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11 EP 2 578 800 A1 12 steam flow decelerates. As shown above, the air pres- sure difference occurs among the steam flow passages portions 50, which deteriorates the safe operation. [0053] In this configuration, the operating steam pres- sure adjusting holes 51 are formed on the rotor disk 20 and the stator disk 30 appropriately in order to adjust the air pressure difference among the steam flow passages portions 50 by connecting these steam flow passages portions 50 in addition to the steam supply route. When the air pressure difference occurs among the steam flow passages portions 50, the steam pressure can be adjust- ed among the steam flow passages portions 50 via the operating steam pressure adjusting holes 51. Therefore the radial flow steam turbine 100 can ease the rapid in- crease or decrease of the steam flow volume appropri- ately, and the steam stuffing problem can be avoided. [0054] Next, the steam flow is described. [0055] Fig. 4 is a figure showing the steam flow super- imposed onto the configuration shown in the Fig.1. [0056] The steam generated in the steam supply source (it is not shown in figures) is introduced from the steam flow input openings 41. In this configuration, the steam flow input openings 41 are formed on both sides of the casing 40, the steam is supplied from both sides into the casing 40. [0057] The introduced steam goes to the rotor disk 20 along to the rotation shaft 10, then the steam goes through the through opening 22 on the rotor disk 20, and passes through the steam supply route formed by the steam passage portion 31 on the stator disk 30. Then the steam flows in the axial direction in the vicinity of the rotor disk 10 along to the rotation shaft 10. The steam flowing in the steam supply route flows in the axis direc- tion, then reaches each operating steam flow passage portion 50 and bend and flows into each operating steam flow passage portion 50. [0058] The operating steam flowing into each operat- ing steam flow passage portion 50 in the outflow radial direction expands and runs through each stator blade 31 and each rotor blade 21 at high speed. The steam gives the rotation energy to each rotor blade 21, and the rotor blades 20 and the rotation shaft 10 rotate together. In this configuration, the steam goes through both side sur- faces of the rotor disk 20, the steam passes through each stage of the stator blades 31 and the rotor blades 21 according to the air pressure difference along the radial direction, and the steam gives the rotation energy to each rotor blade 21 while passing through the operating steam flow passage portion 50. [0059] In this configuration, the rotor blades 21 are mounted on both side surfaces of the rotor disk 20 and the operating steam flow passage portions 50 are formed on both side surface of the rotor disk 20. Thus, about twice the rotation torque can be obtained compared with the case of the configuration in which the rotor blades 21 are mounted on single side surface. [0060] In the conventional radial flow steam turbine shown in Fig.7, the corresponding operating steam flow passage portion running through the stages of the stator blades and the rotor blades can be formed as only one, so the utilized operating steam flow passage portion is only one. On the other hand, regarding the radial flow steam turbine of the present invention, the configuration shown in Fig.4 can form and utilized eight operating steam flow passage portions in the outflow direction, and the output can be enhanced. (Embodiment 2) [0061] Embodiment 2 describes the example of the ra- dial flow steam turbine in which there is a single stage of the rotor blades 21 arrayed annularly and a single stage of the stator blades 31 arrayed annularly. The merit of the single stage is that the safe operation is possible when the steam pressure supplied from the steam supply source is not large enough. [0062] Fig.5 (a) shows the example in which two rotor disks 20 are installed on the rotation shaft 10 and three stator disks 30 are installed. The single stage of the rotor blades 21 is mounted on the rotor disk 20, and the single stage of the stator blades 31 is mounted on the stator disk 30, so the unit is formed as a single stage. The number of the rotor disk 20 and the stator disk 30 can be modified corresponding to the amount of steam supplied from the steam supply source. [0063] As shown in Fig.5 (b), in the operation of the single stage of the radial flow steam turbine, the same as Embodiment 1, the steam generated in the steam sup- ply source (it is not shown in figures) is introduced from the steam flow input openings 41. The introduced steam goes to the rotor disk 20 along to the rotation shaft 10, then the steam goes through the opening portion 21 on the rotor disk 20, and passes through the steam supply route formed by the steam passage portion 32 on the stator disk 30, then the steam flows in the axial direction in the vicinity of the rotor disk 20 along the rotation shaft 10. The steam flowing in the steam supply route flows in the axis direction, then reaches each operating steam flow passage portion 50 and bends and flows into each operating steam flow passage portion 50. In this config- uration, the rotor blade 21 and stator blade 31 compose a single stage, the supplied steam is not required to be high temperature and high pressure. If the amount of the supplied steam is large enough, the rotor disk 20 and the stator disk 30 are provided in multi-stage. The same as Embodiment 1, a large amount of steam can be supplied enough via the through opening 22 formed on the rotor disk 20 and the steam flow portion 32 formed on the stator disk 30. [0064] As shown this Embodiment 2, if the steam sup- plied from the steam supply source such as a boiler is not enough high temperature and high pressure, the ra- dial flow steam turbine in which there is a single stage of the rotor blades 21 arrayed annularly and a single stage of the stator blades 31 arrayed annularly can be applied. The cost for the facility can be restrained and the wasted 5 10 15 20 25 30 35 40 45 50 55 7PDF Image | EP 2 578 800 A1 EUROPEAN PATENT
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