Patent Publication Number: US-2016230771-A1

Title: Geared Turbomachine

Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The invention relates to a geared turbomachine. 
     2. Description of the Related Art 
     EP 2 128 448 A2 discloses a geared turbomachine with a gear unit, a drive unit, and multiple output units. These components of the geared turbomachine are integrated into a machine train. The gear unit comprises a central large gear with a large gear shaft. Multiple pinions mounted on pinion shafts mesh with the large gear. The drive unit is preferentially a steam turbine. The output units are preferentially compressors, namely a main compressor and multiple geared compressors. According to EP 2 128 448 A2 the drive unit is coupled to a first pinion shaft of the gear unit via a first clutch, whereas the output unit that is designed the as main compressor is coupled to a second pinion shaft of the gear unit via a second clutch, so that the drive unit and the first output unit, which is designed as main compressor, are operationally connected to one another via a transmission stage of the gear unit (rotational speed step-down power gear). The optimal design of such known machine trains from the prior art according to EP 2 128 448 A2 is substantially effected in that the drive and output units are operated in the optimal working range and adaptation with respect to the rotational speeds largely takes place via the transmission ratio in the power gear. 
     SUMMARY OF THE INVENTION 
     There is a need for a geared turbomachine that can be operated more effectively and consequently with reduced losses. There is furthermore a need in reducing the installation space requirement of such a geared turbomachine to be able to position the geared turbomachine in smaller-dimensioned buildings with reduced construction height. 
     An object of the invention is creating a new type of geared turbomachine. The geared turbomachine according to one embodiment of the invention comprises a gear unit, a drive unit, and multiple output units integrated into a machine train. The gear unit comprises a central large gear with a large gear shaft and at least two pinions with respective pinion shaft meshing with the large gear. The drive unit can be preferentially designed as a steam turbine in which for power steam is expanded to provide mechanical drive. The drive unit is coupled to a first pinion shaft of the gear unit on a side of the gear unit via a first clutch. A first output unit is designed as a main compressor, in which, utilising mechanical drive power provided by the drive unit, a first process gas is compressed. The first drive unit is coupled to the first pinion shaft of the gear unit on the opposite side of the same via a second clutch such that the first output unit with a closed first clutch and a closed second clutch is directly operationally connected to the drive unit with transmission remaining the same (i.e. without a transmission stage) of the gear unit. At least one second output unit is designed as geared compressor in which, utilising mechanical drive power provided by the drive unit, the first or at least one further process gas is compressed. The second output unit is connected in a rotationally fixed manner to a further pinion shaft of the gear unit. 
     Such a geared turbomachine, in which the drive unit that is preferentially designed as steam turbine is coupled to the first output unit designed as a main compressor directly without a transmission stage of the gear unit of the geared turbomachine, can be operated with higher efficiency or with lower losses than is the case with machine trains known from the prior art. 
     During the course of the considerations regarding a new concept for a machine train with geared turbomachine and drive and output units it has been established that according to the arrangement principles up to now the optimum for the entire machine train is not achieved for each case of application, in particular with respect to costs and installation space. 
     In particular through investigations of the gear unit configuration that by omitting a power gear between the drive unit and output unit the gear friction losses and the costs for the gear unit can be significantly reduced and the overall efficiency of the machine train is thus substantially influenced. 
     Starting out from the objective of minimizing costs, maintaining the compression performance, and also keeping the overall efficiency at least the same, it has unexpectedly been established that a drive unit that is specially designed for the overall process is thus not mandatorily required for achieving the mentioned targets and accordingly the drive unit can be selected less dependent on its rotational speed-optimised working range. 
     According to one embodiment, the main compressor is designed as radial compressor (preferentially at least two stages), wherein downstream of the front compressor stages, but not the last compressor stage, an intercooler is generally connected to reduce the volume and the temperature of the compressing first process gas. The configuration of the main compressor as radial compressor with intercooling after or between the compressor stages of the radial compressor is advantageous for increasing the efficiency and for reducing the installation space requirement of the geared turbomachine. 
     According to one embodiment, the main compressor is designed as an axial compressor with at least one radial final stage, wherein downstream after the axial stages and before entering the radial final stage intercooling is connected. 
     Optionally, an axial compressor with two radial final stages is also possible; in this case intercooling between the two radial stages is also possible. 
