This application is based upon and claims the benefit of priority from Japanese Patent Application No. 2013-050492, filed on Mar. 13, 2013; the entire contents of which are incorporated herein by reference.
Embodiments described herein relate generally to a steam turbine.
In order to improve a power generating efficiency in a power generating plant, a steam turbine installed in the power generating plant is also required to improve efficiency.
In each turbine stage, a pressure P1 of steam 350 at an inlet of the stationary blades 323 is reduced since the steam passes through the stationary blades 323, and the pressure P1 becomes a pressure P2 at an outlet of the stationary blades 323. At this time, the steam 350 expands and increases its volume, and at the same time, a steam outflow direction is changed to a rotational direction of the turbine rotor 340, resulting in that the steam 350 has a velocity energy in the circumferential direction.
By a reaction force obtained when the direction of the steam 350 is changed to a counter-rotational direction by the rotor blades 331, and also by a reaction force obtained when the pressure is reduced to a pressure P3 so that the steam further expands and increases its outflow velocity, the velocity energy in the circumferential direction is converted into a rotational torque.
Here, it is structurally essential to provide a predetermined gap between a static part such as the diaphragm inner ring 321 and a rotating part such as the turbine rotor 340. For this reason, a leakage steam 351 whose flow is divided from the steam 350 passes through a gap 360 between the diaphragm inner ring 321 and the turbine rotor 340, as illustrated in
The leakage steam 351 does not flow through the stationary blade cascade 320, so that the leakage steam 351 on which the predetermined change in the direction is not performed is directly jetted from a portion between the diaphragm inner ring 321 and the rotor blades 331 toward a main flow to interfere with the main flow, which results in generating a loss.
A difference between the pressure P2 and the pressure P3 in front of and at the rear of the rotor blades 331 becomes a force that pushes the rotor disk 341 including the rotor blades 331 toward a turbine rotor axial direction. This force has a substantial magnitude in the entire steam turbine configured by multi-turbine stages. The force is normally cancelled by a thrust bearing with large diameter.
Among conventional steam turbines, one that includes a configuration different from that of the above-described steam turbine 300 has also been considered.
As illustrated in
Here,
Generally, a pressure between the rotor blades 331 becomes high on a pressure side 332 (pressure surface side), and it becomes low on a suction side 333 (suction surface side). Further, a driving force 370 of secondary flow vortex acts from a position with high pressure to a position with low pressure. Normally, a centrifugal force obtained when a steam flows between the rotor blades 331 while a direction thereof is changed acts so as to counter the driving force 370. Meanwhile, in the vicinity of an annular wall surface 334 on the root side, a flow velocity of the steam is significantly lowered due to a friction between the steam and the wall surface 334. Accordingly, the centrifugal force is lowered and cannot counter the driving force 370, resulting in that the secondary flow vortex is generated. The secondary flow vortex is classified into a horseshoe vortex 371 generated at a leading edge portion of the rotor blade 331 and developed along the suction side 333, and a passage vortex 372 developed while being drawn from the pressure side 332 toward the suction side 333 by the driving force 370. Both of the vortices sterically cross each other at a rear flow part of the suction side 333, and generate a large loss while curling up in a blade height direction.
As described above, when the steam passage 342 is not formed on the rotor disk 341 in the conventional steam turbine, there is generated the loss due to the interference of the steam 351 leaked between the diaphragm inner ring 321 and the turbine rotor 340 with the main flow. Further, the thrust bearing with large diameter is required to support the force generated due to the difference between the pressure P2 and the pressure P3 in front of and at the rear of the rotor blades 331, which increases manufacturing cost.
On the other hand, when the steam passage 342 is formed on the rotor disk 341 in the conventional steam turbine, it is possible to suppress the loss due to the interference described above, and to downsize the thrust bearing. However, the amount of steam that flows into the rotor blades is reduced, so that the blade height of each rotor blade set based on the flow rate of the steam becomes low. For this reason, the secondary flow vortex occupies a large area in the blade height direction, resulting in that the influence of loss caused by the secondary flow vortex becomes large.
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
As illustrated in
The turbine rotor 30 includes, in a turbine rotor axial direction, a plurality of stages of rotor disks 31 projected to an outside in a radial direction along a circumferential direction. In each of the rotor disks 31, a plurality of rotor blades 40 inserted from the circumferential direction are implanted in the circumferential direction to form a rotor blade cascade 41.
In the inside of the inner casing 20, a diaphragm outer ring 50 is provided along the circumferential direction. In the inside of the diaphragm outer ring 50, a diaphragm inner ring 51 is provided along the circumferential direction.
