JP6552834B2 - Turbine equipment - Google Patents

Description

The present invention relates turbine set Bei.

2. Description of the Related Art Conventionally, a bearing box that is disposed between a plurality of turbines connected via a rotating shaft or between a turbine and a compressor and supports the rotating shaft is known (for example, see Patent Document 1). ).
In the lower casing main body portion of the turbine disclosed in Patent Document 1, a cat foot portion projecting along the axial direction of the rotating shaft is formed, and the lower surface of the cat foot portion is supported by a bearing stand provided on a bearing box It has become.

Patent No. 5611425 gazette

  When the casing of the turbine disclosed in Patent Document 1 is heated during operation, the entire casing thermally expands in the radial direction orthogonal to the axial direction of the rotation shaft. When the casing of the turbine is installed on the installation surface, as the entire casing thermally expands in the radial direction, the central axis of the casing moves upward and the cat foot also moves upward.

  When the amount of deformation of the passenger compartment due to thermal expansion increases, the central axis of the passenger compartment moves upward relative to the rotating shaft supported by the bearing housing, and these axes do not coincide. In this case, the clearance between the rotary shaft and the seal member provided around the rotary shaft inside the turbine may be adversely affected.

In addition, when the amount of deformation of the passenger compartment due to thermal expansion increases, the claw foot moves upward and is not supported by the bearing base of the bearing box. In this case, the load of the turbine casing is not supported by the bearing stand, and an excessive load may be applied to other locations.

The present invention has been made in view of the above-described circumstances, and even when the turbine casing is deformed by thermal expansion, the rotary shaft is supported in a state in which the rotation axis coincides with the central axis of the turbine casing. and its object is to provide a turbine equipment capable of supporting the platform.

In order to achieve the above object, the present invention provides the following means.
A turbine installation according to an aspect of the present invention includes a turbine casing installed on an installation surface and accommodating therein a rotation axis extending along an axis, and provided at one end side along the axis of the turbine casing And a bearing stand that supports the rotating shaft, the turbine casing includes a bearing stand support portion that supports the bearing stand, and the bearing stand is disposed above the bearing stand support portion and A pair of flange portions that enable relative movement of the bearing base support portion in a horizontal direction perpendicular to the axial direction along the axis, and the base portion disposed above the base portion installed on the installation surface And a moving mechanism for enabling relative movement in the axial direction with respect to the bearing support portion, wherein the turbine casing side of the bearing support is inclined downward from the turbine casing to the bearing stand from the turbine casing. The Tei Ru.

  According to the turbine equipment according to one aspect of the present invention, the bearing stand support portion provided on one end side of the turbine casing supports the bearing stand from below via the flange portion disposed above the turbine stand. Therefore, when the turbine casing is thermally expanded during the operation of the turbine equipment and the central axis of the turbine casing moves upward, the bearing base supported by the bearing base support portion also moves upward. Therefore, even when the turbine casing is deformed due to thermal expansion, it is possible to make the rotation axis coincide with the central axis of the turbine casing.

Further, according to the turbine equipment according to the aspect of the present invention, the bearing stand supporting portion moves relative to the flange portion in the horizontal direction orthogonal to the axial direction of the rotation shaft even when the turbine casing is thermally expanded. Is possible. Therefore, even if the turbine casing thermally expands and the bearing support portion moves in the horizontal direction, the bearing support portion can appropriately maintain the state of supporting the bearing support from below via the flange portion.
Thus, according to the turbine equipment according to one aspect of the present invention, even if the turbine casing is deformed by thermal expansion, the rotating shaft is kept in a state where the rotating shaft and the central axis of the turbine casing are aligned. A turbine installation can be provided that can be supported by a bearing stand.

  In the turbine equipment according to one aspect of the present invention, the bearing stand supporting portion includes a pair of projecting portions protruding along the axis on both sides of the axis at one end side along the axis of the turbine casing. A pair of through holes penetrating in the vertical direction are formed in a pair of the flanges disposed above the tip side of the pair of protrusions, and in the upper side of the tip side of the pair of protrusions A pair of fastening holes are formed at positions facing the pair of through holes, and the turbine casing is fastened to the pair of fastening holes in a state of being inserted into the pair of through holes. A member may be provided, and the first axial length of the through hole and the second horizontal length of the through hole may be longer than the outer diameter of the fastening member.

