Patent Document

CROSS REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is the US National Stage of International Application No. PCT/EP2015/072911 filed Oct. 5, 2015, and claims the benefit thereof. The International Application claims the benefit of European Application No. EP14188998 filed Oct. 15, 2014. All of the applications are incorporated by reference herein in their entirety. 
     
    
     FIELD OF INVENTION 
       [0002]    The invention relates to a turbomachine, especially to a steam turbine, having an inlet region for feeding steam, a rotatably mounted rotor, a casing which is arranged around the rotor, wherein a flow passage is formed between the rotor and the casing, wherein the flow passage and the inlet region are fluidically interconnected, having a shield which is designed in such a way that during operation steam which flows into the inlet region can be deflected into the flow passage, wherein the shield has a cooling medium feed which is designed in such a way that during operation cooling steam can flow into a cooling region which is arranged between the shield and the rotor. 
       BACKGROUND OF INVENTION 
       [0003]    Turbomachines such as steam turbines are exposed to a throughflow of a flow medium which as a rule has high temperatures and pressures. Therefore, in a steam turbine as an embodiment of a turbomachine steam is used as the flow medium. The steam parameters in the live steam inlet region are high to such an extent that the steam turbine is thermally heavily stressed at various points. Therefore, for example in the inlet region of the steam turbine the materials are thermally heavily stressed. A steam turbine comprises in the main a turbine shaft, which is rotatably mounted, and also a casing which is arranged around the turbine shaft. The turbine shaft is thermally heavily stressed as a result of the temperature of the inflowing steam. It is accepted that the higher the temperature, the higher is the thermal stress. Turbine blades are arranged on the rotor in so-called slots. During operation, the slots experience a high level of mechanical stress. The thermal stress, however, lowers the tolerable mechanical stress as a result of rotation and additional loading by the blades which are fastened on the rotor. 
         [0004]    From the thermodynamic point of view, it makes sense to raise the inlet temperature of the steam since the efficiency increases with higher inlet temperature. In order to extend the load capacity of the materials used in the steam turbine at high temperatures, the inlet regions of the shaft are cooled. Providing a suitable cooling method can be developed, changing to a higher quality, but more expensive, material can be dispensed with. 
         [0005]    A steam turbine plant comprises at least one steam generator and a first steam turbine, which is designed as a high-pressure turbine section, and further turbine sections which are designed as an intermediate-pressure turbine section or a low-pressure turbine section. After live steam has flown through the high-pressure turbine section, the steam is heated again in a reheater to a high temperature and conducted into the intermediate-pressure turbine section. The steam which comes from the high-pressure turbine section is referred to as cold reheat steam and is comparatively cool in comparison to the live steam. This cool reheat steam is used as cooling medium. 
         [0006]    This means that the cold reheat steam is conducted into the inlet region of the steam turbine and lowers the material temperature there. However, it is such that the cold reheat steam in the inlet region, for example in an intermediate-pressure turbine section, leads to very large temperature differences. This leads to the disadvantage that despite the cooling locally high temperature gradients, and high thermal stresses as a result thereof, occur. Furthermore, it can bring about local dimensional changes which is enforced by thermal distortion as a result of unequal thermal expansion since intensely cooled and uncooled regions are arranged next to each other. Furthermore, in the event of a cooling failure, i.e. that the cold reheat steam is not made available and therefore forms a failure case, thermal shocks occur, leading to extremely severe thermal stresses. 
         [0007]    In the failure case, this means that in the event of a failure of the cooling the previously cooled shaft expands to a significant degree. This thermal expansion is structurally to be taken into consideration and makes the conducting of the cooling medium and sealing of the cooled region more difficult. 
         [0008]    Document DE 34 06 071 A1 disclosed a shield, wherein the shield has only a cooling steam line but no additional line. 
       SUMMARY OF INVENTION 
       [0009]    The invention starts at this point. It is the object of the invention to specify improved cooling for a steam turbine. 