     According to one embodiment, the drive unit, which is designed as steam turbine, comprises an axial exhaust steam casing, wherein a condenser of the drive unit designed as steam turbine is positioned on separate supports seen in the direction of a longitudinal axis of the steam turbine next to a foundation table supporting the steam turbine. Through this configuration it is not necessary to position the condenser below the foundation table. The condenser is rather arranged next to the foundation table on separate supports. This is advantageous in particular for reducing the installation space requirement since by doing so the height of the foundation table can be reduced for example from up to approximately 12 m to approximately 4 m and the construction height of the entire geared turbomachine thereby reduced. Furthermore it is thus possible to embody the machine foundation thinner or lighter. 
     According to one embodiment, the geared turbomachine comprises two to eight second output units designed as geared compressors. When the geared turbomachine comprises two geared compressors the same are connected to the second pinion shaft in a rotationally fixed manner. When the geared turbomachine comprises three or four geared compressors, the same are connected to a further pinion shaft in a rotationally fixed manner, wherein in particular when the geared turbomachine comprises five or six geared compressors, the same are connected to yet a further pinion shaft in a rotationally fixed manner, and in particular when the geared turbomachine comprises seven or eight geared compressors, the same are yet gain connected to a further pinion shaft in a rotationally fixed manner. By way of the selection of a suitable number of geared compressors the efficiency can be further increased. 
     Other objects and features of the present invention will become apparent from the following detailed description considered in conjunction with the accompanying drawings. It is to be understood, however, that the drawings are designed solely for purposes of illustration and not as a definition of the limits of the invention, for which reference should be made to the appended claims. It should be further understood that the drawings are not necessarily drawn to scale and that, unless otherwise indicated, they are merely intended to conceptually illustrate the structures and procedures described herein. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Preferred further developments of the invention are obtained from the subclaims and the following description. Exemplary embodiments of the invention are explained in more detail with the help of the drawing without being restricted to this. It shows: 
         FIG. 1 a    is a block diagram of a first geared turbomachine according to the invention; 
         FIG. 1 b    is a schematic, perspective view of a gear unit of the geared turbomachine according to  FIG. 1   a;    
         FIG. 2 a    is a block diagram of a second geared turbomachine according to the invention; 
         FIG. 2 b    is a schematic, perspective view of a gear unit of the geared turbomachine according  FIG. 2   a;    
         FIG. 3 a    is a block diagram of a third geared turbomachine according to the invention; 
         FIG. 3 b    is a schematic, perspective view of a gear unit of the geared turbomachine according  FIG. 3   a;    
         FIG. 4 a    is a block diagram of a fourth geared turbomachine according to the invention; 
         FIG. 4 b    is a schematic, perspective view of a gear unit of the geared turbomachine according  FIG. 4   a;    
         FIG. 5 a    is a block diagram of a fifth geared turbomachine according to the invention; 
         FIG. 5 b    is a schematic, perspective view of a gear unit of the geared turbomachine according  FIG. 5   a;    
         FIG. 6 a    is a block diagram of a sixth geared turbomachine according to the invention; 
         FIG. 6 b    is a schematic, perspective view of a gear unit of the geared turbomachine according  FIG. 6   a.    
         FIG. 7 a    is a block diagram of a seventh geared turbomachine according to the invention; 
         FIG. 7 b    is a schematic, perspective view of a gear unit of the geared turbomachine according  FIG. 7   a;    
         FIG. 8 a    is a block diagram of a eight geared turbomachine according to the invention; and 
         FIG. 8 b    is a schematic, perspective view of a gear unit of the geared turbomachine according  FIG. 8   a.    
     
    
    
     DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS 
       FIGS. 3 a  and 3 b    show a preferred exemplary embodiment of a geared turbomachine  10  according to one embodiment the invention. The geared turbomachine  10  comprises an integrated gear unit  11 , a drive unit  12 , multiple output units  13 ,  14 ,  15 , and  16 , wherein the gear unit  11 , the drive unit  12  and the multiple output units  13 ,  14 ,  15 , and  16  are integrated into a machine train. 
     The gear unit  11  of the geared turbomachine  10  comprises a large gear  17 , which is positioned on a large gear shaft  18  and via the large gear shaft  18  is rotatably mounted in a gear unit housing  19  of the gear unit  11 . Multiple pinions  21 ,  23 ,  25  mesh with the large gear  17  of the gear unit  11  on the circumference of the large gear  17 , which pinions are fastened on pinion shafts  22 ,  24 ,  26  and via the pinion shafts  22 ,  24  and  26  are likewise rotatably mounted in the gear unit housing  19 . 
