Patent Publication Number: US-10760452-B2

Title: Condenser and steam turbine plant provided with same

Description:
TECHNICAL FIELD 
     The present invention relates to a condenser configured to condense steam exhausted from a steam turbine, and a steam turbine plant including the same. 
     Priority is claimed on Japanese Patent Application No. 2016-034231, filed Feb. 25, 2016, and PCT International Application No. PCT/JP2016/072623, filed Aug. 2, 2016, the contents of which are incorporated herein by reference. 
     BACKGROUND ART 
     A steam turbine plant includes a steam turbine driven by steam, and a condenser configured to condense the steam exhausted from the steam turbine and return the steam into water. 
     As such a steam turbine plant, for example, a steam turbine plant is disclosed in the following Patent Literature 1. The steam turbine plant includes an axial-flow exhaust type steam turbine, and a condenser configured to return steam exhausted from the steam turbine into water. The condenser includes a plurality of heat transfer pipe groups, a main body configured to cover the plurality of heat transfer pipe groups, and an intermediate body configured to guide steam from the steam turbine into the main body. 
     The intermediate body is formed in a tubular shape using a virtual axis that is substantially horizontal as a center. An intermediate body inlet is formed on one end of the intermediate body having a tubular shape, and an intermediate body outlet is formed on the other end. The steam from the steam turbine flows into the intermediate body from the intermediate body inlet. The main body has a bottom plate, a plurality of side plates extending upward from an edge of the bottom plate, and a top plate. A main body inlet is formed in the side plate of the main body on the side of the steam turbine. Steam from the intermediate body flows into the main body from the main body inlet. In other words, steam flows into the main body from a substantially horizontal direction. A plurality of heat transfer pipe groups arranged in a horizontal direction and a plurality of heat transfer pipe groups arranged in a vertical direction are disposed in the main body. 
     CITATION LIST 
     Patent Literature 
     [Patent Literature 1] 
     Japanese Unexamined Patent Application, First Publication No. H09-273875 
     SUMMARY OF INVENTION 
     Technical Problem 
     As described above, the condenser disclosed in Patent Literature 1 has the plurality of heat transfer pipe groups arranged in the vertical direction. For this reason, a cooling water pump configured to supply cooling water to a plurality of heat transfer pipes that constitute the heat transfer pipe groups is required to have a capability of supplying the cooling water to the heat transfer pipe disposed on the uppermost section in the heat transfer pipe group located furthest upward. Accordingly, in the technology disclosed in Patent Literature 1, a cooling water pump having a high pumping head is required, and thus initial cost and running cost increase. 
     Here, the present invention is directed to providing a condenser capable of reducing initial cost and running cost, and a steam turbine plant including the same. 
     Solution to Problem 
     In order to accomplish the above-mentioned object, a condenser of a first aspect of the present invention includes: a plurality of heat transfer pipe groups constituted by a plurality of heat transfer pipes through which cooling water that exchanges heat with steam passes; a main body configured to cover the plurality of heat transfer pipe groups; and an intermediate body connected to the main body and configured to guide steam into the main body. The intermediate body has an intermediate body inlet that opens from the inside in a horizontal direction and into which steam flows, an intermediate body outlet that opens downward from the inside and through which steam is exhausted, and a flow path configured to connect the intermediate body inlet and the intermediate body outlet and cause the steam flowing in from the intermediate body inlet to be directed gradually downward as it flows away from the intermediate body inlet in the horizontal direction to reach the intermediate body outlet. The main body has a main body inlet that opens upward from the inside and is connected to the intermediate body outlet, and into which the steam from the intermediate body flows. The plurality of heat transfer pipe groups are arranged in the horizontal direction and disposed in the main body. A near-side outlet edge that is an edge of the intermediate body outlet on a side near the intermediate body inlet in the horizontal direction is disposed below the uppermost position among the plurality of heat transfer pipe groups. 
     In the condenser, since the plurality of heat transfer pipe groups are arranged in the horizontal direction and disposed in the main body, a level difference between the uppermost position among the plurality of heat transfer pipe groups and a water source of the cooling water supplied to the heat transfer pipe group can be reduced. Accordingly, in the condenser, a pumping head of a cooling water pump configured to supply the cooling water from the water source to the heat transfer pipe can be reduced. For this reason, the condenser can reduce installation cost and running cost of the cooling water pump. 
     Further, in the condenser, the near-side outlet edge of the intermediate body outlet is disposed below the uppermost position among the plurality of heat transfer pipe groups. For this reason, in the condenser, an installation position of the steam turbine connected to the condenser can be lowered. Accordingly, in the condenser, installation cost of the steam turbine can be reduced. 
     According to a condenser of a second aspect, in the condenser of the first aspect, a near-side inner surface including the near-side outlet edge that is an inner surface of the intermediate body that forms the flow path of the intermediate body is a surface directed toward the side near the intermediate body inlet while being directed upward from the near-side outlet edge. 
     In the condenser, a flow path area of the flow path on the side of the intermediate body outlet in the flow path of the intermediate body can be increased. For this reason, in the condenser, it is considered possible to reduce an average flow speed of the steam flowing into the heat transfer pipe group and provide a certain effect of suppressing erosion in the heat transfer pipe. 
