VЕRFАНRЕN ZUR ЕNТNАНМЕ VОN WÄRМЕ ВЕI UМGЕВUNGSТЕМРЕRАТUR

The invention concerns a procedure for the transformation by warmth into mechanical work, with which in a cyclic process a working medium under delivery is consolidated by warmth, afterwards over a first heat exchanger in thermal contact with the environment is brought, afterwards under production of mechanical work is eased, on which the cyclic process will again go through. There is well-known different working procedures, in order to convert heat energy into mechanical work. Usually with such cyclic processes a working medium is consolidated, eased, cooled down warmed up, in the warmed up condition, on which the cyclic process begins from the front. A condition for such cyclic processes is that two different temperature levels are available, which are consulted for warming up and/or cooling of the working medium. Generally thereby a certain temperature is defined as ambient temperature, that is the temperature of a medium, which is available for an unlimited period in principle and free of charge. This can be for example the air temperature of the environment or take the temperature of a waters, out of the water for purposes of the temperature exchange in sufficient quantity can. So far no cyclic processes well-known, with which it is possible to win mechanical work from heat energy, are to be had without a heat distribution medium medium, its temperature substantially by the ambient temperature differ. After past view such a cyclic process is impossible by the second main clause of the caloric theory. In a more precise version of the second main clause of the caloric theory stated that the efficiency of any cyclic process cannot exceed the so-called Carnot efficiency for the transformation of thermal energy into mechanical work it computes itself, from the relationship of the temperature levels the available. Material existing procedures and devices are however generally also from Carnot wirkungsgard far. There is devices for the production of temperature differences well-known, which use gas dynamics effects, which arise during high accelerations, in order to manufacture temperature differences. These devices are not suitable however, in order to accomplish cyclic processes for the production of mechanical work. The DE 38 12 928 A shows a device, which tries, to overcome the above disadvantages. However also with such a device no wentliche improvement of the efficiency is possible. Task of the available invention is it to indicate a procedure of the kind described above which makes it possible to win mechanical work from thermal energy with a greatest possible efficiency. A further task of the invention is it to indicate a device with which the execution of the procedure according to invention is possible. This procedure is characterized according to invention by the fact that the working medium is led after the relaxation by a further heat exchanger, which is arranged inside a fast rotating rotor and which is surrounded by at least an essentially circular gas area at its exterior, at its exterior warmth is exhausted. The inventor of the available invention recognized that including the statistic gas theory in connection with the consideration force of gravity of the affecting the Gasmoleküle or atoms and/or acceleration the representation of cyclic processes is possible, which exhibit a particularly high efficiency. In this connection however that the effects caused by the force of gravity are very small, 3 RK 413,734 B is problematic whereby the technical conversion is very difficult. According to invention the use from heat energy can be achieved by the cyclic process to the production by mechanical work under economically justifiable basic conditions. A substantial condition for the procedure according to invention is the achievement of highest accelerations by a fast running rotor, whereby the obtained acceleration values are selected so highly as possible. It is particularly preferential, if the working medium is led downstream the rotor by a compressor. The heating up caused in the compressor is anyhow so small that the working medium cooled down in the rotor remains below the ambient temperature. Thus it is ensured that the working medium takes up ambient heat in the first heat exchanger. In a particularly favoured execution variant of the procedure according to invention it is intended that the working medium is essentially led in axial direction by the rotor. In this way the effects of high acceleration can be eliminated inside the rotor on the pressure ratios in the working medium to a large extent. Further the available concerns invention a device to the withdrawal of warmth with ambient temperature with a rotor, which essentially exhibits one in axial direction flow throughable heat exchanger, which is limited at its exterior of a cylindrical wall, at their exterior at least an essentially circular gas area is intended. This device is characterized according to invention by the fact that the heat exchanger is essentially ring-cylindrically trained and that