         [0010]    This object is achieved by means of a turbomachine, especially a steam turbine, having an inlet region for feeding steam, a rotatably mounted rotor, a casing which is arranged around the rotor, wherein a flow passage is formed between the rotor and the casing, wherein the flow passage and the inlet region are fluidically interconnected, having a shield which is designed in such a way that during operation steam which flows into the inlet region can be deflected into the flow passage, wherein the shield has a cooling medium feed which is designed in such a way that during operation cooling steam can flow in a cooling region which is arranged between the shield and the rotor, wherein the shield has a line which creates a fluidic connection between the cooling region and the inlet region. 
         [0011]    The invention therefore refers to turbomachines, especially steam turbines, which comprise a shield which is arranged in the inlet region and shields the shaft from the hot flow medium. Used for the cooling is a cooling medium feed which during operation conducts cooling steam to the rotor. The invention follows the following ideas: Up to the present, a comparatively intense cooling of the rotor has been put into effect in the cooling region, i.e. between shield and rotor surface. 
         [0012]    The rotor is cooled by a cold reheat steam which, however, leads to very intense cooling down of the rotor in the inlet region. In the event of a failure of the cooling medium, the rotor heats up in this region very intensely which leads to undesirable alternating extreme thermal stresses. In order to avoid this, it is proposed according to the invention to design the shield with a line through which the live steam can flow into the space between the rotor and the shield in addition to the cooling medium feed. The flow rate of the cooling medium and the flow rate of the live steam through the line is selected in this case in such a way that the temperature of the rotor in the inlet region is heated to a limit value. This limit value is selected in this case in such a way that in the event of a failure of the cooling medium heating up to the maximum temperature, i.e. heating up without cooling medium, is moderate. 
         [0013]    According to the invention, it is therefore proposed to realize a passive mixed cooling, by means of holes, which can be of small design, in the shield to add a certain quantity of live steam to the cooling steam from the cooling medium feed. As a result, by suitable selection of the lines a suitable mixing temperature can be established. 
         [0014]    A flow medium which in addition to steam can be ammonia or a steam-CO 2  mixture is to be understood by the term steam. 
         [0015]    Using the invention, therefore, damage being caused by the shaft as a result of unstable malfunctioning behavior when cooling with very cold reheat steam or with costly instrumentation and control implementation in the case of temperature-controlled cooling steam is avoided. Such a new cooling arrangement is advantageous since it is passive. This means that there is no requirement for costly instrumentation and control systems and control valves for temperature control of the cooling medium. As a result of the small temperature differences in the component, a low level of thermal stress, a small additional local distortion as a result of cooling and a more robust behavior in the event of a short-term failure of the cooling are achieved. 
         [0016]    Advantageous developments are specified in the dependent claims. 
         [0017]    In a first advantageous development, the turbomachine is of double-flow design. This means that the shield covers a region which allows the inflowing steam to flow into a first flow and a second flow. 
         [0018]    In one advantageous development, the cooling medium feed is designed in such a way that during operation the cooling steam impinges tangentially upon the rotor. Therefore, the cooling medium feed does not reach radially through the shield but in essence is conducted in the circumferential direction so that the cooling steam experiences a swirl into the region between the shield and the rotor. 
         [0019]    By the same token, in an advantageous development, the line can be designed in such a way that during operation steam from the inlet region impinges tangentially upon the rotor. In this case, it is also proposed not to design the line radially through the shield but to take into consideration a tangential component which leads to a swirl of the steam from the inlet region into the space between shield and rotor. 
         [0020]    In the case of the tangential arrangement of the cooling medium feed, a residual cooling effect as a result of the swirl-imposed inflow of live steam can be maintained in the event of failure of the cooling. 
         [0021]    The above-described characteristics, features and advantages of this invention and also the way in which these are achieved become clearer and more distinctly comprehensible in conjunction with the following description of the exemplary embodiments which are explained in more detail in conjunction with the drawings. 
