 
     The bearing gap of at least one of the contactless magnetic bearings is now preferably connected to the gas area and allows gas to be exchanged. In consequence, the bearing gap is located in the same gas atmosphere as that found in the gas area. 
     In general, the wall of the gas area is in a fixed position with respect to the rotor, that is to say its position relative to the rotation axis of the rotor remains unchanged during rotation of the rotor. 
     The rotor is preferably borne in the magnetic bearing via a rotor shaft which is connected or can be connected to the rotor. The rotor shaft is preferably passed to the outside through an opening, which is sealed by a rotation seal, in the wall of the gas area. 
     In one particularly advantageous embodiment of the device, the rotor is borne in at least two magnetic bearings, preferably via in each case one rotor shaft, which magnetic bearings are arranged on axially opposite sides of the rotor with respect to the rotation axis. The rotor is thus held in bearings on both sides and thus in a particularly robust manner. 
     One advantageous development of the rotor is characterized by at least one winding (coil) which generally runs around the rotation axis and is preferably formed by a superconductor. 
     Any low-temperature superconductors or high-temperature superconductors may be used as superconductors for the magnetic bearings and/or for the winding on the rotor. The superconductor may be a traditional low-temperature superconductor with a critical temperature up to 35 K, for example a metallic alloy such as a niobium tin alloy, or preferably a high-temperature superconductor with a critical temperature above 35 K, preferably above 77 K (i.e. the boiling point of nitrogen), preferably a metal-oxide or ceramic high-temperature superconductor such as bismuth strontium calcium copper oxide, yttrium barium copper oxide or a compound of mercury or thallium. The higher the critical temperature of the superconductor, the less energy is required for cooling. 
     Since high-temperature superconductors are, in particular, self-supporting only to a restricted extent, one advantageous development allows the superconducting structure of the magnetic bearing or the superconducting winding of the rotor to be arranged on or in a support or winding support. In order to cool the superconductor, the support or winding support preferably has a high thermal conductivity, for example being formed from metal. 
     In one particularly advantageous embodiment, the winding support of the rotor has a cavity (internal area) which extends axially with respect to the rotation axis. The winding can now advantageously be cooled in a space-saving manner via this cavity, in that a heat transmission unit in the cavity or on the cavity is thermally coupled to the winding support, preferably via a contact gas in the cavity. 
     The heat transmission unit is now preferably thermally coupled or can be thermally coupled to a cooling device for the rotor. This cooling device may be designed in a manner known per se, for example according to the initially cited U.S. Pat. No. 5,482,919 A, whose entire disclosure content is also included in the present application. The cooling device and/or heat transmission unit for the rotor may also operate with a liquid coolant such as liquid helium or liquid nitrogen, or else may have a cryogenic cooler system with at least one cold head, in the same way as the cooling system for the magnetic bearing. 
     According to one particular embodiment, the heat transmission unit has a preferably cylindrical heat transmission body which projects into the cavity in the winding support and between which and the winding support an intermediate gap is formed, which runs around the rotation axis and is filled with a contact gas. The heat transmission from the or cooling of the winding now takes place essentially by thermal conduction through the solid body and via the contact gas. 
     However, alternatively or additionally, cyclic vaporization and condensation of a heat transport gas, with appropriately chosen vaporization enthalpy, can also be used as the heat transport mechanism. The heat transmission unit may then, in particular, comprise a heat pipe. 
     In an embodiment which makes use of both the thermal transport mechanisms of thermal conduction and vaporization, the cavity in the winding support is at least partially filled with the heat transport gas, so that the heat transport gas is also used as the thermally conductive contact gas. 
     The cavity in the winding support and the intermediate gap between the heat transport body and the winding support can also be connected to the gas area in a manner which allows gas to be exchanged. This then results in a standard gas atmosphere inside and outside the rotor, and there is no longer any need to take any special measures in order to seal these gas areas. 