     According to a condenser of a third aspect, in the condenser of the first or second aspect, a far-side outlet edge that is an edge of the intermediate body outlet on a side far from the intermediate body inlet in the horizontal direction is disposed above the uppermost position among the plurality of heat transfer pipe groups. 
     In the condenser, the intermediate body outlet edge is inclined from the far-side outlet edge toward the near-side outlet edge. Accordingly, in the condenser, an opening area of the intermediate body outlet can be increased. For this reason, in the condenser, it is considered possible to reduce an average flow speed of the steam flowing into the heat transfer pipe group and provide a certain effect of suppressing erosion in the heat transfer pipe. 
     In addition, according to a condenser of a fourth aspect, in the condenser according to any one of the first to third aspects, the plurality of heat transfer pipe groups are disposed at positions below a lower end of the intermediate body inlet in the main body. 
     In the condenser, since the steam that flows straight from the steam turbine in the horizontal direction does not directly flow into the heat transfer pipe group, a certain effect of suppressing erosion in the heat transfer pipe is considered to be provided. 
     In addition, according to a condenser of a fifth aspect, in the condenser according to any one of the first to fourth aspects, a dimension in a vertical direction of a pipe group outline formed by virtual surfaces that circumscribe the plurality of heat transfer pipes disposed on the outermost side among the plurality of heat transfer pipes that constitute the heat transfer pipe group is larger than a dimension of the pipe group outline in the horizontal direction. 
     In the condenser, the bottom surface of the pipe group outline can be reduced. For this reason, in the condenser, even when the plurality of heat transfer pipe groups are disposed to be arranged in the main body in the horizontal direction, an increase in occupation area of the condenser can be minimized. 
     According to a condenser of a sixth aspect, in the condenser of the fifth aspect, the pipe group outline has an upper surface directed upward and a bottom surface directed downward, and an upper section including the upper surface in the pipe group outline has a cross-sectional area in the horizontal direction that is gradually increased downward. 
     The steam passing through the intermediate body flows into the main body from the main body inlet. The steam flows mainly downward through the main body. The steam exchanges heat with the cooling water flowing through the plurality of heat transfer pipes that constitute each of the heat transfer pipe groups while flowing through the main body. 
     When the steam flows downward through the main body, as an area of the upper surface of the pipe group outline facing the flow is increased, the efficiency of heat exchange between the steam and the cooling water in the heat transfer pipes that constitute the heat transfer pipe group is increased. In the condenser, since a part of the upper surface of the pipe group outline is an inclined surface, an area of the upper surface can be increased more than when the entire upper surface is a horizontal surface. Accordingly, in the condenser, the efficiency of heat exchange between the steam and the cooling water in the heat transfer pipes that constitute the heat transfer pipe group can be increased more than when the entire upper surface of the pipe group outline is a horizontal surface. 
     According to a condenser of a seventh aspect, in the condenser of the sixth aspect, the pipe group outline of at least one of the heat transfer pipe groups is an eccentric outline in which a center of a top surface at the uppermost position in the upper surface is disposed closer to the intermediate body inlet in the horizontal direction than a center of the bottom surface in the same pipe group outline. 
     In the condenser, even when a ratio of the horizontal component in the flow direction component of the steam flowing into one of the heat transfer pipe groups is large, the efficiency of heat exchange between the steam and the cooling water in the heat transfer pipes that constitute one of the heat transfer pipe groups can be increased. 
     According to a condenser of an eighth aspect, in the condenser of the seventh aspect, the plurality of heat transfer pipe groups are arranged in a far side-near side direction with respect to the intermediate body inlet that is the horizontal direction, and the pipe group outline of the heat transfer pipe group closest to the intermediate body inlet in the far side-near side direction among the plurality of heat transfer pipe groups is the eccentric outline. 
     A flow direction component of the steam flowing into the heat transfer pipe group closest to the intermediate body inlet in the far side-near side direction has a ratio of the horizontal component that is larger than that of the flow direction component of the steam flowing into another heat transfer pipe group. Accordingly, since the pipe group outline of the heat transfer pipe group closest to the intermediate body inlet in the far side-near side direction has an eccentric outline, the efficiency of heat exchange with the cooling water in the heat transfer pipes that constitute the heat transfer pipe group can be increased. 
     According to a condenser of a ninth aspect, the condenser of the fifth or sixth aspect further includes a steam guide disposed in the intermediate body and causing a direction of a flow of the steam flowing in from the intermediate body inlet to be directed gradually downward. 
     In the condenser, a downward component in the flow direction component of the steam flowing into the plurality of heat transfer pipe groups can be increased. For this reason, in the condenser, the efficiency of heat exchange between the steam and the cooling water in the heat transfer pipes that constitute the heat transfer pipe groups can be increased. 
     In order to accomplish the above-mentioned object, a steam turbine plant of a tenth aspect according to the present invention includes the condenser according to any one of the first to ninth aspects, and a steam turbine configured to exhaust the steam into the condenser. 
     According to a steam turbine plant of an eleventh aspect, in the steam turbine plant of the tenth aspect, the steam turbine is an axial-flow exhaust type steam turbine. 