         [0022]    Exemplary embodiments of the invention are described below with reference to the drawing. This drawing is not to definitively represent the exemplary embodiments, rather the drawing, where useful for the explanation, is implemented in schematized and/or slightly distorted form. With regard to supplements to the teachings which are directly recognizable in the drawing, reference is made to the applicable prior art. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0023]    In the drawing 
           [0024]      FIG. 1  shows a schematic view of a steam power plant 
           [0025]      FIG. 2  shows a schematic view of the invention during operation 
           [0026]      FIG. 3  shows a schematic view of the invention in the event of failure of the cooling medium feed 
           [0027]      FIG. 4  shows a side view of the arrangement according to the invention 
           [0028]      FIG. 5  shows a side view of the arrangement according to the invention in an alternative embodiment. 
       
    
    
     DETAILED DESCRIPTION OF INVENTION 
       [0029]      FIG. 1  shows a steam power plant  1  in a schematized overview. The steam power plant  1  comprises a high-pressure turbine section  2  which has a live steam feed  3  and a high-pressure steam outlet  4 . Live steam from a live steam line  5  flows through the live steam feed  3 , wherein the live steam was produced in a steam generator  6 . Arranged in the live steam line  5  is a live steam valve  7  which controls the flow of live steam through the high-pressure turbine section  2 . Also arranged in the live steam line  5  is a stop valve (not shown) which closes off the steam feed to the high-pressure turbine section  2  in the event of a failure. After steam has flown through the high-pressure turbine section  2 , during which the steam in the high-pressure turbine section  2  converts the thermal energy into rotational energy of the rotor  21 , the steam flows out of the high-pressure steam outlet  4  into a cold reheat line  8 . The steam in the cold reheat line  8  in comparison to the steam parameters of the live steam in the live steam line  5  is such that this cold reheat steam can be used as cooling medium, which is shown schematically in  FIG. 1  by means of the cooling medium line  9 . The cold reheat steam is heated in a reheater  10  and via a hot reheat line  11  conducted to an intermediate-pressure turbine section  12 . The cooling medium line  9  can be directed to the intermediate-pressure turbine section  12  into the inlet region (not shown). The rotor of the intermediate-pressure turbine section  12  is connected with torque transmitting effect to the rotor of the high-pressure turbine section  2  and also to the rotor  21  of a low-pressure turbine section  13 . Similarly, an electric generator  14  is connected with torque transmitting effect to the rotor  21  of a low-pressure turbine section  13 . After the steam has flown through the intermediate-pressure turbine section  12 , the steam flows out of the intermediate-pressure steam outlets  15  to the low-pressure turbine section  13 . The intermediate-pressure turbine section  12  selected in  FIG. 1  comprises a first flow  29  and a second flow  30 . The steam is conducted out of the intermediate-pressure steam outlets  15  in a crossover line  16  to the low-pressure turbine section  13 . After flowing through the low-pressure turbine section  13 , the steam flows into a condenser  17  and is condensed there, forming water. The steam which is converted in the condenser  17 , forming water, then flows via a line  18  to a pump  19  and from where the water is conducted to the steam generator  6 . 
         [0030]    The high-pressure turbine section  2 , the intermediate-pressure turbine section  12  and the low-pressure turbine section  13  together are referred to as a steam turbine and constitute an embodiment of a turbomachine. 
         [0031]    In  FIG. 2 , a view of the arrangement according to the invention is to be seen.  FIG. 2  shows in particular an inlet region  20  of the intermediate-pressure turbine section  12 . The intermediate-pressure turbine section  12  comprises a rotor  21  which is rotatably mounted around a rotational axis  22 . The rotor  21  comprises a plurality of rotor blades  23  which are arranged in slots (not shown) on the rotor surface  24 . Arranged between the rotor blades  23  are stator blades  25  which are retained on a casing (not shown). A first stator blade row  26  is designed in such a way that this stator blade row  26  supports a shield  27 . The shield  27  is designed in such a way that during operation steam which flows into the inlet region  20  can be deflected into a flow passage  28 . Since the intermediate-pressure turbine section  12  shown in  FIG. 2  has a first flow  29  and a second flow  30 , the flow passage  28  is divided into a first flow passage  31  and a second flow passage  32 . The inflowing steam  33  is therefore deflected forming a first steam  34  and a second steam  35 . The first steam  34  flows into the first flow passage  31 . The second steam  35  flows into the second flow passage  32 . 