According to the turbine equipment of the present configuration, the first length in the axial direction of the pair of through holes and the second length in the horizontal direction orthogonal to the axial direction are longer than the outer diameters of the pair of fastening members. Therefore, if a pair of protrusion part moves to an axial direction by thermal expansion at the time of an operation | movement, it will move relatively to an axial direction with respect to a pair of flange part formed in a bearing stand. Similarly, when the pair of protrusions move in the horizontal direction due to thermal expansion during operation, they move relative to the pair of flange portions formed on the bearing base in the horizontal direction.
As described above, according to the turbine equipment according to the present configuration, even if the pair of protrusions move in the axial direction or in the horizontal direction orthogonal to the axial direction due to thermal expansion during operation, the pair of protrusions support the bearing stand It can be maintained properly.

A bearing stand according to an aspect of the present invention is a bearing stand that supports a rotating shaft that extends along an axis, and is installed on an installation surface and along the axis of a turbine casing that houses the rotating shaft therein. were provided on the one end side, said turbine wheel chamber, said pedestal support portion supporting the pedestal, one end of the axial axis direction along the attached below the turbine casing, said axis direction of the other end is attached below the pedestal, and the pressing part for moving extruding the pedestal in the axial direction, comprises a front Symbol shaft while being disposed above the pedestal supporting portion A flange portion that enables relative movement of the bearing stand support portion in a horizontal direction perpendicular to the linear direction, and a relative position in the axial direction relative to the base portion that is disposed above the base portion installed on the installation surface. It is possible to move Includes a moving mechanism that, a.

  According to the bearing stand according to one aspect of the present invention, the bearing stand is supported from below by the bearing stand support portion provided on one end side of the turbine casing through the flange portion disposed above the bearing stand support portion. Therefore, when the turbine casing is thermally expanded during the operation of the turbine equipment and the central axis of the turbine casing moves upward, the bearing base supported by the bearing base support portion also moves upward. Therefore, even when the turbine casing is deformed due to thermal expansion, it is possible to make the rotation axis coincide with the central axis of the turbine casing.

Further, according to the bearing stand according to one aspect of the present invention, the bearing stand supporting portion moves relative to the flange portion in the horizontal direction orthogonal to the axial direction of the rotation shaft even when the turbine casing is thermally expanded. Is possible. Therefore, even if the turbine casing thermally expands and the bearing support portion moves in the horizontal direction, the bearing support portion can appropriately maintain the state of supporting the bearing support from below via the flange portion.
As described above, according to the bearing stand according to one aspect of the present invention, even when the turbine casing is deformed by thermal expansion, the rotation shaft is in a state in which the rotation axis and the central axis of the turbine casing are aligned. It is possible to provide a bearing stand that can be supported.

  In the bearing stand according to one aspect of the present invention, the bearing support portion includes a pair of projecting portions protruding along the axis on both sides of the axis at one end side along the axis of the turbine casing. A pair of through holes penetrating in the vertical direction are formed in a pair of the flanges disposed above the tip side of the pair of protrusions, and in the upper side of the tip side of the pair of protrusions A pair of fastening holes are formed at positions facing the pair of through holes, and a pair of fastening members are fastened to the pair of fastening holes in a state of being inserted into the pair of through holes. The first length in the axial direction of the hole and the second length in the horizontal direction of the through hole may be longer than the outer diameter of the fastening member.

According to the bearing stand according to the present configuration, the first length in the axial direction of the pair of through holes and the second length in the horizontal direction orthogonal to the axial direction are longer than the outer diameters of the pair of fastening members. Therefore, if a pair of protrusion part moves to an axial direction by thermal expansion at the time of an operation | movement, it will move relatively to an axial direction with respect to a pair of flange part formed in a bearing stand. Similarly, when the pair of protrusions move in the horizontal direction due to thermal expansion during operation, they move relative to the pair of flange portions formed on the bearing base in the horizontal direction.
Thus, according to the bearing stand according to the present configuration, even if the pair of protrusions move in the axial direction or the horizontal direction perpendicular thereto due to thermal expansion during operation, the pair of protrusions support the bearing stand. It can be maintained properly.

According to the present invention, even when the turbine casing is deformed due to thermal expansion, the turbine installation is such that the rotating shaft can be supported by the bearing stand in a state where the rotating shaft and the central axis of the turbine casing are aligned. it is possible to provide a Bei.

1 is a configuration diagram of a marine propulsion plant according to an embodiment of the present invention. It is a front view which shows the low pressure turbine shown in FIG. It is a top view which shows the low pressure turbine shown in FIG. It is an AA arrow side sectional view of a bearing stand shown in Drawing 2, (a) shows the state before operation of turbine equipment, and (b) shows the state in operation of turbine equipment. It is a BB arrow sectional view of the bearing stand shown in Drawing 4 (a). It is a principal part enlarged view of the low-pressure turbine shown in FIG. 2, (a) shows the state before operation | movement of turbine equipment, (b) shows the state under operation of turbine equipment. It is a front view which shows the low pressure turbine of a comparative example. It is CC arrow line sectional side view of the bearing stand of the comparative example shown in FIG. 7, (a) shows the state before operation of a turbine installation, (b) shows the state in operation of a turbine installation.