     The contactless arrangement of the heat transmission unit in the winding support is particularly advantageous when the two components are intended to be mechanically decoupled from one another, that is to say the heat transmission unit is intended to be fixed during rotation of the rotor. Such a fixed configuration of the heat transmission unit, which does not rotate with the rotor, and possibly of the connected cold head is expedient since there is no need to seal any rotating parts of the cooling system with respect to one another. 
     In one special physical development, at least one rotor shaft, which is borne in the associated magnetic bearing, is in the form of a hollow shaft. The hollow shaft can now at least partially accommodate the heat transmission unit and/or a connection between the gas area and an internal area of the rotor, in particular the cavity in the winding support 
     In order to protect the winding, it is preferably arranged in an internal area of a container in the rotor, which is preferably evacuated and is sealed from the rest of the gas area and from the cavity in the winding support. 
     The gas area of the device, in which the rotor and the magnetic bearing are arranged, is generally filled with a gas or a gas mixture which is used for thermal conduction for cooling of those components which need to be cooled and for this purpose makes contact with them and is therefore also referred to as the contact gas. This gas generally remains in the gas area throughout the operating life of the device. The contact gas is therefore in one advantageous embodiment an inert gas or a mixture of inert gases, with helium or neon being preferable, although nitrogen can be used for correspondingly high operating temperatures. Furthermore, in principle, hydrogen or oxygen are also suitable, although their handling is somewhat more problematic. 
     The gas with which the gas area is filled preferably contains virtually no water, or contains less than a critical amount of water, so that it is impossible for water to freeze on cold parts in the gas area. For this purpose, the gas is prepared with an appropriate purity, and/or is dried. 
     The gas pressure of the gas in the gas area in one advantageous embodiment is preferably at least as high as, and preferably higher than, the gas pressure in the outer area surrounding the wall of the gas area, in general atmospheric pressure. Even in the event of sealing problems or leakages in the area of the gas area wall, this reliably prevents the ingress of moist air and the possibility of ice being formed in consequence in the cold area. 
     The device is preferably used for electrical machines such as motors and generators. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     These and other objects and advantages of the present invention will become more apparent and more readily appreciated from the following description of the preferred embodiments, taken in conjunction with the accompanying drawings of which: 
     FIG. 1 shows a device having a rotor, which is borne in two magnetic bearings, in a longitudinal section on a plane containing the rotation axis of the rotor, 
     FIG. 2 shows an embodiment of a magnetic bearing of the device, in a perspective and partially sectioned view, 
     FIG. 3 shows another embodiment of a magnetic bearing of the device, in a longitudinal section, 
     FIG. 4 shows a further embodiment of a magnetic bearing of the device, in a cross section in a plane at right angles to the rotation axis, and 
     FIG. 5 shows a device having a rotor, which is borne in two magnetic bearings, and having a heat pipe, in a longitudinal section, in each case illustrated schematically. Mutually corresponding parts are provided with the same reference symbols in FIGS. 1 to  5 . 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to like elements throughout. 
     FIG. 1 shows a device having a rotor  20  which is borne such that it can rotate in magnetic bearings  2  and  3  positioned respectively on both sides (end faces) axially with respect to its rotation axis A. For this purpose, a first rotor shaft, which is in the form of a hollow shaft (neck tube)  34 , is formed or mounted on the rotor  20  on the left-hand side in FIG. 1, and is borne in a contactless manner in the magnetic bearing  2 . In the illustrated embodiment, the hollow shaft  34  also has a length compensator  36 , in particular an expanding bellows, for length compensation. A second rotor shaft  4  (which is, for example, solid), is formed or mounted on the rotor  20  on the opposite side, on the right in FIG. 1, and is borne in a contactless manner in the magnetic bearing  3 . Both shafts, the hollow shaft  34  and the rotor shaft  4 , are preferably rotationally symmetrical with respect to the rotation axis A, in particular being hollow-cylindrical or cylindrical, or else at least slightly conical. 