     According to a steam turbine plant of a twelfth aspect, in the steam turbine plant of the tenth aspect, the steam turbine is a lateral exhaust type steam turbine. 
     Advantageous Effects of Invention 
     According to an aspect of the present invention, it is possible to reduce initial cost and running cost of a steam turbine plant. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG. 1  is a system diagram of a steam turbine plant according to a first embodiment of the present invention. 
         FIG. 2  is a schematic cross-sectional view of a steam turbine and a condenser according to the first embodiment of the present invention. 
         FIG. 3  is a view explaining a difference in configuration between the condenser according to the first embodiment of the present invention and a condenser of a comparative example. 
         FIG. 4  is a schematic cross-sectional view of a steam turbine and a condenser according to a second embodiment of the present invention. 
         FIG. 5  is a schematic cross-sectional view of a condenser according to a first variant of the present invention. 
         FIG. 6  is a schematic cross-sectional view of a condenser according to a second variant of the present invention. 
         FIG. 7  is a schematic cross-sectional view of a condenser according to a third variant of the present invention. 
         FIG. 8  is a schematic cross-sectional view of a condenser according to a fourth variant of the present invention. 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     Hereinafter, various embodiments and various variants of a steam turbine plant according to the present invention will be described with reference to the accompanying drawings. 
     First Embodiment 
     A first embodiment of the steam turbine plant according to the present invention will be described with reference to  FIGS. 1 to 3 . 
     As shown in  FIG. 1 , the steam turbine plant of the embodiment includes a steam generator  17  such as a boiler, a steam turbine  20  driven by steam generated in the steam generator  17 , a generator  19  configured to generate power through driving of the steam turbine  20 , a condenser  30  configured to condense steam S exhausted from the steam turbine  20 , a water-feeding pump  15  configured to return water in the condenser  30  to the steam generator  17 , and a cooling water pump  11  configured to supply cooling water for cooling steam to the condenser  30 . 
     The steam generator  17  and the steam turbine  20  are connected by a main steam line  18 . The steam generated in the steam generator  17  is supplied to the steam turbine  20  via the main steam line  18 . The condenser  30  and the steam generator  17  are connected by a water-feeding line  16 . The water-feeding pump  15  is installed on the water-feeding line  16 . Water returned to liquid from the steam S in the condenser  30  is supplied to the steam generator  17  via the water-feeding line  16 . 
     The steam turbine  20  has a rotor  21  that rotates about a turbine axis At, a main body casing  22  configured to cover the rotor  21 , and an exhaust casing  25  configured to exhaust steam from the main body casing  22 . The turbine axis At extends in a substantially horizontal direction. Further, hereinafter, a direction in which the turbine axis At extends is referred to as an axial direction Da, one side in the axial direction Da is referred to as an axial upstream side Dau, and the other side is referred to as an axial downstream side Dad. 
     The rotor  21  of the steam turbine  20  is connected to a rotor of the generator  19 . The main body casing  22  and the exhaust casing  25  are formed in a tubular shape around the turbine axis At. A steam inlet  23  is formed on the axial upstream side Dau of the main body casing  22  having a tubular shape. In addition, a steam outlet  24  is formed on an end on the axial downstream side Dad of the main body casing  22 . The steam outlet  24  opens toward the axial downstream side Dad from the inside of the main body casing  22 . An exhaust steam inlet  26  is formed on an end on the axial upstream side Dau of the exhaust casing  25 . The exhaust steam inlet  26  opens toward the axial upstream side Dau from the inside of the exhaust casing  25 . The exhaust steam inlet  26  is connected to the steam outlet  24  of the main body casing  22 . An exhaust steam outlet  27  is formed on an end on the axial downstream side Dad of the exhaust casing  25 . The exhaust steam outlet  27  opens toward the axial downstream side Dad from the inside of the exhaust casing  25 . Accordingly, the steam turbine  20  is an axial-flow exhaust type configured to exhaust the steam in the axial direction Da. 
     As shown in  FIG. 2 , the condenser  30  includes a plurality of heat transfer pipe groups  41 , a main body  35  configured to cover the plurality of heat transfer pipe groups  41 , and an intermediate body  31  configured to guide the steam S from the steam turbine  20  into the main body  35 . 
     The intermediate body  31  has an intermediate body inlet  32  that opens in the horizontal direction from the inside and into which the steam S flows, an intermediate body outlet  33  that opens downward from the inside and configured to exhaust the steam S, and a flow path  34  configured to connect the intermediate body inlet  32  and the intermediate body outlet  33 . The flow path  34  in the intermediate body  31  extends from the intermediate body inlet  32  in a far side-near side direction Df with respect to the intermediate body inlet  32  that is the horizontal direction, extends gradually downward as it extends away from the intermediate body inlet  32 , and reaches the intermediate body outlet  33 . The intermediate body inlet  32  is connected to the exhaust steam outlet  27  of the steam turbine  20 . Accordingly, the far side-near side direction Df with respect to the intermediate body inlet  32  coincides with the axial direction Da of the steam turbine  20 . 