A marine propulsion plant 1 according to an embodiment of the present invention will be described below with reference to the drawings.
As shown in FIG. 1, the marine propulsion plant 1 according to the present embodiment includes a turbine equipment 100 for providing rotational power to a rotary shaft attached to the turbine by rotating a turbine with steam, and a turbine equipment for generating superheated steam. A marine boiler 200 for supplying to 100, a reducer 300 for reducing the rotational power of the rotating shaft to rotate the propeller shaft, and a propeller for generating propulsion of the ship by being connected to the propeller shaft 70 rotated by the reducer 300 400 and a condenser 500 for cooling and condensing the steam used in the turbine equipment 100.

  The turbine equipment 100 includes a high-pressure turbine 10 to which superheated steam generated by the marine boiler 200 is supplied, and an intermediate-pressure turbine 20 to which reheated steam discharged from the high-pressure turbine 10 and reheated by the reheater 250 is supplied. And a low pressure turbine 30 to which steam discharged from the intermediate pressure turbine 20 is supplied, and a reverse turbine 40 to which superheated steam generated by the marine boiler 200 is supplied and used when the marine vessel is going backward.

  The rotating shaft 50 connecting the high pressure turbine 10 and the intermediate pressure turbine 20 is further connected to the reduction gear 300. Further, the rotating shaft 60 connected to the low-pressure turbine 30 is further connected to the speed reducer 300. Therefore, the rotational power given to the rotary shaft 50 by the high-pressure turbine 10 and the intermediate-pressure turbine 20 and the rotary power given to the rotary shaft 60 by the low-pressure turbine 30 are transmitted to the speed reducer 300, respectively.

  In addition, you may employ | adopt a diaphragm coupling (illustration omitted) in the connection position of the rotating shaft 50 and the speed reducer 300, and the connection position of the rotating shaft 60 and the speed reducer 300. FIG. By adopting the diaphragm coupling, even when the rotating shaft 50 and the rotating shaft 60 expand and contract in the axial direction due to thermal expansion or the like, the state in which each rotating shaft transmits the rotational power of the speed reducer 300 can be appropriately maintained. it can.

  Reducer 300 decelerates the rotational speed of rotary shaft 50 and the rotational speed of rotary shaft 60, respectively, and transmits the rotational power of rotary shaft 50 and rotary shaft 60 to propeller shaft 70. The propeller 400 coupled to the propeller shaft 70 generates rotational power that propels the ship by rotating with rotational power transmitted from the speed reducer 300.

  Marine boiler 200 has a main burner 210 for burning fuel, a furnace 220 in which main burner 210 is disposed to form a combustion area for fuel, and water evaporated by combustion gas generated by the combustion of fuel in furnace 220. Evaporation tubes 230, a superheater 240 which superheats the steam generated by the evaporation tubes 230 to generate superheated steam and supplies the superheated steam to the high pressure turbine 10, and reheat which superheats the steam discharged from the high pressure turbine 10 And the container 250.

  The condenser 500 is a device that condenses the steam discharged from the low-pressure turbine 30 and the steam discharged from the reverse turbine 40 with cooling water such as seawater. Water generated by condensation of steam by the condenser 500 is again supplied to the evaporation tube group 230 via the water drum.

Next, the low pressure turbine 30 of the present embodiment will be described in more detail with reference to FIGS. 2 to 6.
As shown in the front view of FIG. 2, the low pressure turbine 30 is provided on one end side of the low pressure turbine casing 31 and the low pressure turbine casing 31 installed on the installation surface S formed by the upper surface of the condenser 500. And a bearing stand 32 for supporting a rotating shaft 60, a part of which is accommodated inside the low pressure turbine casing 31.
In the following description, the “horizontal direction” refers to a direction in which there is no inclination with respect to the installation surface S on which the low pressure turbine 30 is installed. Further, the “vertical direction” means a direction orthogonal to the installation surface S on which the low pressure turbine 30 is installed. Therefore, “horizontal direction” and “vertical direction” in the following description refer to a direction uniquely determined based on the installation surface S regardless of the inclination angle with respect to the sea level of the ship provided with the marine propulsion plant 1.