     Each of the magnetic bearings  2  and  3 , which are preferably essentially the same, has a bearing inner part  5 , which is connected to the associated hollow shaft  34  or rotor shaft  4 , and a bearing outer part  11 , which surrounds the bearing inner part  5  forming a bearing gap  10 . The bearing inner part  5  has two or more permanent magnets, which are not annotated in any more detail in FIG. 1, on its outside facing the bearing gap  10 . Opposite the permanent magnets, the bearing outer part  11  has a superconducting structure  12  on its inside facing the bearing gap  10 , and this is supported on the outside on a supporting body  13 . The superconducting structure  12  makes contact with a respective cold head  22  or  23 , which projects through the supporting body  13  from the outside, for cooling. The design of the magnetic bearings  2  and  3  will be described with reference to the detailed FIGS. 2 to  4 . First of all, the further parts of the device shown in FIG. 1 will now be described in more detail. 
     The rotor  20  has at least one winding (coil)  25 , which is composed of a superconducting material and has one or more turns which run around the rotation axis A, preferably with essentially the same radius. The winding  25  is supported on or in a winding support  26 , which surrounds the rotation axis A in the form of a hollow body, preferably with a hollow-cylindrical shape. The winding support  26  is composed of a thermally highly conductive material such as a metal. 
     A central cavity  30 , through which the rotation axis A runs, is formed in the interior of the winding support  26 . On the side pointing toward the rotor shaft  4 , the cavity  30  is closed by the winding support  26 , while it is open on the side pointing toward the hollow shaft  34 . On this side, a cylindrical heat transmission body  35  projects through the opening in the winding support  26  into the cavity  30 , and extends to a point shortly before its end on the opposite side. The heat transmission body  35  is composed of a thermally highly conductive material, for example of a metal such as aluminum or copper, or, in order to avoid Eddy currents, alternatively of a dielectric, thermally conductive material such as a ceramic, for example aluminum oxide (Al 2 O 3 ) or aluminum nitride (AlN), or of monocrystalline sapphire. 
     An intermediate space  39  is formed all round between the heat transmission body  35  and the inner surface of the winding support  26 . Adjacent to the winding support  26 , the heat transmission body  35  is passed outward through a central cavity in the suspension element  48  located on this side, into the cavity of the hollow shaft  34 , in each case forming an intermediate space  38  or  37 . The intermediate spaces (gaps)  37  to the hollow shaft  34 ,  38  to the suspension element  48  and  39  to the winding support  26  mean that the heat transmission body  35  can be arranged in a fixed position overall with respect to these rotating parts and the respective rotor  20 , that is to say not rotating with them. 
     A contact gas is introduced at least into the intermediate space  39  between the heat transmission body  35  and the winding support  26 , and provides thermal coupling between the winding support  26  and the heat transmission body  35 . The intermediate spaces  39 ,  38  and  37  are preferably connected to one another, as shown, so that the contact gas is located in all the intermediate spaces  37  to  39 . Helium or neon is preferably provided as the contact gas. 
     At its end facing away from the end that is located in the cavity  30  in the winding support  26 , the heat transmission body  35  is thermally coupled to one end of a cold head  24 , which extends into the hollow shaft  34  from the opposite side, axially with respect to the rotation axis A. The heat transmission body  35  is cooled via the cold head  24 , which is connected to a cooling device which is not illustrated in any further detail, in particular to a cryogenic cooler that is known per se. In consequence, the winding support  26  is also cooled indirectly by thermal conduction via the contact gas and, finally, the superconducting winding  25 , which actually needs to be cooled, is cooled by the good thermal conduction capability of the winding support  26 . This therefore provides cooling for a rotating part, the winding  25 , via a stationary part, the heat transmission body  35 . 