the gas area is divided into several ring-cylindrical subspaces into radial direction. Only by the descriptive training of the rotor it is possible to realize in more technical and for economically meaningful way a cyclic process of the kind described above. In principle it is possible that in the individual subspaces the same gas is present in each case. In such a case generally the pressure at the exterior of a subspace is larger than the pressure at the inside of the further subspace following outside to this subspace. That is, that within the individual subspaces the pressure increases by the ZentripetalBeschleunigung from the inside outward, this increase however in the borders of the individual subspaces is interrupted. From this results a mechanical load of the partitions between the individual subspaces, which is technically controllable however, since the resulting thrust force works outward and from there the partitions are not burdening on becoming baggy. In preferential way however different gases are taken up in the individual subspaces, which exhibit in particular different critical temperatures and pressures. In this way it can be achieved that the pressure load of the partitions is minimized, since in the equilibrium inside and outside essentially the same pressure fits. Due to the extremely fast rotation of the rotor the pressures available inside the rotor differ in a state of rest substantially those in the operating condition. In order to minimize the load of the partitions and the other construction units, a printing control mechanism is intended, which stands with the ring-cylindrical subspaces in connection, in order to adjust the internal pressure in a particularly preferred execution variant of the invention. Particularly preferential way are the ring-cylindrical subspaces by thin-walled cylindrical partitions from each other separated. In this way the mechanical loads of the individual construction units can be minimized. In the consequence the available invention on the basis the remark examples represented in the figures more near describes. Show: Fig. 1 a schematic representation of a device for the execution of the erfin4 RK 413,734 B dungsgemäßem of procedure, Fig. 2 a rotor of the device of Fig. 1 in the increased yardstick, Fig. 3 a cut after line Ill III in Fig. 2, Fig. 4 a diagram, which represent the temperature gradient in radial direction of the rotor, and Fig. 5 a Ts-diagram, which explains the cyclic process. The device of Fig. 1 consists of a turbine 11 for the expansion of the working medium, which is divided into two sections 11a, 11b. In the first section 11a a heat exchanger 11c is intended, in order to make an isotherm possible expansion. In principle it is possible to plan several turbine stages in those the working medium is adiabatically eased and the heat exchangers between the individual turbine stages to plan, whereby only one approach isotherm relaxation is reached. If the heat exchanger 11c is intended in the turbine 11, a large isotherm relaxation can be actually achieved. In the second section 11b of the turbine 11 an adiabatic relaxation takes place. Therefore the cooling agent at the exit of the turbine 11 with a temperature is present, which is under the ambient temperature. By the turbine 11 a generator 12 is propelled and propelled at the same time a rotor 13 of a centrifuge, which is flowed through by the working medium in axial direction. In a turbine 14 a compression takes place, on which the working medium is reconducted over a return line again to the turbine 11. The rotor 13 possesses a ring-cylindrical heat exchanger 18 and several gas areas 17a, 17b, 17c, 17d, which are likewise ring-cylindrically trained and lie outside of the heat exchanger 18. It is to be marked that the dimensions of the heat exchanger 18 and the gas area 17a, 17b, 17c, 17d in radial direction in Fig. 1 are exaggerated represented, because with material remarks these dimensions are very small, and the heat exchanger 18 and the gas areas 17a, 17b, 17c, 17d lies in the proximity of the outside coat of the rotor 13. At its exterior the rotor 13 equipped with cooling fins 19 is, which represent a heat exchanger to the removal of warmth. This is suggested by the arrows 20. In preferential way the gas areas 17a, 17b, 17c, 17d are filled with different gases, whereby the internal gas area 17a is filled with helium for example, that to it following gas area 17b with xenon, the third gas area 17c with nitrogen or a suitable hydrocarbon and the outermost gas area 17d with a suitable refrigerant. By the fast rotation of the rotor 13 in the gas areas 17a, 17b, 17c, 17d a temperature gradient, is from outside to inside caused which cools the working medium down in the heat exchanger 17 strongly. In the heat exchanger 16 warmth on the temperature level of the environment is supplied, which is suggested by the arrows 21. An increase of the efficiency can be obtained, if the waste heat of the rotor 13 according to the arrows 20 is likewise supplied to the heat exchanger 16. In Fig. the rotor 13 is in detail