  The low pressure turbine casing 31 is formed of a metal member, and extends along the axis X and accommodates therein a rotating shaft 60 to which a turbine blade (not shown) is attached on the outer peripheral surface. The steam discharged from the intermediate pressure turbine 20 is supplied to the low pressure turbine casing 31 from a steam inlet 31j. Therefore, during operation of the turbine equipment 100, the low pressure turbine casing 31 is heated by the steam and thermally expanded. Since the low-pressure turbine casing 31 is installed on the installation surface S which is the upper surface of the condenser 500, when heated by steam and thermally expanded, the total height extends along the axis X while extending in the vertical direction. . The internal temperature of the low-pressure turbine casing 31 during the operation of the turbine facility 100 is, for example, about 350 ° C. to 400 ° C. at the upstream steam inlet 31j.

  The low pressure turbine casing 31 is, as shown in the plan view of FIG. 3, a pair of projecting portions 31a, which project along the axis X on both sides of the axis X at one end side along the axis X of the low pressure turbine casing 31 31b (bearing support part) is provided. As shown in the side cross-sectional views of FIGS. 4A and 4B, the pair of protrusions 31a and 31b has the weight of the bearing base 32 via the pair of flange portions 32a and 32b included in the bearing base 32. It is supposed to support. In addition, a pair of fastening holes 31d and 31e are formed on the upper surfaces of the pair of projecting portions 31a and 31b.

As shown in FIG. 2, the protruding portion 31 a has a shape in which the distal end side disposed below the flange portion 32 a extends along the axis X. On the other hand, the low pressure turbine casing 31 side of the projecting portion 31 a is shaped to be inclined downward from the upper side in the vertical direction from the low pressure turbine casing 31 to the bearing stand 32. By making the low-pressure turbine casing 31 side of the protrusion 31 a inclined, it is possible to suppress local load from being applied to the connecting portion between the tip end of the protrusion 31 a and the low-pressure turbine casing 31.
In addition, you may make it form in the curved surface shape which can suppress the local load more instead of the shape shown in FIG. 2 instead of the shape shown in FIG. 2 in the connection part of the front end side of the protrusion part 31a and the low pressure turbine casing 31 side.
In addition, although the shape of the protrusion part 31a was demonstrated here, the shape of the protrusion part 31b shall also be the same as that of the protrusion part 31a.

Further, as shown in the front view of FIG. 2, the low pressure turbine casing 31 is disposed at one end side along the axis X of the low pressure turbine casing 31 and pushes the bearing stand 32 in the axial direction along the axis X And a centering beam 31c (pushing portion) to be moved.
One end of the centering beam 31 c in the direction of the axis X is mounted below the low pressure turbine casing 31, and the other end in the direction of the axis X is mounted below the bearing stand 32. As shown in FIG. 2, the centering beam 31c is a member whose lower side is open when viewed from the front.
When the low pressure turbine casing 31 thermally expands, thermal expansion in the direction of the axis X of the low pressure turbine casing 31 occurs. The centering beam 31c transmits this thermal expansion to the bearing stand 32, and pushes the bearing stand 32 in the direction of the axis X.

Also, when the low pressure turbine casing 31 thermally expands, the portion of the steam inlet 31 j of the low pressure turbine casing 31 moves downward in the vertical direction orthogonal to the axis X. The centering beam 31c bends so that the opening is narrowed by this thermal expansion, and moves the bearing base 32 downward in the vertical direction. Thereby, adjustment is performed so that a difference in displacement in the vertical direction between the low pressure turbine casing 31 and the bearing stand 32 does not occur.
Further, as shown in the side cross sectional views of FIG. 4 (a) and FIG. 4 (b), the low pressure turbine casing 31 is provided with a pair of fastening bolts 31f and 31g fastened to the pair of fastening holes 31d and 31e. ).

  As shown in FIGS. 4 (a) and 4 (b), the bearing stand 32 protrudes in the horizontal direction perpendicular to the axis X and is opposed to the upper surface on the tip side of the pair of protrusions 31a and 31b. A pair of flanges 32 a and 32 b disposed and a slide key groove 32 c (moving mechanism) disposed at a position facing the slide key 33 a formed on the upper surface of the base 33 are provided.

  FIG. 4A shows the state of the bearing stand 32 before the operation of the turbine equipment 100. Before the operation of the turbine equipment 100, the low pressure turbine casing 31 is not thermally expanded because high temperature steam is not supplied to the low pressure turbine 30 to the steam inlet 31j. The height of the upper surface of the pair of flange portions 32a and 32b of the bearing stand 32 with respect to the installation surface S is H1. Further, the distance in the horizontal direction between the pair of fastening bolts 31f and 31g is L1.