     The winding support  26  together with the winding  25  is arranged in the internal area of a container  21  and is suspended on both end faces on the wall of the container  21 , via in each case one suspension element  48  with a metal sleeve and a hollow core composed of thermally insulating material. On the outside (outer surface), the winding support  26  is at a distance from the wall of the container  21 . The intermediate space which is formed in the internal area of the container  21  between the winding support  26  and the container wall is preferably evacuated to a desired residual pressure, in order to ensure that the winding support  26  is thermally insulated as well as possible from the outside. This evacuated area in the container  21  is separated in a gastight manner by the winding support  26  itself and by the two suspension elements  48  from the Intermediate spaces  39  and  38  around the heat transmission body  35 . 
     The rotor  20  together with the two rotor shafts  34  and  4  and the two magnetic bearings  2  and  3  are now jointly arranged in a gas area  60 , which is surrounded in a gastight manner by a wall  61  through which gas cannot pass. This gas area  60  is filled with a gas  50  with a predetermined composition, in particular a chemically resistant (inert) gas such as neon or helium, or a mixture of them. 
     The hollow shaft  34  on the rotor  20  now preferably opens, as illustrated, at the end facing the rotor  20  into the gas area  60 , so that a gas connection is formed between the external region of the gas area  60  and the intermediate spaces  37 ,  38  and  39 . Furthermore, the bearing gaps  10  of the magnetic bearings  2  and  3  are also each open on both sides to the gas area  60 . The intermediate spaces  37 ,  38  and  39 , the bearing gaps  10  and the other gas area  60  are thus filled with the same gas  50 . The gas  50  thus at the same time forms the contact gas for cooling the winding  25  and acts as a protective gas for the magnetic bearings  2  and  3 , thus carrying out a plurality of functions. 
     The cold head  24  for the winding  2  and the cold heads  22  and  23  for the magnetic bearings  2  and  3  are passed through the wall  61  of the gas area  60 , and are expediently also held or secured on the wall  61  of the gas area  60 . The bearing outer parts  11  of the magnetic bearings  2  and  3  are also mounted on the wall  61 , via holding elements  52  and  53 , respectively. The wall  61  and the components which are mounted on it are preferably fixed in position and do not rotate with the rotor  20 . 
     The rotor shaft  4 , which is mounted in the magnetic bearing  3 , passes through an opening in that end face of the wall  61  of the gas area  60  which is opposite the cold head  24 . This passage for the rotor shaft  4  through the wall  61  of the gas area  60  is sealed from the inside by an externally located rotating seal  40 , in particular a sliding ring or retaining ring seal, a radial shaft seal, a gland seal or a ferro-fluid seal against the ingress of air from the outside or against the contact gas  50  escaping. 
     The pressure of the gas  50  in the gas area  60  is generally set to at least atmospheric pressure (approximately 1 bar) and preferably to a pressure which is greater than atmospheric pressure. This results in a device which is insensitive to pressure fluctuations and is particularly well protected against air moisture entering from the outside, and against leakage. 
     The gas  50  is generally at least approximately at the ambient temperature in the region of the gas area  60  (outer area) that is located outside the rotor  20  and outside the magnetic bearings  2  and  3 . The temperature gradient between the cryogenic temperatures inside the rotor  20  and inside the magnetic bearings  2  and  3 , on the one hand, and the considerably higher temperature in the external area of the gas area  60  on the other hand is maintained in relatively narrow gaps, which are filled with the gas  50  and are formed by the intermediate spaces  37  to  39  and the bearing gaps  10 . In order to produce the temperature gradient in the gas gap which is formed from the intermediate space  37  between the hollow shaft  34  and the cold head  24 , annular brushes, which are not shown, for example three to five brushes, can also be arranged staggered in the axial direction in the gas gap, in order to avoid or to reduce the introduction of heat by convection. 
     Outside the container  21 , the winding  26  surrounds a stator winding  45  on a stator support  46 . The stator winding  45  and stator support  46  together with an external housing which encloses them both form the stator of an electric motor, in particular of a synchronous motor, or generator. These are the preferred applications, but not the only applications, of the device according to the invention. 