     The main body  35  has a bottom plate  36   b , and a side plate  36   s  extending upward from an edge of the bottom plate  36   b . While not shown, the inside of the main body  35  is partitioned into a condensing chamber  37 , a cooling water inlet chamber (not shown), and a cooling water outlet chamber (not shown). An upper section of the condensing chamber  37  opens. The opening forms a main body inlet  38 . Accordingly, the main body inlet  38  opens upward from the condensing chamber  37 . The main body inlet  38  is connected to the intermediate body outlet  33 . A lower section in the condensing chamber  37  constitutes a hot well  39  in which the steam S condensed into liquid is accumulated. 
     The plurality of heat transfer pipe groups  41  are arranged in the horizontal direction and disposed in the condensing chamber  37 . Among the plurality of heat transfer pipe groups  41 , at least two of the heat transfer pipe groups  41  are arranged in the above-mentioned far side-near side direction Df. 
     Each of the plurality of heat transfer pipe groups  41  is constituted by a plurality of heat transfer pipes  42 . Each of the heat transfer pipes  42  extends in the horizontal direction. 
     Here, a three-dimensional shape formed by virtual surfaces that circumscribe the plurality of heat transfer pipes  42  disposed on the outermost side among the plurality of heat transfer pipes  42  that constitute the heat transfer pipe group  41  is set as a pipe group outline  43 . The pipe group outline  43  has a bottom surface  44  directed downward, a side surface  45  extending upward from an edge of the bottom surface  44 , and an upper surface  46  directed upward. A dimension of the pipe group outline  43  in the vertical direction is larger than a dimension of the pipe group outline  43  in the horizontal direction. An upper section of the pipe group outline  43  including the upper surface  46  has a cross-sectional area in the horizontal direction that is gradually increased downward. Accordingly, the upper surface  46  has an inclined surface  47  gradually inclined downward as it approaches the side surface  45 . In the embodiment, a position in the horizontal direction of a center Ct of a top surface  48  which is a collection of points at highest positions in the upper surface  46 , and a position in the horizontal direction of a center Cb of the bottom surface  44  coincide with each other. 
     In addition, here, a side of the main body with reference to the intermediate body inlet in the far side-near side direction Df is referred to as a far side Dff, and a side of the intermediate body inlet with respect to the main body in the far side-near side direction Df is referred to as a near side Dfn. 
     A near-side outlet edge  33   n  that is an edge of the intermediate body outlet  33  on the near side Dfn in the far side-near side direction Df is disposed below the uppermost position among the plurality of heat transfer pipe groups  41 . More specifically, the near-side outlet edge  33   n  is disposed in the vicinity of an intermediate position in the heat transfer pipe group  41  in the vertical direction. Meanwhile, a far-side outlet edge  33   f  that is an edge of the intermediate body outlet  33  on the far side Dff in the far side-near side direction Df is disposed above the uppermost position among the plurality of heat transfer pipe groups  41 . For this reason, a position of the edge of the intermediate body outlet  33  is disposed gradually downward from the far-side outlet edge  33   f  toward the near side Dfn. Further, the uppermost position among the plurality of heat transfer pipe groups  41  is a position of the top surface  48  of the pipe group outline  43 . 
     A near-side inner surface  34   n  that is an inner surface of the intermediate body  31  that forms the flow path  34  of the intermediate body  31  and including the near-side outlet edge  33   n  is a surface directed toward the near side Dfn in the far side-near side direction Df while being directed upward from the near-side outlet edge  33   n . In addition, a far-side inner surface  34   f  that is an inner surface of the intermediate body  31  and including the far-side outlet edge  33   f  is a surface directed toward the near side Dfn in the far side-near side direction Df while being directed upward from the far-side outlet edge  33   f.    
     The water-feeding line  16  is connected to the hot well  39  of the condenser  30 . The cooling water pump  11  is connected to the heat transfer pipes  42  that constitute the plurality of heat transfer pipe groups  41  by a cooling water line  12  via the cooling water inlet chamber (not shown) in the main body  35 . The cooling water pump  11  pumps up water from a water source W such as the sea or a river and supplies the water to the heat transfer pipes  42  that constitute the plurality of heat transfer pipe groups  41 . The heat transfer pipes  42  that constitute the plurality of heat transfer pipe groups  41  are connected to a drain line  13  via the cooling water outlet chamber (not shown) in the main body  35 . The drain line  13  extends to the inside of a drain pit  14  or directly to the water source W. The drain pit  14  extends to, for example, the above-mentioned water source W. 
     The steam generated in the steam generator  17  flows into the main body casing  22  of the steam turbine  20  via the main steam line  18 . The steam rotates the rotor  21  while flowing through the main body casing  22 . As a result, the rotor of the generator  19  rotates and the generator  19  generates power. 
     The steam flowing into the main body casing  22  is exhausted to the axial downstream side Dad from the exhaust steam outlet  27  of the exhaust casing  25  via the inside of the exhaust casing  25 . The steam S exhausted from the steam turbine  20  flows into the intermediate body  31  of the condenser  30  from the intermediate body inlet  32 . As described above, the exhaust steam outlet  27  of the steam turbine  20  opens from the inside of the exhaust casing  25  in the horizontal direction (the axial downstream side Dad). In addition, the intermediate body inlet  32  connected to the exhaust steam outlet  27  opens from the inside of the intermediate body  31  in the horizontal direction. Accordingly, a flow direction component of the steam S flowing into the intermediate body  31  has a large horizontal component. As the steam S flowing into the intermediate body  31  flows through the inside of the intermediate body  31  from the intermediate body inlet  32  toward the intermediate body outlet  33 , the downward component in the direction component of the flow of the steam S increases gradually. In other words, as the steam S flowing into the intermediate body  31  flows through the inside of the intermediate body  31  from the intermediate body inlet  32  toward the intermediate body outlet  33 , the flow is directed gradually downward. 