  On the other hand, FIG. 4B shows the state of the bearing stand 32 during the operation of the turbine equipment 100. During operation of the turbine equipment 100, the low pressure turbine casing 31 is thermally expanded because high temperature steam is supplied to the low pressure turbine 30 to the steam inlet 31j. Therefore, the overall height of the low-pressure turbine casing 31 extends upward in the vertical direction. Further, the horizontal width of the low-pressure turbine casing 31 is extended.

  When the entire height of the low pressure turbine casing 31 is extended, the vertical position of the pair of protrusions 31 a and 31 b is raised as compared with that before the operation of the turbine equipment 100. When the vertical position of the pair of protrusions 31a and 31b rises, the vertical position of the bearing stand 32 supported by the pair of protrusions 31a and 31b via the pair of flange parts 32a and 32b also rises. Therefore, the height H2 of the upper surfaces of the pair of flange portions 32a and 32b of the bearing stand 32 with respect to the installation surface S shown in FIG. 4B is higher than the height H1 shown in FIG.

  As described above, in the low pressure turbine 30 according to the present embodiment, the pair of projecting portions 31a and 31b is disposed on the one end side of the low pressure turbine casing 31 via the pair of flange portions 32a and 32b disposed at the position facing the upper surface thereof. The bearing stand 32 is supported from below. Therefore, when the low pressure turbine casing 31 thermally expands during operation of the turbine equipment 100 and the central axis of the low pressure turbine casing 31 moves upward, the bearing stand 32 supported by the pair of projecting portions 31a and 31b accordingly. Also move upwards. Therefore, even when the low pressure turbine casing 31 is deformed by thermal expansion, the rotary shaft 60 and the central axis of the low pressure turbine casing 31 can be made to coincide with each other.

  When the horizontal width of the low-pressure turbine casing 31 is increased, the horizontal distance between the pair of protrusions 31a and 31b is extended to be the distance L2 before the turbine facility 100 is operated. Even if the horizontal distance between the pair of protrusions 31a and 31b extends from L1 to L2, the low pressure turbine casing 31 is formed by the pair of through holes 32d and 32e formed in the pair of flanges 32a and 32b of the bearing stand 32. The state of supporting the bearing stand 32 is maintained.

As shown in FIG. 5 (sectional view taken along the line B-B in FIG. 4A), the pair of flanges 32a and 32b penetrates in the vertical direction and has a first length W1 in the direction of the axis X and the axis A pair of through holes 32d and 32e which are circular in plan view and in which the lengths W2 in the horizontal direction orthogonal to X coincide with each other are formed. The pair of fastening holes 31d and 31e described above are formed at positions facing the pair of through holes 32d and 32e on the upper surfaces of the pair of protrusions 31a and 31b.
Further, as shown in FIG. 4, the pair of fastening bolts 31f, 31g provided in the low pressure turbine casing 31 is fastened to the pair of fastening holes 31d, 31e in a state of being inserted into the pair of through holes 32d, 32e.

  Further, a pair of slide pedestals 32f and 32g (sliding members) that slide on the upper surfaces of the pair of projecting portions 31a and 31b of the low-pressure turbine casing 31 are attached to the lower surfaces of the pair of flanges 32a and 32b. . The lower surface of the slide bases 32f and 32g and the upper surface of the pair of projecting portions 31a and 31b are smoothly slid by the lubricating oil.

  As shown in FIG. 5, the second length W2 in the horizontal direction of the pair of through holes 32d and 32e is longer than the outer diameter W3 of the pair of fastening bolts 31f and 31g. Therefore, when the pair of protrusions 31a and 31b move in the horizontal direction due to thermal expansion during operation of the low pressure turbine casing 31, the pair of protrusions 31a with respect to the pair of flanges 32a and 32b formed on the bearing stand 32 , 31b move relative to each other.

  Further, as shown in FIG. 5, the first length W1 in the direction of the axis X of the pair of through holes 32d and 32e into which the pair of fastening bolts 31f and 31g fastened to the pair of projecting portions 31a and 31b are inserted The fastening bolts 31f and 31g are longer than the outer diameter W3. Therefore, when the pair of protrusions 31a and 31b move in the direction of the axis X due to thermal expansion during operation of the low pressure turbine casing 31, the pair of protrusions 31a is formed with respect to the pair of flanges 32a and 32b formed on the bearing stand 32. , 31b move relative to each other.

  As described above, in the low pressure turbine 30 of the present embodiment, even if the low pressure turbine casing 31 thermally expands and the arrangement distance between the pair of projecting portions 31a and 31b spreads in the horizontal direction orthogonal to the axis X direction, the pair The pair of projecting portions 31a, 31b can be relatively moved in the horizontal direction with respect to the flange portions 32a, 32b. Therefore, even if the low-pressure turbine casing 31 thermally expands and the arrangement interval between the pair of protrusions 31a and 31b spreads in the horizontal direction, the pair of protrusions 31a and 31b are bearings via the pair of flanges 32a and 32b. The state which supports the stand 32 from below can be appropriately maintained.