     FIG. 2 shows a magnetic bearing which may be used in particular as the magnetic bearing  3  shown in FIG. 1, illustrated in an enlarged, perspective form. The bearing inner part  5  is provided with two or more, for example six, permanent-magnet elements (permanent magnets)  6   a  to  6   f  in the form of annular disks. These permanent-magnet elements  6   a  to  6   f  are in each case polarized such that, seen axially, that is to say in the direction of the rotation axis A, the polarization alternates from one element to the next. The individual polarization directions are indicated by lines  7  with arrows on them in the figure. Elements (intermediate elements)  8   a  to  8   e  composed of a ferromagnetic material, for example iron, and in the form of annular disks are arranged between the permanent-magnet elements  6   a  to  6   f . Furthermore, ferromagnetic elements  8   f  and  8   g , which correspond to the elements  8   a  to  8   e , are provided on the end-face outer surfaces of the outer permanent-magnet elements  6   a  to  6   f . The ferromagnetic material of these ferromagnetic elements  8   a  to  8   g  is used to concentrate and homogenize the magnetic flux on the cylindrical outer surface of the bearing inner part  5 , and thus increases the supporting force of the bearing  2 . At the same time, the ferromagnetic elements  8   a  to  8   g  also mechanically reinforce the bearing inner part  5  with the permanent-magnet elements  6   a  to  6   f , which are generally composed of a brittle material. All the elements  6   a  to  6   f  and  8   a  to  8   g  are mounted in the form of a stack, axially one behind the other, on the rotor shaft  4 . The rotor shaft  4  is advantageously composed of a nonmagnetic material, or material which cannot be magnetized, for example of a special steel. 
     The bearing inner part  5  is surrounded by a hollow-cylindrical, fixed-position bearing outer part  11 , separated by a bearing gap  10 . The gap width (radial size) w of the bearing gap  10  between the bearing inner part  5  and the bearing outer part  11  is preferably in the same order of magnitude as the axial thickness d 2  of the ferromagnetic intermediate elements  8   a  to  8   g , and is typically between 0.1 mm and 5 mm, and preferably between 0.3 mm and 1.5 mm. 
     The bearing outer part  11 , which forms a stator, has a superconducting structure  12  on its inner face, facing the bearing inner part  5 , which superconducting structure  12  is supported externally on a supporting body  13  which is composed, for example, of metal, in particular copper (Cu). Any known superconductor material, in particular textured YBa 2 Cu 3 O 7-x , may be used as the superconducting material for the superconducting structure  12 . The crystalline a-b planes of at least a large proportion of the superconductor material are in this case advantageously aligned essentially parallel to the outer surface of the bearing inner part  5 . The mean grain size (grain diameter) of the crystallites (grains) of the superconductor should in this case be larger than the axial thickness d 1  of the permanent-magnet elements  6   a  to  6   f , with the grain size being considered in the crystalline a-b planes. 
     The magnetic flux which is caused by adjacent permanent-magnet elements (for example  6   d ,  6   e ) on the bearing inner part  5  is largely concentrated in the shared ferromagnetic intermediate element ( 8   d ) and thus emerges with a high flux density via this intermediate element into the bearing gap  10 . In the bearing gap  10 , the flux path is closed to the respectively adjacent intermediate elements ( 8   c  and  8   e , respectively). The magnetic flux which is produced by the individual magnetic poles induces corresponding currents, which in turn result in magnetic coupling or negative feedback, in the fixed-position superconducting structure  12  which surrounds the bearing inner part  5  and bounds the bearing gap  10 . The magnetic flux path in the area of the nonmagnetic material of the rotor shaft  4  is closed on the side of the rotor shaft  4 . This advantageously avoids any magnetic short-circuit there, which would lead to a reduction in the magnetic flux emerging into the bearing gap  10 . 