         [0032]    The intermediate-pressure turbine section  12  comprises a casing (not shown) which is arranged around the rotor  21 , wherein the first flow passage  31  and the second flow passage  32  are formed between the rotor  21  and the casing, wherein the first flow passage  31  and the second flow passage  32  are fluidically connected to the inflow region  20 . 
         [0033]    A flow medium which in addition to steam can be ammonia or a steam-CO 2  mixture is to be understood by the term steam. 
         [0034]    The shield  27  has a cooling medium feed  36  which is designed in such a way that during operation cooling steam flows into a cooling region  37  which is arranged between the shield  27  and the rotor  21 . Used as cooling steam is steam from the cooling medium line  9  which comes from the cold reheat line  8 . Other cooling steam can be used in alternative embodiments. The cooling steam therefore flows out the cooling medium feed  36  onto the rotor surface  24  and cools a thermally stressed region which is represented by means of a parabolic gray area  38 . The temperature is represented in shades of gray. As is to be seen in  FIG. 2 , the shade of gray in the parabolic gray area  38  is a little darker than the shades of gray of the rotor  21 . This means that the temperature in the parabolic gray area  38  is higher than the temperature of the rotor  21 . 
         [0035]    In addition to the cooling medium feed  36 , a line  39  is now arranged according to the invention in the shield  27 . This line  39  creates a fluidic connection between the cooling region  37  and the inlet region  20 . The line  39  can be constructed as a hole or as a plurality of holes. These holes can be constructed in a distributed manner on the circumference. The line  39  can be arranged symmetrically to the parabolic gray area  38 , which means that the line  39  is arranged in the direction of a central inflow direction  40 . In  FIG. 2 , the line  39  is not shown in the same direction as the central inflow direction  40  but shown a small distance further to the right. 
         [0036]      FIG. 3  shows in the main the same arrangement as in  FIG. 2 . A repeat of the description and principle of operation of the components is therefore dispensed with. The difference in the view of  FIG. 3  lies in the fact that a failure of the cooling medium feed  36  is symbolized by a cross. The failure of the cooling medium feed  36  leads to a heating up of the cooling region  37 . This leads to a change of the temperature in the parabolic gray area  38 . In  FIG. 3 , it is to be seen that the shades of gray are darker compared with the gray area in  FIG. 2 . This means that the temperature is increased compared with the normal operation which is to be seen in  FIG. 2 . Nevertheless, the temperature difference between the normal operation, as is to be seen in  FIG. 2 , and the failure operation which is shown in  FIG. 3 , is moderate. This means that the material of the rotor  21  experiences a comparatively small temperature jump. 
         [0037]      FIG. 4  shows a side view of the arrangement according to the invention. The cooling medium feed  36  in a first embodiment is designed in the radial direction  41  toward the rotational axis. This means that during operation the cooling steam impinges radially upon the rotor  21 . Similarly, the line  39  according to  FIG. 4  is designed in such a way that during operation steam from the inlet region impinges radially upon the rotor  21 . 
         [0038]      FIG. 5  shows an alternative embodiment to the embodiment according to  FIG. 4 .  FIG. 5  shows that the cooling medium feed  36  is designed in such a way that during operation the cooling steam impinges tangentially upon the rotor  21 . To this end, the cooling medium feed  36  is basically constructed in such a way that the shield has a hole through which the steam can impinge tangentially upon the rotor  21 . This leads to a swirl of the steam which is present in the cooling region  37 . The line  39  is similarly designed in an alternative embodiment in such a way that during operation steam from the inlet region  20  impinges tangentially upon the rotor  21 . This leads to a better mixing in the cooling region  37 . 
         [0039]    Although the invention has been fully illustrated and described in detail by means of the preferred exemplary embodiment, the invention is not thus limited by the disclosed examples, and other variations can be derived by the person skilled in the art without departing from the extent of protection of the invention.

Technology Category: f