     The steam S passing through the intermediate body  31  flows into the condensing chamber  37  of the main body  35  from the main body inlet  38 . The steam S flows mainly downward through the inside of the condensing chamber  37 . The steam S exchanges heat with the cooling water flowing through the plurality of heat transfer pipes  42  that constitute each of the heat transfer pipe groups  41  while flowing through the condensing chamber  37 . 
     The steam S is condensed through heat exchange with the cooling water flowing through the plurality of heat transfer pipes  42  that constitute each of the heat transfer pipe groups  41  and liquefied into water. The water is accumulated in the hot well  39  on a lower side in the condensing chamber  37 . The water accumulated in the hot well  39  is returned to the steam generator  17  via the water-feeding line  16  and the water-feeding pump  15 . 
     In the embodiment, the plurality of heat transfer pipe groups  41  are disposed to be arranged in the main body  35  in the horizontal direction. For this reason, in the embodiment, in comparison with the condenser in which the heat transfer pipe groups are disposed to be arranged in the vertical direction, a level difference between the heat transfer pipe  42  at the highest position and a water surface of the water source W can be relatively reduced. Accordingly, in the embodiment, a pumping head of the cooling water pump  11  can be decreased. For this reason, in the embodiment, installation cost and running cost of the cooling water pump  11  can be reduced. 
     When the position of the heat transfer pipe  42  is high, the cooling water flowing out of the heat transfer pipe  42  may boil under a reduced pressure in a process in which the cooling water reaches the water source W. For this reason, in this case, a method of raising a water level of the drain pit  14  between the heat transfer pipe group  41  and the water source W and reducing a level difference between the heat transfer pipes  42  at the highest position and the water surface of the drain pit  14  is adopted. In the embodiment, as described above, since a height of the heat transfer pipes  42  at the highest position can be lowered, installation cost of the drain pit  14  can be reduced. 
     Accordingly, in the embodiment, initial cost and running cost of the steam turbine plant can be reduced. 
     In addition, the pipe group outline  43  of the embodiment has a dimension in the horizontal direction that is smaller than a dimension in the vertical direction. Accordingly, in the embodiment, the bottom surface  44  of the pipe group outline  43  can be reduced. For this reason, in the embodiment, even when the plurality of heat transfer pipe groups  41  are disposed to be arranged in the main body  35  in the horizontal direction, an increase in occupation area of the condenser  30  can be minimized. 
     Further, an effect of the steam turbine plant of the embodiment will be described in comparison with a steam turbine plant of a comparative example with reference to  FIG. 3 . 
     The steam turbine plant of the comparative example also includes the steam turbine  20  and a condenser  30   x  configured to condense the steam exhausted from the steam turbine  20 , both shown by two-dot chain lines in  FIG. 3 . The steam turbine  20  of the comparative example is the same as the steam turbine  20  of the embodiment. Meanwhile, the condenser  30   x  of the comparative example is different from the condenser  30  of the embodiment. 
     The condenser  30   x  of the comparative example also includes a plurality of heat transfer pipe groups  41 , a main body  35   x  configured to cover the plurality of heat transfer pipe groups  41 , and an intermediate body  31   x  configured to guide the steam S from the steam turbine  20  into the main body  35   x.    
     The intermediate body  31   x  has an intermediate body inlet  32   x  that opens in the horizontal direction from the inside and into which the steam S flows, an intermediate body outlet  33   x  that opens downward from the inside and through which the steam S is exhausted, and a flow path  34   x  configured to connect the intermediate body inlet  32   x  and the intermediate body outlet  33   x . The flow path  34   x  in the intermediate body  31   x  extends from the intermediate body inlet  32   x  in the far side-near side direction Df with respect to the intermediate body inlet  32   x  that is the horizontal direction, extends gradually downward as it extends away from the intermediate body inlet  32   x , and reaches the intermediate body outlet  33   x . The intermediate body inlet  32   x  is connected to the exhaust steam outlet  27  of the steam turbine  20 . The intermediate body outlet  33   x  is connected to a main body inlet  38   x  of the main body  35   x . The above-mentioned configuration related to the intermediate body  31   x  of the comparative example is the same as the configuration of the intermediate body  31  of the embodiment. 
     However, in the comparative example, a near-side outlet edge  33   nx  that is an edge of the intermediate body outlet  33   x  on the near side Dfn in the far side-near side direction Df and a far-side outlet edge  33   fx  that is an edge of the intermediate body outlet  33   x  on the far side Dff in the far side-near side direction Df are disposed at the same position in the vertical direction. Moreover, in the comparative example, the entire edge of the intermediate body outlet  33   x  is disposed above the uppermost position among the plurality of heat transfer pipe groups  41 . Further, the far-side outlet edge  33   fx  of the comparative example and the far-side outlet edge  33   f  of the embodiment are disposed at the same position in the vertical direction. 