     The permanently magnetic material of the elements  6   a  to  6   f  should have a maximum energy product (B*H) max  of at least 20 MGOe, in order to apply the necessary bearing forces and provide the necessary bearing robustness. Suitable materials with such a high energy product are in particular a neodymium (Nd) iron (Fe) boron (B) alloy, or a samarium (Sm) cobalt (Co) alloy. The permanently magnetic material may also, if required, be cooled in order to increase its coercivity field strength. 
     Outside the region of the bearing inner part  5 , the magnetic bearing  3  has a holding and centering apparatus  15  which can be lowered and absorbs the bearing force when at rest, when the superconducting material is above its operating temperature. 
     At the same time, the bearing position is centered axially and laterally by a groove  17  in the rotor shaft  4  and by a rest  18 , in the form of a blade, on the device  15 . Electromagnetic induction results in electromagnetic forces between the bearing inner part  5  and the bearing outer part  11  (stator) which surrounds it, and these electromagnetic forces act counter to the direction of movement and lead to the bearing inner part  5  and the rotor shaft  4  floating freely approximately in the center of the bearing gap  10 . This type of bearing makes it possible to achieve bearing pressures of up to  10  bar and considerable bearing stiffness against movements of the rotor shaft  4  and of the rotor  20  in the radial and axial directions. 
     FIG. 3 shows a further embodiment of a magnetic bearing, which is expediently used as the magnetic bearing  3  (or  2 ) as shown in FIG. 1. A stack of permanent-magnet elements  6   j  alternating with ferromagnetic elements  8   i  is once again provided on the bearing inner part  5 . This stack of elements  6   j  and  8   i  is mounted, as shown in FIG. 3, on a supporting body  54 , which is kept at a distance from the rotor shaft  4  by holding disks  57  which are composed of thermally insulating, mechanically robust material, for example of a fiber-reinforced, in particular glass-fiber-reinforced, plastic, and with a thermal insulation material  55  located in between. The bearing outer part  11  likewise once again has a superconducting structure  12  and a supporting body  13  for the superconducting structure  12 . 
     A cold head  23  is once again connected to the supporting body  13 , running vertically from the outside to the inside, and is thus thermally coupled to it, and rests on or is attached to an outer sleeve  19  of the magnetic bearing  3 . The supporting body  13  is connected to the outer sleeve  19  via holding disks  57  and thermal insulation material  56  arranged in between. 
     In the particular refinement shown in FIG. 3, a thermal insulation body  14  or  14 ′, which points inward to the rotor shaft  4  from the outside sleeve  19 , is now in each case mounted in front of the end faces of the superconducting structure  12  with the supporting body  13  and the inner bearing part  5  with the magnet stack on both sides, axially with respect to the rotation axis. A first bearing gap element  41 , which runs parallel to the rotation axis A, is formed between the thermal insulation body  14  and the rotation shaft  4 . A second bearing gap element  42 , which runs at right angles to the rotation axis A, is formed between the bearing inner part  5  and a side of the thermal insulation body  14  which faces inward toward the bearing inner part  5 . A third bearing gap element  43 , which runs at right angles to the rotation axis A, is formed in an analogous manner between the bearing inner part  5  and a side of the further thermal insulation body  14 ′ which faces inward toward the bearing inner part  5 , and a further, fourth bearing gap element  44 , which runs parallel to the rotation axis A once again, is formed between the rotation shaft  4  and the thermal insulation body  14 ′. A gas passage through the magnetic bearing  3  for the gas  50  is formed by the first bearing gap element  41 , the second bearing gap element, the bearing gap  10 , the third bearing gap element  43  and the fourth bearing gap element  44  that are connected in series. The advantage of this specific embodiment of the bearing gaps is that the first bearing gap element  41  and the fourth bearing gap element  44 , which are located in the comparatively warm end regions of the magnetic bearing  3 , are located closer to the rotation axis A than the bearing gap  10 , and the gas  50  in the two bearing gap elements  41  and  44  is subjected to a correspondingly less centrifugal force during rotation of the rotor shaft  4  with the bearing inner part  5 . This in turn means that, when the bearing inner part  5  is rotating on the rotor shaft  4 , the density of the gas  50  which rotates with it in the bearing gap elements  41  and  44  (as well as  42  and  43 ) which are closer to the axis is reduced, and that in the bearing gap  10  which is further from the axis is greater. Since, on the other hand, the density of the gas  50  increases again since the temperature decreases sharply toward the bearing gap  10 , these two effects that act in opposite senses compensate for one another, to a certain extent. This embodiment of the magnetic bearing  3  thus results in a more homogeneous density distribution and more stable layering of the gas  50  within the magnetic bearing  3 . 