A plurality of stationary blades 52 (nozzles) are supported in the circumferential direction between the diaphragm outer ring 50 and the diaphragm inner ring 51 to form a stationary blade cascade 53. The stationary blade cascade 53 is provided on an upstream side of each rotor blade cascade 41, and in the turbine rotor axial direction, a plurality of stages of alternately arranged stationary blade cascades 53 and rotor blade cascades 41 are provided. Further, the stationary blade cascade 53 and the rotor blade cascade 41 at an immediately downstream of the stationary blade cascade 53 form one turbine stage.
Although explanation will be made later in detail, on each of a predetermined turbine stage and a turbine stage on a downstream side of the predetermined turbine stage, there is formed a steam passage 60 through which a leakage steam 101 flown downstream between the diaphragm inner ring 51 and the turbine rotor 30 is led from an upstream side to a downstream side of the rotor disk 31.
On the diaphragm inner ring 51 on a side opposing the turbine rotor 30, a sealing part 70 is provided. With this configuration, the leakage of steam from a portion between the diaphragm inner ring 51 and the turbine rotor 30 to the downstream side is suppressed.
Further, in the steam turbine 10, a steam inlet pipe 80 is provided to penetrate through the outer casing 21 and the inner casing 20. An end portion of the steam inlet pipe 80 is connected to communicate with a nozzle box 81. Note that stationary blades 52 of a first stage are provided at an outlet of the nozzle box 81.
On an inside of the inner casing 20 and the outer casing 21 on an outside of a position at which the nozzle box 81 is provided (on an outside in a direction along the turbine rotor 30, and on a left side of the nozzle box 81 in
Next, the steam passage 60 will be described in detail.
In
As illustrated in
As illustrated in
Note that in this case, although the steam passage 60 formed on the turbine stage 90b is described, the steam passage 60 with the same configuration is provided also on a turbine stage at a downstream of the turbine stage 90b.
Here, explanation will be made on a boundary between the turbine stage 90a including no steam passage 60 and the turbine stage 90b including the steam passage 60.
As illustrated in
By a reaction force obtained when the direction of the steam 100 is changed to a counter-rotational direction by the rotor blades 40a, and by a reaction force obtained when the pressure is reduced to P3 so that the steam further expands and increases its outflow velocity, the velocity energy in the circumferential direction is converted into a rotational torque. Accordingly, it becomes structurally essential to provide a gap 110 between a static part such as the diaphragm inner ring 51a and a rotating part such as the turbine rotor 30. Note that the above-described operation is also provided to another turbine stage 90b in the same manner.
By providing the gap 110 in the turbine stage 90a including no steam passage 60, a leakage steam 101 whose flow is divided from the steam 100 passes through the gap 110 between the diaphragm inner ring 51a (sealing part 70a) and the turbine rotor 30, as illustrated in
Generally, a flow rate g of the leakage steam 101 is represented by a function of flow coefficient C, steam density ρ, annular leakage area A and stationary blade pressure ratio P1/P2, as represented by an equation (1). The flow coefficient C is also represented by a function of the stationary blade pressure ratio P1/P2. Here, the annular leakage area A is a cross-sectional area of annular gap 110 formed between a seal fin of the sealing part 70a and the turbine rotor 30.
g=f(C,ρ,A,P1/P2) equation (1)
Here, the flow rate g of the leakage steam 101 is set by assuming that the stationary blade pressure ratio P1/P2 and the annular leakage area A in the respective turbine stages are equal. In this case, as the steam proceeds to the downstream turbine stages, the pressure is lowered so that the steam density ρ is lowered, resulting in that the flow rate g of the leakage steam 101 is reduced. Specifically, as the steam proceeds to the downstream turbine stages, a ratio of the flow rate g of the leakage steam 101 to the total flow rate G of steam that flows through the turbine stage (g/G) is reduced. Note that the total flow rate G of steam includes the flow rate g of the leakage steam 101.
As illustrated in
As illustrated in
Here, since the whole amount of the leakage steam 101 is jetted into the steam 100 as described above, the flow rate of steam that passes through the rotor blades is increased, when compared to a case where the steam passage 60 is provided. For this reason, it is possible to increase the blade height of each rotor blade in response to the increase in the flow rate of the steam. In the present embodiment, the blade height of each rotor blade is increased in response to the fact that the flow rate is increased by the amount of the leakage steam 101 in the turbine stage 90a including no steam passage 60.
Here, the result from the turbine stage of first stage to the turbine stage 90a (described as last stage in
As the blade height of each rotor blade becomes higher, a proportion of secondary flow vortex with respect to the blade height is reduced, so that the reduction of efficiency caused by the secondary flow vortex is suppressed. Specifically, as illustrated in
As illustrated in
From the above description, the following findings regarding the boundary between the turbine stage 90a including no steam passage 60 and the turbine stage 90b including the steam passage 60, are obtained.