     Suppose that a distance in the vertical direction from a lower end  32   bx  of the intermediate body inlet  32   x  to the near-side outlet edge  33   nx  of the intermediate body outlet  33   x  in the comparative example is equal to a distance in the vertical direction from a lower end  32   b  of the intermediate body inlet  32  to the near-side outlet edge  33   n  of the intermediate body outlet  33  in the embodiment. In this case, since the near-side outlet edge  33   n  of the embodiment is disposed below the near-side outlet edge  33   nx  of the comparative example in the vertical direction, the lower end  32   b  of the intermediate body inlet  32  of the embodiment is disposed below the lower end  32   bx  of the intermediate body inlet  32   x  of the comparative example. 
     Accordingly, the steam turbine  20  connected to the intermediate body inlet  32  in the embodiment is disposed below the steam turbine  20  connected to the intermediate body inlet  32   x  in the comparative example. For this reason, installation cost of the steam turbine  20  in the embodiment can be made lower than that of the comparative example. Accordingly, in the embodiment, also from this viewpoint, initial cost of the steam turbine plant can be reduced. 
     In addition, in the embodiment, the position of the edge of the intermediate body outlet  33  is disposed gradually downward from the far-side outlet edge  33   f  toward the near side Dfn. In other words, in the embodiment, the edge of the intermediate body outlet  33  is inclined from the far-side outlet edge  33   f  toward the near-side outlet edge  33   n . Accordingly, in the embodiment, an opening area of the intermediate body outlet  33  can be increased. In addition, in the embodiment, the near-side outlet edge  33   n  of the intermediate body outlet  33  is disposed below the uppermost position among the plurality of heat transfer pipe groups  41 , and the near-side inner surface  34   n  of the intermediate body  31  is directed toward the near side Dfn in the far side-near side direction Df while being directed upward from the near-side outlet edge  33   n . For this reason, in the embodiment, the steam flows from the lateral side as well as from the upper side into the heat transfer pipe group  41  farthest on the near side Dfn among the plurality of heat transfer pipe groups  41 . In other words, in the embodiment, a flow path area of the flow path on the side of the intermediate body outlet  33  in the flow path  34  in the intermediate body  31  is increased. As a result, in the embodiment, an average flow speed of the steam flowing into the heat transfer pipe groups  41  can be made lower than that of the comparative example, and it is considered that a certain effect on suppression of erosion in the heat transfer pipes  42  is provided. 
     Second Embodiment 
     A second embodiment of the steam turbine plant according to the present invention will be described with reference to  FIG. 4 . 
     The steam turbine plant of the embodiment includes, like the steam turbine plant of the first embodiment, a steam turbine  20   a  and a condenser  30 . 
     The steam turbine  20   a  of the embodiment also has, like the steam turbine  20  of the first embodiment, the rotor  21  that rotates about the turbine axis At, a main body casing  22   a  configured to cover the rotor  21 , and an exhaust casing  25   a  configured to exhaust steam from the inside of the main body casing  22   a . The main body casing  22   a  is formed in a tubular shape around the turbine axis At. A steam inlet (not shown) is formed axially upstream from the main body casing  22   a  having a tubular shape. A steam outlet  24   a  is formed axially downstream from the main body casing  22   a  having a tubular shape. However, unlike the steam outlet  24  of the first embodiment, the steam outlet  24   a  opens sideways from the inside of the main body casing  22   a.    
     The exhaust casing  25   a  is formed in a tubular shape about an axis that is perpendicular to the turbine axis At and oriented in the horizontal direction. The exhaust steam inlet  26  is formed on one end of the exhaust casing  25   a  in the axial direction. In addition, the exhaust steam outlet  27  is formed on the other end of the exhaust casing  25   a  in the axial direction. Both of the exhaust steam inlet  26  and the exhaust steam outlet  27  open from the inside of the exhaust casing  25   a  in the horizontal direction. The exhaust steam inlet  26  is connected to the steam outlet  24   a  of the main body casing  22   a.    
     Accordingly, the steam turbine  20   a  of the embodiment is a lateral exhaust type steam turbine configured to exhaust steam sideways perpendicular to the turbine axis At. 
     The condenser  30  of the embodiment includes, like the condenser  30  of the first embodiment, the plurality of heat transfer pipe groups  41 , the main body  35  configured to cover the plurality of heat transfer pipe groups  41 , and the intermediate body  31  configured to guide the steam S from the steam turbine  20   a  into the main body  35 . The plurality of heat transfer pipe groups  41 , the main body  35  and the intermediate body  31  of the embodiment are basically the same as the plurality of heat transfer pipe groups  41 , the main body  35  and the intermediate body  31  of the first embodiment, respectively. Accordingly, the intermediate body  31  of the embodiment also has the intermediate body inlet  32  that opens from the inside in the horizontal direction and into which the steam S flows, the intermediate body outlet  33  that opens downward from the inside and through which the steam S is exhausted, and the flow path  34  configured to connect the intermediate body inlet  32  and the intermediate body outlet  33 . The flow path  34  in the intermediate body  31  extends from the intermediate body inlet  32  in the far side-near side direction Df with respect to the intermediate body inlet  32  that is the horizontal direction, extends downward as it extends away from the intermediate body inlet  32 , and reaches the intermediate body outlet  33 . The intermediate body inlet  32  is connected to the exhaust steam outlet  27  of the steam turbine  20   a . Accordingly, unlike in the first embodiment, the far side-near side direction Df with respect to the intermediate body inlet  32  is a horizontal direction perpendicular to the turbine axis At. 