     FIG. 4 shows a cross section through a modified form of a magnetic bearing  2  for the device as illustrated in FIG.  1 . The permanent-magnet elements on the outer bearing part, which is annotated  29 , of the magnetic bearing  2  and a hollow-cylindrical, superconducting structure, which is annotated  32  and is fitted on the outside of the hollow shaft  34 , are now provided as the inner part  31 . Furthermore, the permanent magnets of the magnetic bearing  2  are not stacked axially, with permanent-magnet elements  27   i ,  27   j  (where 1≦i≦j; 1≦j≦n) which are axially extended and are in the form of segments of hollow cylinders being provided instead. The permanent-magnet elements  27   i ,  27   j  are each spaced apart from one another via ferromagnetic elements  28   k (where 1≦k≦2n), which are like strips and are likewise in the form of segments of hollow cylinders, and, together with them, form a closed hollow-cylindrical arrangement for the outer bearing part  29 . The fixed-position outer bearing part  29  surrounds the inner bearing part  31 , which can rotate, at a distance w which is defined by the gap width w of the bearing gap  10 . The hollow shaft  34  in turn surrounds the heat transmission body  35 , forming the intermediate space  37  with the gap width x. The illustrated cross section clearly shows that both the gaps, which are arranged concentrically with one another, the bearing gap  10  and the intermediate space  37 , are each filled with the same gas  50 . 
     FIG. 5 shows an embodiment of a device, modified from that shown in FIG. 1, in which the heat transmission unit as shown in FIG. 1, which is formed from the heat transmission body  35  and the cold head  24 , is replaced by a heat transmission unit as shown in FIG. 5, which operates on the heat pipe principle. Working liquid  50 ′, which preferably corresponds to the liquefied contact gas  50 , is introduced into the cavity  30  via a preferably vacuum-insulated heat pipe  70  and via an internal area  38 ′ which widens conically from the rear part of the hollow shaft  34  through the suspension element  48  to the cavity  30  in the winding support  26 . The heating results in the working liquid being vaporized, and dissipates heat from the winding support  26  in the form of vaporization heat. The vaporized gas  50 , which is used as the working gas for the heat pipe  70 , is transported on the opposite path through the internal area  38 ′ and through the heat pipe  70  to a condenser  71  which is located outside the gastight wall  61 , where it is cooled down via the cold head  72  until it once again liquefies (condenses) to form the working liquid  50 ′. The circuit (working cycle) in the heat pipe  70  then commences once again. In this embodiment, the gas  50  is used not only as a contact gas but also as a working gas for the cooling process by the heat pipe. A narrow intermediate gap  37 ′ is formed between the heat pipe  70  and the hollow shaft  34 , is connected to the rest of the gas area  60 , and allows mechanical decoupling between the heat pipe  70  and rotating parts such as the hollow shaft  34 . 
     For further details of the materials, configuration, dimensions and operation of the magnetic bearings, in particular as shown in FIGS. 1 to  5 , reference shall be made to DE 44 36 831 C2, whose contents are also included in the disclosure of the present application. 
     The invention has been described in detail with particular reference to preferred embodiments thereof and examples, but it will be understood that variations and modifications can be effected within the spirit and scope of the invention.