FIG. 6A shows the state of the low pressure turbine 30 before the operation of the turbine equipment 100. 6B shows the state of the low pressure turbine 30 during operation of the turbine equipment 100. FIG.
In the low-pressure turbine 30 before operation shown in FIG. 6 (a), the low-pressure turbine casing 31 is not thermally expanded, and in the low-pressure turbine 30 during operation shown in FIG. 6 (b), the low-pressure turbine casing 31 is thermally expanded. ing.
When the low pressure turbine casing 31 thermally expands, the entire length in the direction of the axis X extends. Since the low pressure turbine casing 31 is fixed to the installation surface S, the centering beam 31c provided in the low pressure turbine casing 31 pushes out and moves the bearing stand 32 in the direction of the axis X, as shown in FIG. It will be in the state shown to 6 (b).

As shown in FIGS. 4A and 4B, the slide key groove 32 c formed in the bearing base 32 is a groove extending along the axis X. Further, on the upper surface of the base portion 33, a slide key 33a extending along the axis X and projecting upward is formed. A slide key 33 a formed on the upper surface of the base portion 33 is inserted into the slide key groove 32 c included in the bearing stand 32.
Therefore, the slide key groove 32c is a mechanism that prevents relative movement of the bearing stand 32 in the horizontal direction while allowing relative movement of the bearing stand 32 in the axial line X direction with respect to the base portion 33.

  As shown in FIG. 4 (b), when the vertical position of the bearing stand 32 rises due to the thermal expansion of the low pressure turbine casing 31, the vertical distance between the base portion 33 and the bearing stand 32 becomes long. The slide key groove 32 c of the bearing stand 32 is engaged with the slide key 33 a formed on the upper surface of the portion 33. Therefore, even if the low-pressure turbine casing 31 is thermally expanded, the horizontal relative movement of the bearing base 32 with respect to the base portion 33 remains blocked.

  As described above, the low-pressure turbine 30 of the present embodiment has the centering beam 31c included in the low-pressure turbine casing 31 when the low-pressure turbine casing 31 is thermally expanded and approaches the bearing stand 32 along the axis X. The bearing stand 32 is pushed out, and the bearing stand 32 moves relative to the base portion 33 in the direction of the axis X by the slide key groove 32c. Therefore, even when the low-pressure turbine casing 31 is thermally expanded and the length in the axis X direction is extended, the bearing base 32 can be moved to an appropriate position in the axis X direction to support the rotating shaft 60.

Next, a low pressure turbine 30 ′ of a comparative example of the present embodiment will be described with reference to FIGS. 7 and 8.
The low pressure turbine 30 of the present embodiment has a pair of projecting portions 31 a and 31 b provided in the low pressure turbine casing 31 disposed below the pair of flange portions 32 a and 32 b provided in the bearing stand 32. And a pair of projection parts 31a and 31b support bearing stand 32 from the lower part.

  On the other hand, the low pressure turbine 30 'of the comparative example has a pair of flanges 32'a, 32' provided with a bearing stand 32 'and a pair of protrusions 31'a, 31'b provided with a low pressure turbine casing 31'. It is disposed above b. The pair of flange portions 32'a and 32'b support the low-pressure turbine casing 31 'via the pair of projecting portions 31'a and 31'b.

As shown in FIG. 7, in the low pressure turbine 30 ′ of the comparative example, the low pressure turbine casing 31 ′, the base portion 33, and the bearing stand 32 ′ are respectively provided to the turbine pedestal 600 disposed above the condenser 500. It is arranged. As described above, the low pressure turbine casing 31 'and the bearing stand 32' are disposed on the turbine pedestal 600 because the lower surfaces of the pair of projecting portions 31'a and 31'b and the pair of flange portions 32'a and 32 ' b To accurately adjust the positional relationship with the upper surface.
Thus, in a comparative example, it installs in the common installation surface called the turbine mount 600, and the positional relationship of a lower surface of a pair of protrusion part 31'a, 31'b and a pair of flange part 32'a, 32'b upper surface Need to adjust.

FIGS. 8 (a) and 8 (b) are cross-sectional views of the bearing stand 32 'shown in FIG.
FIG. 8 (a) shows the state of the bearing stand 32 'before the operation of the turbine equipment. Prior to the operation of the turbine equipment, high-pressure steam is not supplied to the low-pressure turbine 30 ′, so the low-pressure turbine casing 31 ′ is not thermally expanded. The height of the upper surface of the pair of flange portions 32'a and 32'b of the bearing stand 32 'with respect to the turbine pedestal 600 is H3.