     As described above, the condenser  30  of the embodiment is also the same as the condenser  30  of the first embodiment. Accordingly, also in the embodiment, initial cost and running cost of the steam turbine plant can be reduced. 
     In addition, also in the embodiment, the pipe group outline  43  has a dimension in the horizontal direction that is smaller than a dimension in the vertical direction. Accordingly, also in the embodiment, an increase in occupation area of the condenser  30  can be minimized. 
     That is, also when the steam turbine  20   a  is a lateral exhaust type, since the condenser  30  having the same structure as the first embodiment is employed, the same effect as in the first embodiment can be obtained. 
     [First Variant] 
     A first variant of the condenser  30  according to the first embodiment will be described with reference to  FIG. 5 . 
     In a condenser  30   b  of the variant, a pipe group outline  43   a  of a heat transfer pipe group  41   a  disposed farthest on the near side Dfn in the far side-near side direction Df with respect to the intermediate body inlet  32  among the plurality of heat transfer pipe groups  41  is changed. In the variant, the center Ct of a top surface  48   a  in the pipe group outline  43   a  of the heat transfer pipe group  41   a  on the near side Dfn is disposed closer to the near side Dfn than the center Cb of the bottom surface  44  in the pipe group outline  43   a . Accordingly, the pipe group outline  43   a  has an eccentric outline. 
     Most of steam Sa flowing into the intermediate body  31  from an upper part in the opening of the intermediate body inlet  32  flows into the main body  35  from a part on the far side Dff in the opening of the main body inlet  38 . Meanwhile, most of steam St flowing into the intermediate body  31  from a lower part in the opening of the intermediate body inlet  32  flows into the main body  35  from a part on the near side Dfn in the opening of the main body inlet  38 . Accordingly, a distance in the vertical direction from the intermediate body inlet  32  to the main body inlet  38  for the most of the steam St flowing into the main body  35  from the part on the near side Dfn is smaller than that for the steam Sa flowing into the main body  35  from the part on the far side Dff. For this reason, a downward component in the flow direction component of the steam S is smaller in the steam St flowing into the main body  35  from the part on the near side Dfn than in the steam Sa flowing into the main body  35  from the part on the far side Dff. In other words, a horizontal component in the flow direction component of the steam S is larger in the steam St flowing into the main body  35  from the part on the near side Dfn than in the steam Sa flowing into the main body  35  from the part on the far side Dff. 
     In addition, among the plurality of heat transfer pipe groups  41 , the heat transfer pipe group  41   a  disposed on the near side Dfn has a larger contact quantity with the steam Sa flowing into the main body  35  from the part on the near side Dfn than with the steam St flowing into the main body  35  from the part on the far side Dff. 
     Here, in the variant, since the pipe group outline  43   a  of the heat transfer pipe group  41   a  disposed on the near side Dfn has an eccentric outline as described above, efficiency of heat exchange between the cooling water in the heat transfer pipes  42  that constitute the heat transfer pipe group  41   a  and the steam S is increased. 
     Further, while the variant is the variant of the first embodiment, the heat transfer pipe group  41  on the near side Dfn of the second embodiment may have the same configuration as in the variant. 
     [Second Variant] 
     A second variant of the condenser  30  according to the first embodiment will be described with reference to  FIG. 6 . 
     In the condenser  30   b  of the first variant, among the plurality of heat transfer pipe groups  41 , only the heat transfer pipe group  41   a  farthest on the near side Dfn has an eccentric outline. However, like in a condenser  30   c  of the variant, a heat transfer pipe group  41   b  on the far side Dff may also have an eccentric outline. 
     Here, a distance in the far side-near side direction Df from the center Cb of the bottom surface  44  in the pipe group outline  43   a  of the heat transfer pipe group  41   a  on the near side Dfn to the center Ct of the top surface  48   a  of the pipe group outline  43   a  is set as an eccentric amount Δa. In addition, a distance in the far side-near side direction Df from the center Cb of the bottom surface  44  in a pipe group outline  43   b  of the heat transfer pipe group  41   b  on the far side Dff to the center Ct of a top surface  48   b  of the pipe group outline  43   b  is set as an eccentric amount Δb. 
     When the heat transfer pipe group  41   b  on the far side Dff also has an eccentric outline as in the variant, the eccentric amount Δb in the pipe group outline  43   b  of the heat transfer pipe group  41   b  is preferably smaller than the eccentric amount Δa in the pipe group outline  43   a  of the heat transfer pipe group  41   a  on the near side Dfn. In other words, the eccentric amount Δa in the pipe group outline  43   a  of the heat transfer pipe group  41   a  on the near side Dfn is preferably larger than the eccentric amount Δb in the pipe group outline  43   b  of the heat transfer pipe group  41   b  on the far side Dff. 