It is preferable that the steam passage 60 is not formed on a turbine stage including rotor blades each having a blade height lower than the blade height H at which the interference loss and the benefit brought by increasing the blade height of each rotor blade (efficiency increased in accordance with the increase in the blade height of each rotor blade) are cancelled. Here, the description in which the interference loss and the benefit brought by increasing the blade height of each rotor blade are cancelled means that a subtraction between the interference loss and the benefit brought by increasing the blade height of each rotor blade becomes 0.
In other words, the steam passage 60 is preferably formed on a turbine stage including rotor blades each having a blade height equal to or more than the blade height H at which the interference loss and the benefit brought by increasing the blade height of each rotor blade are cancelled.
Here, a threshold value of the blade height H is changed depending on a variation of various design parameters. Main causes thereof will be described hereinafter.
The flow rate g of the leakage steam 101 is changed depending on a shape of flow path through which the leakage steam 101 flows and the stationary blade pressure ratio P1/P2. For this reason, in the turbine stage 90a including no steam passage 60 illustrated in
It can be considered that the higher a degree of reaction, the smaller the interference loss when the leakage steam 101 is jetted. Here, the degree of reaction corresponds to a proportion of rotor blade pressure ratio P2/P3 with respect to a stage pressure ratio P1/P3. Specifically, when the degree of reaction is high, the proportion of rotor blade pressure ratio becomes large.
By making a cross-sectional area of flow path when the steam flows out of the rotor blades 40a to be smaller than a cross-sectional area of flow path when the steam flows into the rotor blades 40a, the pressure of the steam 100 is reduced while accelerating the steam 100. Specifically, even if the leakage steam 101 which is not normally accelerated and whose direction is not normally changed between the stationary blades 52a, is jetted from an upstream side of roots of the rotor blades 40a, as the degree of reaction becomes higher, the leakage steam 101 reduces its pressure and is accelerated in the rotor blades 40a. For this reason, a proportion of energy retrieved as a rotational force in the rotor blades 40a becomes high.
Here, there is conducted a study regarding the blade height of each rotor blade at which the interference loss and the benefit brought by increasing the blade height of each rotor blade (efficiency increased in accordance with the increase in the blade height of each rotor blade) are cancelled, while changing the degree of reaction under the flow rate of practical leakage steam 101 in the turbine stages each including no steam passage 60.
As illustrated in
Here, as a steam turbine including rotor blades each having a low blade height such as a blade height of rotor blade of lower than 30 mm, there can be cited, for example, a high-pressure turbine to which high-pressure and high-density steam is supplied, or the like. Further, as the steam turbine, there can be cited a high-pressure turbine applied to a combined cycle and to which a steam with small flow rate generated by exhaust gas in a gas turbine is supplied, or the like. Concretely, the steam turbine 10 of the present embodiment can be applied to, for example, a high-pressure turbine applied to a high-efficiency combined cycle using natural gas in which CO2 emission is smaller than that of coal and heavy oil.
Note that in this case, an example in which the configuration of the present embodiment is applied to the high-pressure turbine is shown, but, the present invention is not limited to these. The steam turbine 10 of the present embodiment can be applied to, for example, the steam turbine including the rotor blades each having the low blade height such as the blade height of lower than 30 mm as described above.
Next, an operation of the steam turbine 10 will be described with reference to
The steam 100 that passes through the steam inlet pipe 80 and flows into the nozzle box 81 is jetted toward the rotor blades 40 from the stationary blades 52 provided at the outlet of the nozzle box 81.
In the turbine stage including no steam passage 60, the leakage steam 101 whose flow is divided from the steam 100 passes through the gap 110 between the diaphragm inner ring 51 (sealing part 70) and the turbine rotor 30. Further, the whole amount of the leakage steam 101 is jetted into the steam 100 being the main flow, from a portion between the diaphragm inner ring 51 and the rotor blades 40.
The leakage steam 101 jetted into the steam 100 interferes with the flow of the steam 100, and flows into portions between the rotor blades 40 together with the steam 100. The turbine rotor 30 is rotated with a rotational force given by the steam 100 and the leakage steam 101 flown into the portions between the rotor blades 40.
Meanwhile, in the turbine stage including the steam passage 60, the leakage steam 101 whose flow is divided from the steam 100 passes through the gap 110 between the diaphragm inner ring 51 (sealing part 70) and the turbine rotor 30. Further, a large portion of the leakage steam 101 passes through the steam passage 60, and flows out to a portion between the rotor blades 40 or the rotor disk 31 and the diaphragm inner ring 51 in the turbine stage on the downstream side. The remaining leakage steam 101 is jetted into the steam 100 from a portion between the diaphragm inner ring 51 and the rotor blades 40.