     In the exemplary embodiment of  FIGS. 3 a  and 3 b   , a total of three such pinions  21 ,  23 , and  25  mounted on pinion shafts  22 ,  24 , and  26  mesh with the large gear  17  on the circumference of the large gear  17 . 
     The drive unit  12  is designed as steam turbine, in which steam is expanded for providing mechanical drive power. The drive unit  12  is coupled to a first pinion shaft  22  of the gear unit  11 , namely on a first side  27  of the gear unit  11  or of the gear unit housing  19 , wherein the drive unit  12  which is designed as steam turbine is coupled to the first pinion shaft  22  via a first clutch  29 . 
     The multiple drive units  13 ,  14 ,  15 , and  16  include a first output unit  13  designed as main compressor and multiple second output units  14 ,  15 , and  16  designed as geared compressors. The main compressor or the first output unit  13  is designed in at least two stages wherein in the main compressor a first process gas is compressed utilizing the mechanical drive power provided by the drive unit  12 . 
     The first output unit  13  or the main compressor is coupled to the first pinion shaft  22  of the gear unit  11 , namely on a second side  28  of the gear unit  11  or gear unit housing  19  located opposite the first side  27 . Here, the first output unit  13 , which is designed as a main compressor, acts via a second clutch  30  on the first pinion shaft  22 , to which the drive unit  12  is also coupled via the first clutch  29 . 
     In particular when the first clutch  29  and the second clutch  30  are both closed, the drive unit  12  and the first output unit  13 , designed as main compressor, are directly operationally connected to one another with transmission remaining the same and without intermediate connection of a transmission stage of the gear unit  11 , so that the same rotate with the same rotational speed. 
     In addition to the drive unit  12  and the first output unit  13  designed as main compressor, the geared turbomachine  10  of  FIG. 3 a    comprises three second output units  14 ,  15 , and  16 , which are designed as geared compressors. In the second output units  14 ,  15 , and  16  designed as geared compressors, the first process gas and/or one or multiple further process gases is/are compressed or further compressed utilising the mechanical drive power provided by the drive unit  12 , wherein the second output units  14 ,  15 , and  16  are connected to further pinion shafts  24 ,  26  of the gear unit  11  in a rotationally fixed manner. 
     Accordingly, the three further second output units  14 ,  15 , and  16  are connected, in the exemplary embodiment of  FIGS. 3 a  and 3 b   , to two further pinion shafts  24  and  26  in a rotationally fixed manner namely in such a manner that the two geared compressors  14  and  15  are connected to a second pinion shaft  24  of the gear unit  11  in a rotationally fixed manner on opposite sides  27  and  28  of the gear unit  11  or gear unit housing  19 , whereas the geared compressor  16  is connected to a third pinion shaft  26  of the gear unit  11  in a rotationally fixed manner, preferentially in the region of that side  28  of the gear unit housing  19 , on which the geared compressor  14  and the main compressor  13  are also positioned. 
     Of the total power of the machine train, at least 50% is accounted for by the main compressor and the rest (less than 50%) by the geared compressor that makes it clear that the rotational speed-optimised design in particular of the main compressor and of the drive unit  12  is of great important for increasing the effectiveness of the machine train. 
     In the exemplary embodiment of  FIGS. 3 and 3   b , the first pinion shaft  22  is positioned approximately in the 6 o&#39;clock position of the large gear  17  and via the pinion  21  meshes with the large gear  17  in this position. The second pinion shaft  24  with the pinion  23  is positioned approximately in the 3 o&#39;clock position and the third pinion shaft  26  with the pinion  25  is positioned approximately in the 9 o&#39;clock position of the large gear  17 , these pinions  23  and  25  meshing with the large gear  17  in these positions. 
     As shown in  FIG. 3 a   , an optional generator  31  or alternatively a motor can be coupled to the large gear shaft  18  of the gear unit  11 , namely via a clutch  32 . 
     As already explained, the first output unit  13  designed as main compressor can be designed in multiple stages with multiple compressor stages. 
     Downstream of the front compressor stage  13   a  an intercooler  13   b  is positioned to cool the already compressed fluid, first process gas and by doing so reduce the volume and the temperature of the same. The efficiency of the geared turbomachine can thereby be improved, in particular with a view to further processing the first process gas in the region of the geared compressors  14 ,  15 , or  16 . 