     Further, while the variant is the variant of the first embodiment, the plurality of heat transfer pipe groups  41  of the second embodiment may have the same configuration as in the variant. 
     [Third Variant] 
     A third variant of the condenser  30  according to the first embodiment will be described with reference to  FIG. 7 . 
     A condenser  30   d  of the variant includes a steam guide  51  disposed in the intermediate body  31  and configured to cause a direction of a flow of the steam S flowing in from the intermediate body inlet  32  to be directed gradually downward. The steam guide  51  is curved gradually downward as it extends toward the far side Dff in the far side-near side direction Df. 
     Accordingly, in the variant, a downward component in the flow direction component of the steam S flowing into the main body  35  from the main body inlet  38  can be made larger than the same component in the first embodiment. For this reason, in the variant, efficiency of heat exchange between the cooling water in the heat transfer pipes  42  that constitute each of the heat transfer pipe groups  41  and the steam S can be increased. 
     Further, while the variant is the variant of the first embodiment, the condenser of the second embodiment may also have the same configuration as in the variant. 
     [Fourth Variant] 
     A fourth variant of the condenser  30  according to the first embodiment will be described with reference to  FIG. 8 . 
     In the first embodiment, the uppermost position among the plurality of heat transfer pipe groups  41  is above the lower end  32   b  of the intermediate body inlet  32 . Meanwhile, in a condenser  30   e  of the variant, the uppermost position among the plurality of heat transfer pipe groups  41  is below the lower end  32   b  of the intermediate body inlet  32 . In other words, the plurality of heat transfer pipe groups  41  are disposed at positions below the lower end  32   b  of the intermediate body inlet  32 . 
     In the variant, to realize the above-mentioned disposition of the plurality of heat transfer pipe groups  41 , a position of a near-side outlet edge  33   ne  of the intermediate body outlet  33  in an intermediate body  31   e  is set to be higher than a position of the near-side outlet edge  33   n  of the intermediate body outlet  33  of the first embodiment. In relation to this, a shape of a main body  35   e  of the variant is also slightly different from a shape of the main body  35  of the first embodiment. Further, together with this, an installation position of the steam turbine  20  is raised. Further, in the variant, a position of a far-side outlet edge  33   fe  of the intermediate body outlet  33  is the same as the position of the far-side outlet edge  33   f  of the intermediate body outlet  33  of the first embodiment in the vertical direction. 
     Thus, in the variant, since the plurality of heat transfer pipe groups  41  are disposed at positions below the lower end  32   b  of the intermediate body inlet  32 , it is considered that the steam that flows straight from the steam turbine  20  in the horizontal direction does not directly flow into the heat transfer pipe groups  41 , and that occurrence of erosion in the heat transfer pipes  42  can be reduced to a lower level than in the first embodiment. However, in the variant, as described above, an installation position of the steam turbine  20  is raised. Accordingly, whether to set the uppermost position among the plurality of heat transfer pipe groups  41  to be above or below the lower end  32   b  of the intermediate body inlet  32  should be determined according to which of reducing the occurrence of erosion in the heat transfer pipes  42  and lowering the installation position of the steam turbine  20  is given more emphasis. 
     Incidentally, a gas turbine combined cycle plant includes a steam turbine plant provided with a steam turbine and a condenser. Accordingly, the present invention may also be applied to the condenser of a gas turbine combined cycle plant. 
     INDUSTRIAL APPLICABILITY 
     According to an aspect of the present invention, initial cost and running cost of a steam turbine plant can be reduced. 
     REFERENCE SIGNS LIST 
       11  Cooling water pump 
       12  Cooling water line 
       13  Drain line 
       14  Drain pit 
       15  Water-feeding pump 
       16  Water-feeding line 
       17  Steam generator 
       18  Main steam line 
       19  Generator 
       20 ,  20   a  Steam turbine 
       21  Rotor 
       22 ,  22   a  Main body casing 
       23  Steam inlet 
       24 ,  24   a  Steam outlet 
       25 ,  25   a  Exhaust casing 
       26  Exhaust steam inlet 
       27  Exhaust steam outlet 
       30 ,  30   a ,  30   b ,  30   c ,  30   d ,  30   e  Condenser 
       31 ,  31   e  Intermediate body 
       32  Intermediate body inlet 
       32   b  Lower end 
       33  Intermediate body outlet 
       33   f ,  33   fe  Far-side outlet edge 
       33   n ,  33   ne  Near-side outlet edge 
       34  Flow path 
       34   f  Far-side inner surface 
       34   n  Near-side inner surface 
       35 ,  35   e  Main body 
       36   b  Bottom plate 
       36   s  Side plate 
       37  Condensing chamber 
       38  Main body inlet 
       39  Hot well 
       41 ,  41   a ,  41   b  Heat transfer pipe group 
       42  Heat transfer pipe 
       43 ,  43   a ,  43   b  Pipe group outline 
       44  Bottom surface 
       45  Side surface 
       46  Upper surface 
       47  Inclined surface 
       48 ,  48   a ,  48   b  Top surface 
       51  Steam guide 
     At Turbine axis 
     Da Axial direction 
     Dad Axial downstream side 
     Dau Axial upstream side 
     Df Far side-near side direction 
     Dff Far side 
     Dfn Near side 
     S Steam 
     W Water source