  On the other hand, FIG. 8B shows a state of the bearing stand 32 'during operation of the turbine equipment. During the operation of the turbine facility, the low-pressure turbine casing 31 'is thermally expanded because high-pressure steam is supplied to the low-pressure turbine 30'. Therefore, the total height of the low-pressure turbine casing 31 ′ extends upward in the vertical direction.

  When the overall height of the low pressure turbine casing 31 'is extended, the vertical position of the pair of protrusions 31'a and 31'b is increased as compared with before the operation of the turbine equipment. Even if the vertical positions of the pair of projecting portions 31'a and 31'b rise, the vertical positions of the pair of flange portions 32'a and 32'b do not change. Therefore, the height H3 of the upper surface of the pair of flange portions 32'a and 32'b of the bearing stand 32 'with respect to the turbine mount 600 shown in FIG. 8B is equal to the height H3 shown in FIG.

  As shown in FIG. 8B, when the vertical position of the pair of projecting portions 31′a and 31′b rises, the vertical position of the central axis of the low-pressure turbine casing 31 ′ also rises accordingly. The height from the turbine mount 600 is H4. The height H4 is higher than the height H3. Therefore, when the low pressure turbine casing 31 'shown in FIG. 8 (b) is thermally expanded, the central axis of the rotating shaft 60 and the central axis of the low pressure turbine casing 31 do not coincide with each other.

As described above, in the low pressure turbine 30 'of the comparative example, the position of the bearing base 32' supporting the rotary shaft 60 matches the central axis of the low pressure turbine casing 31 when the low pressure turbine casing 31 'is thermally expanded. It will be in the state of not doing. Therefore, the rotary shaft 60 is not properly supported by the bearing stand 32, and the clearance between the rotary shaft 60 and the seal member provided around the rotary shaft 60 in the low pressure turbine casing 31 'may be adversely affected. There is.
On the other hand, in the low pressure turbine 30 of the present embodiment, even when the low pressure turbine casing 31 is thermally expanded, the position of the bearing stand 32 supporting the rotating shaft 60 and the central axis of the low pressure turbine casing 31 coincide with each other. Maintained.

Moreover, as shown in FIG.8 (b), low pressure turbine 30 'of a comparative example is a pair of protrusion part 31'a, 31 to a pair of fastening bolt fastened by a pair of flange part 32'a, 32'b. There is a possibility that the 'b' contacts and an excessive load is applied to a pair of fastening bolts.
On the other hand, in the low pressure turbine 30 of the present embodiment, an excessive load is prevented from being applied to the pair of fastening bolts 31f, 31g fastened to the pair of flange portions 32a, 32b.

Further, the low-pressure turbine 30 ′ of the comparative example is installed on a common installation surface called the turbine mount 600, and the lower surfaces of the pair of projecting portions 31′a and 31′b and the upper surfaces of the pair of flange portions 32′a and 32′b. It is necessary to adjust the positional relationship with the
On the other hand, the low pressure turbine 30 of this embodiment is installed on a common installation surface of the turbine pedestal 600, and adjusts the positional relationship between the lower surfaces of the pair of projecting portions 31a and 31b and the upper surfaces of the pair of flanges 32a and 32b. There is no need.

Hereinafter, the operation and effects of the turbine equipment 100 of the present embodiment will be described.
According to the turbine equipment 100 of the present embodiment, a pair of projecting portions 31a and 31b protruding along the axis X on both sides sandwiching the axis X on one end side of the low pressure turbine casing 31 are disposed above The bearing stand 32 is supported from below via the flange portions 32a and 32b. Therefore, when the low pressure turbine casing 31 thermally expands during operation of the turbine equipment 100 and the central axis of the low pressure turbine casing 31 moves upward, the bearing stand 32 supported by the pair of projecting portions 31a and 31b accordingly. Also move upwards. Therefore, even when the low pressure turbine casing 31 is deformed by thermal expansion, the rotary shaft 60 and the central axis of the low pressure turbine casing 31 can be made to coincide with each other.

  Further, according to the turbine equipment 100 of the present embodiment, when the low pressure turbine casing 31 thermally expands and approaches the bearing base 32 along the axis X, the centering beam 31 c provided in the low pressure turbine casing 31 is The bearing stand 32 is pushed out, and the bearing stand 32 moves relative to the base portion 33 in the direction of the axis X by the slide key groove 32c. Therefore, even when the low-pressure turbine casing 31 is thermally expanded and the length in the axis X direction is extended, the bearing base 32 can be moved to an appropriate position in the axis X direction to support the rotating shaft 60.