     It is preferentially possible to position an intercooler like  13   b  for cooling down the respective compressed process gas also downstream of each geared compressor  14 ,  15 , and  16 . 
     The gear unit  11  together with the geared compressors  14 ,  15 , and  16 , the drive unit  12  designed as steam turbine and the first output unit  13  designed as main compressor are preferentially mounted on a common foundation table  20  of a machine foundation. 
     In the region of the steam turbine or of the drive unit  12 , an axial exhaust steam casing  33  is employed so that expanded medium leaves the steam turbine  12  in axial direction. 
     A condenser  34  positioned downstream of the steam turbine  12 , seen in the direction of a longitudinal axis of the steam turbine  12 , is then preferentially positioned next to the foundation table of the machine foundation supporting the steam turbine  12 , namely preferentially on separate supports  35 . 
     The geared turbomachine  10  shown in  FIGS. 3 a  and 3 b    accordingly comprises the integrated gear unit  11 , the drive unit  12  designed as steam turbine, the first output unit  13  designed as main compressor and at least three second output units  14 ,  15 , and  16  designed as geared compressors. According to one embodiment of the invention, the steam turbine  12  and the at least two-stage main compressor  13  are coupled via corresponding clutches  29 ,  30  to the same pinion shaft  22  of the gear unit  11  so that in particular when the two clutches  29  and  30  are coupled, steam turbine  12  and main compressor  13  without gearing of the gear unit  11  are directly operationally connected with transmission remaining the same and operated with the same rotational speed. Following the passing through of other process steps outside the machine train, the geared compressors  14 ,  15 , and  16  generally serve for the further processing of the process gas compressed in the main compressor  13  and/or for compressing at least one further process gas. The pinion  21  mounted on the first pinion shaft  22  has to transmit the full power of the geared turbomachine  10  or the full drive power of the steam turbine  12 . The steam turbine  12  comprises an axial outflow or exhaust steam casing  33 , wherein the condenser  34  is positioned next to the foundation table  20  on separate supports  35 . 
     The main compressor  13  is preferably embodied at least in two stages, preferentially as a radial compressor. In the two-stage radial compressor intercoolers are integrated after the front stages. In the geared compressors  14 ,  15 , and  16 , the process gas compressed in the main compressor  13  and/or at least one further process gas is/are compressed or further compressed. Downstream of each geared compressor  14 ,  15 ,  16 , a further intercooler can be preferentially positioned. 
     The geared turbomachine  10  is preferentially driven via the drive unit  12  designed as steam turbine drives the main compressor  13  directly or indirectly with the same rotational speed through the housing  19  of the gear unit  11 . The geared compressors  14 ,  15 , and  16  are likewise driven starting out from the steam turbine  12  or from the drive unit, however with different rotational speeds and namely with an optimal rotational speed for the respective geared compressor that is dependent on the specific transmission ratio of the gear unit  11 . 
     Further exemplary embodiments of the geared turbomachine  10  according to the invention are shown by  FIG. 1 a , 1 b   ,  FIG. 2 a , 2 b   ,  FIG. 4 a , 4 b   ,  FIG. 5 a , 5 b   ,  FIG. 6 a , 6 b   ,  FIG. 7 a , 7 b   , and  FIG. 8 a , 8 b   , wherein in the following only details by which the further geared turbomachines  10  according to the invention differ from the geared turbomachine  10  of  FIG. 3 a , 3 b    are discussed. 
     With the geared turbomachine  10  of  FIG. 1 a , 1 b    only one geared compressor  14  is present, which is connected to a pinion shaft  24  in a rotationally fixed manner. 
     With the geared turbomachine  10  of  FIG. 2 a , 2 b    a total of two geared compressors  14 ,  15  are present, which are connected to the pinion shaft  24  in a rotationally fixed manner. Accordingly, the two geared compressors  14  and  15  are connected to the second pinion shaft  24  of the gear unit  11  in a rotationally fixed manner on different sides of the gear unit housing  10 . 
     With the geared turbomachine  10  of  FIG. 4 a , 4 b   , a total of four geared compressors  14 ,  15 ,  16 , and  36  are present, which are connected to two pinion shafts  24  and  26  in a rotationally fixed manner. Accordingly, the two geared compressors  14  and  15  are connected to the second pinion shaft  24  on different sides of the gear unit housing  10  and the two geared compressors  16 ,  36  are connected to the third pinion shaft  26  of the gear unit  11  on different sides of the gear unit housing  10  in a rotationally fixed manner. 