represented 2 in a modified execution variant. The working medium is supplied inside a hollowbored first wave 22, which is stored in a camp 23, and led across distribution conduits 24 radially to the heat exchanger 18 outward. Inside the heat exchanger 18 the working medium flows into axial direction for the opposite side of the rotor 13, in order into further distribution conduits 25 radially inward to a further wave 26 to be led, which is stored in a camp 27. As is the case for the previous execution variant four gas areas 17a, 17b, 17c, 17d are radially into one another intended. At the exterior a heat exchanger 18 is arranged for the removal of the warmth. A housing 28 is schematically suggested, in which the rotor is swivelling arranged, which exhibits a multiplicity of magnet 29 in circumferential direction. The magnets 29 serve for it at high numbers of revolutions the camps 23 and 27 to relieve and are with not represented magnets at the exterior of the rotor 13 even in reciprocal effect. The polarity is in such a way arranged that RKs 413,734 B repel themselves the magnets 29 and the magnets at the rotor 13, whereby a Kraft directed inward is expenditure-practiced on the lateral surface of the rotor 13, high mechanical loads due to centrifugal forces the clear reduced and made possible higher numbers of revolutions. Inside the rotor 13 at least one gas tank 30 is intended, which stands with one the gas area 17a, 17b, 17c, 17d over not represented lines in connection. Preferably however the header tank possesses 30 not represented Unterbehälter with the individual gas areas the 17a, 17b, 17c, 17d is separately connected. In this way the middle pressure level in the gas areas 17a, 17b, 17c, 17d can be held to a large extent independently of the respective number of revolutions of the rotor 13 to a pre-determined value, so that lo the mechanical load of the partitions between the heat exchanger 18 and the gas areas 17a, 17b, 17c, 17d remains within pre-determined borders. In the following tables 1 to 4 the ZustandsgröBen of the gas and/or that is indicated to table 2 on the gas area 17b, table 3 gases in the individual gas areas 17a, 17b, 17c, 17d, whereby the table 1 to the internal gas area 17a refers, on the gas area 17c and table 4 on the gas area 17d in the way of a remark example. The left table half indicates in each case for it the variables of state at the external wall of the respective gas area 17a, 17b, 17c, 17d, and the right table half indicates in each case for it the variables of state at the inner wall of the respective gas area 17a, 17b, 17c, 17d. In the tables 1 to 4 mean: T temperature in K D density in kg/m3 p pressure in MPa s entropy in kJ/kgK u internal energy in k J/kg h enthalpy in k J/kg table 1 T 276.32 D 174.43 p 14.33 s 5.18 u 173.15 h 255.33 T 424.17 D 129.39 p 17.61 s 5.62 u 294.47 h 430.58] 121.51 D 28.62 p 0.91 s 5.18 u 81.95 h 114.07 T 276.32 D 50.25 p 4.07 s 5.62 u 195.45, h 276.45 table 2 6 RKs 413,734 B table 3 T 579.04 D 94.29 p 17.54 s 5.98 u 419.52 h 605.58 T 739.98 D 77.64 p 18.39 s 6.24 u 550.60 h 787.48 T 424.17 D 45.76 p 5.88 s 5.98 u 307.62 h 436.27 r 579.04 D 42.67 p 7.54 s 6.24 u 426.66 h 604.32 table 4 Fig. shows 3 schematically a cut after line III - III in Fig. 2, whereby for the increase of the clarity of the heat exchangers 18 and the cooling fins 19 are omitted. Arrows 20 symbolize the heat flow. In Fig. a diagram is represented 4, which indicates schematically the temperature distribution in radial direction of the rotor 13, which is indicated by r. The curve K1 represents the temperature T in the open-circuit condition, i.e., if no heat flow arises, what the case is if the rotor 13 is insulating inside and outside. The curve K2 represents the temperature T in the enterprise, i.e. if a heat flow in radial direction is present. Fig. an idealized T-s shows 5 - diagram, with which the temperature over the entropy is laid on. The cyclic process will go through in the direction of the arrows 31. With the double arrow 32 the temperature difference of the centrifuge, i.e. the rotor 13 represented over the gas areas 17a, 17b, 17c, 17d is. Under the losses with the heat transition the temperature difference 33 actually usable in the cyclic process is clearly smaller. The conditions 1, 2, 3, 4 in the diagram correspond to the conditions to similar to designated points in Fig. 1. It is to be for example marked that with a single-phase working medium the changes in status 1 --, 2 and 3 --, 4 is not exactly isothermal. The table 5 indicates the variables of state in the individual points by idealized assumptions. 7 RKs 413,734 B table point 1 point 2 point 3 point 4 T [kg/m3] [kJ/kgK] k J/kg k J/kg D p s u h 130 15 0.54937258 130 70 2.10257662 283 316.5007 30.2486572 283 92.150807 7.66041346 5.44088686 4.92707388 4.92707388 5.44088686 92.1986033 128.823442 77.8876766 107.924486 153.810311 249.382476 192.911843 276.040941 the available invention makes it possible to realize a device and a cyclic process the WJrkungsgrade exhibits, which lie substantially over those conventional solutions.