Further, according to the turbine equipment 100 of the present embodiment, even if the low-pressure turbine casing 31 thermally expands and the arrangement distance between the pair of protrusions 31a and 31b spreads in the horizontal direction orthogonal to the axis X direction, the pair The pair of projecting portions 31a, 31b can be relatively moved in the horizontal direction with respect to the flange portions 32a, 32b. Therefore, even if the low-pressure turbine casing 31 thermally expands and the arrangement interval between the pair of protrusions 31a and 31b spreads in the horizontal direction, the pair of protrusions 31a and 31b are bearings via the pair of flanges 32a and 32b. The state of supporting the table 32 from below can be maintained properly.
Thus, according to the turbine equipment 100 of the present embodiment, even when the low-pressure turbine casing 31 is deformed due to thermal expansion, the rotating shaft 60 and the central axis of the low-pressure turbine casing 31 are aligned. The rotating shaft 60 can be supported by the bearing stand 32.

According to the turbine equipment 100 of the present embodiment, the first length W1 in the axis X direction of the pair of through holes 32d and 32e and the second length W2 in the horizontal direction orthogonal to the axis X direction are the pair of fastening bolts 31f, It is longer than the 31 g outer diameter W3. Therefore, when the pair of protrusions 31a and 31b move in the axis X direction due to thermal expansion during operation, the pair of protrusions 31a and 31b move relative to the pair of flange portions 32a and 32b formed in the bearing base 32 in the axis X direction. Similarly, when the pair of protrusions 31a and 31b move in the horizontal direction due to thermal expansion during operation, they move in the horizontal direction relative to the pair of flanges 32a and 32b formed on the bearing stand 32.
As described above, according to the turbine equipment 100 of the present embodiment, even if the pair of protrusions 31a and 31b move in the direction of the axis X or in the horizontal direction orthogonal thereto due to thermal expansion during operation, the pair of protrusions 31a and 31b Can properly maintain the state in which the bearing stand 32 is supported.

Other Embodiments
In the above description, the slide key groove 32 c is provided on the lower surface of the bearing stand 32, and the slide key 33 a is provided on the upper surface of the base portion 33.
For example, the slide key may be provided on the lower surface of the bearing stand 32 and the slide key groove may be provided on the upper surface of the base portion 33.

  In the above description, the low-pressure turbine 30 is provided with the low-pressure turbine casing 31 and the bearing stand 32. However, other modes may be used. For example, a support structure similar to that of the low pressure turbine 30 may be employed for the high pressure turbine 10, the intermediate pressure turbine, and the like.

DESCRIPTION OF SYMBOLS 1 Marine propulsion plant 10 High pressure turbine 20 Medium pressure turbine 30 Low pressure turbine 31 Low pressure turbine casing 31a, 31b Protrusion part (bearing stand support part)
31c Centering beam (extrusion section)
31d, 31e fastening holes 31f, 31g fastening bolts (fastening members)
31j steam inlet 32 bearing base 32a, 32b flange portion 32c slide key groove (moving mechanism)
32d, 32e through holes 32f, 32g slide base (sliding member)
33 Foundation 33a Slide key 50, 60 Rotating shaft 100 Turbine equipment S Installation surface

Claims (2)

A turbine casing which is installed on the installation surface and which accommodates therein a rotation axis extending along the axis;
A bearing base provided on one end side along the axis of the turbine casing and supporting the rotation shaft;
The turbine casing is provided with a bearing block supporting portion for supporting the bearing stand,
The bearing base is disposed above the bearing base support part and allows the relative movement of the bearing base support part in a horizontal direction perpendicular to the axial direction along the axis, and the installation surface A moving mechanism disposed above the base portion installed on the base and enabling relative movement in the axial direction with respect to the base portion ;
Wherein the turbine casing side of the bearing block supporting portion, turbine equipment that has a shape that is inclined downward from the top toward the pedestal from the turbine casing. The bearing stand supporting portion includes a pair of projecting portions protruding along the axis on both sides sandwiching the axis at one end side along the axis of the turbine casing.
A pair of through holes are formed in the pair of flanges disposed above the tip side of the pair of protrusions,
A pair of fastening holes are formed at a position facing the pair of through holes above the distal end side of the pair of projecting portions,
The turbine casing includes a pair of fastening members fastened to the pair of fastening holes in a state of being inserted into the pair of through holes.
The turbine equipment according to claim 1, wherein the first axial length of the through hole and the second horizontal length of the through hole are longer than the outer diameter of the fastening member.

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