     In the exemplary embodiment of  FIGS. 5 and 5   b  and  FIGS. 6 a  and 6 b    the gear unit  11  of the geared turbomachine  10  each comprises a fourth pinion shaft  39 , with which in the exemplary embodiment of  FIG. 5 a , 5 b    a fifth geared compressor  37  and in the exemplary embodiment of  FIG. 6 a , 6 b    additionally a sixth geared compressor  40  is connected in a rotationally fixed manner. The fourth pinion shaft  39  in this case is arranged together with the pinion mounted on the same approximately in the 12 o&#39;clock position of the large gear  17 , wherein the pinion  38  mounted on the fourth pinion shaft  39  meshes with the large gear  17  on this position on the circumference of the same. 
     Two further exemplary embodiments of geared turbomachines  10  are shown by  FIG. 7 a , 7 b    and  FIG. 8 a , 8 b   , wherein in  FIG. 7 a , 7 b    and  FIG. 8 a , 8 b    a fifth pinion shaft  43  each is present. In the exemplary embodiment of  FIG. 7 a , 7 b   , a seventh geared compressor  41  is connected to this fifth pinion shaft  43  in a rotationally fixed manner, wherein in  FIG. 8 a , 8 b    the seventh geared compressor  41  and additionally an eighth geared compressor  44  is connected to the fifth pinion shaft  43  in a rotationally fixed manner. As is evident from  FIG. 7 b , 7 b   , the fourth pinion shafts  39  in these exemplary embodiments is arranged approximately in the 1 o&#39;clock position and the fifth pinion shafts  43  approximately in the 11 o&#39;clock position of the large gear  17 , wherein the corresponding pinions  38 ,  42  mesh with the large gear  17  in these positions on the circumference of the same. 
     Independently of the aforementioned embodiment versions it is possible that the first pinion shaft  22  meshes with the large gear via the pinion approximately in the 6 o&#39;clock position or approximately in the 9 o&#39;clock position or approximately in the 11 o&#39;clock position or approximately in the 12 o&#39;clock position or approximately in the 1 o&#39;clock clock position or approximately in the 3 o&#39;clock position of the large gear and that the at least one further pinion shaft  24 ,  26 ,  39 ,  43  meshes with the large gear in at least one of the free positions of the large gear via the respective pinions. 
     In addition to the aforementioned embodiment versions it is optionally also possible that in each case between the pinion shafts  22 ,  24 ,  26 ,  39 ,  43  and the large gear  17  at least one intermediate gear with intermediate gear shaft each which is not shown is arranged and connected to the pinion shafts  22 ,  24 ,  26 ,  39 ,  43  and the large gear  17  in a rotationally fixed manner. 
     In particular areas of application of geared turbomachines it can also be that instead of at least one of the second drive units  14 ,  15 ,  16 ,  36 ,  37   40 ,  41   44  at least one further drive unit  14 ′,  15 ′,  16 ′,  36 ′,  37 ′,  40 ′,  41 ′,  44 ′ is connected to one of the pinion shafts  24 ,  26 ,  39 ,  43  in a rotationally fixed manner. The further drive unit could be an expander, a motor or even a gas or steam turbine. 
     In addition, for running up the geared turbomachine the generator/motor  31  can initially function as drive unit and only following the running up of the motor/generator  31  function as output unit in generator mode. 
     Under special circumstances it can also be possible that the drive unit is embodied as a gas turbine, expander or motor. 
     Thus, while there have shown and described and pointed out fundamental novel features of the invention as applied to a preferred embodiment thereof, it will be understood that various omissions and substitutions and changes in the form and details of the devices illustrated, and in their operation, may be made by those skilled in the art without departing from the spirit of the invention. For example, it is expressly intended that all combinations of those elements and/or method steps which perform substantially the same function in substantially the same way to achieve the same results are within the scope of the invention. Moreover, it should be recognized that structures and/or elements and/or method steps shown and/or described in connection with any disclosed form or embodiment of the invention may be incorporated in any other disclosed or described or suggested form or embodiment as a general matter of design choice. It is the intention, therefore, to be limited only as indicated by the scope of the claims appended hereto.