Note that since the large portion of the leakage steam 101 passes through the steam passage 60, a differential pressure in front of and at the rear of the rotor blades 40 becomes small. Accordingly, a force applied to the thrust bearing also becomes small, so that the diameter of the thrust bearing can be reduced.
The leakage steam 101 jetted into the steam 100 interferes with the flow of the steam 100, and flows into portions between the rotor blades 40 together with the steam 100. In this case, since the flow rate of the leakage steam 101 jetted into the steam 100 is small, the interference loss is small. Further, the turbine rotor 30 is rotated with a rotational force given by the steam 100 and the leakage steam 101 flown into the portions between the rotor blades 40.
The steam 100 (including the leakage steam 101) passed through a turbine stage of final stage passes through an exhaust passage (not illustrated) to be exhausted to the outside of the steam turbine 10.
As described above, according to the steam turbine 10 of the first embodiment, since there are provided the turbine stages each including no steam passage 60 and the turbine stages each including the steam passage 60, it is possible to reduce the loss caused in accordance with the flow of steam and to realize the improvement of efficiency.
Here, in the steam turbine 10 of the first embodiment described above, the rotor blades 40 implanted in the rotor disk 31 by being inserted from the circumferential direction are exemplified, but, the configuration of the rotor blades 40 is not limited to this.
As illustrated in
In concave implanting grooves 32 between the blade wheels 33, the rotor blades 40 are inserted from the upstream side of the turbine rotor axial direction. The rotor blade cascade 41 is configured by the plurality of rotor blades 40 implanted in the implanting grooves 32 formed in the circumferential direction.
The implant part 43 has a fitting concavo-convex shape, and the concavo-convex shape corresponds to a shape of the implanting groove 32 of the rotor disk 31. The fitting concavo-convex shape prevents the rotor blade 40 from coming out of the rotor disk 31 to the outside in the radial direction.
Further, on a downstream end of the blade wheel 33, there is provided a projecting portion (not illustrated) projecting to the implanting groove 32 side and preventing the implant part 43 of the rotor blade 40 from coming out to the downstream side, for example. For this reason, even when a load to the downstream side is applied to the rotor blade 40, the rotor blade 40 does not come out of the implanting groove 32.
As illustrated in
Here, in the turbine stage including no steam passage 60, no gap is formed between the inside diameter side end face 43a of the implant part 43 and the bottom face 32a of the implanting groove 32. Further, when the gap between the inside diameter side end face 43a of the implant part 43 and the bottom face 32a of the implanting groove 32 is formed in the turbine stage including no steam passage 60, the gap is sealed.
Note that the steam passage 60 is not limited to the above, and it may also be configured by a through hole formed on the rotor disk 31, for example.
A configuration of the steam turbine 11 of the second embodiment is the same as that of the steam turbine 10 of the first embodiment except for a configuration of arrangement in the circumferential direction of the rotor blades 40. Accordingly, the configuration of arrangement in the circumferential direction of the rotor blades 40 will be mainly described here.
As illustrated in
As illustrated in
Accordingly, it is possible to control a distribution of degree of reaction in the blade height direction. By locally increasing the degree of reaction on the root side of the rotor blades 40, it is possible to suppress the interference loss. For this reason, the efficiency can be improved even if a turbine stage including no steam passage 60 is extended to a turbine stage with higher blade height of each rotor blade.
Here, the configuration of the rotor blade 40 described above can also be applied to the stationary blade 52. Similar to the configuration illustrated in
As illustrated in
A configuration of the steam turbine 12 of the third embodiment is the same as that of the steam turbine 10 of the first embodiment except for a shape of the rotor blade 40. Accordingly, the shape of the rotor blade 40 will be mainly described here.
As illustrated in
By curving the rotor blade 40 as above, it is possible to intentionally control the distribution of pressure in the blade height direction. For example, in the rotor blade 40 curved so as to make the center portion in the blade height project toward the suction side 47, it is possible to intentionally generate a velocity in a radial direction directed from the center of blade to the root side and the tip side. Accordingly, a force that presses the flow of steam, against an annular wall surface side on the root side at which a curling of secondary flow is strong due to the operation of centrifugal force, in particular is obtained. For this reason, it is possible to suppress the development of secondary flow vortex.
Specifically, a pressure P3 at an outlet of the rotor blades 40 is locally lowered on the root side to increase a rotor blade pressure ratio (P2/P3) between a pressure P2 at an inlet of the rotor blades 40 and the pressure P3 at the outlet of the rotor blades 40, thereby increasing the degree of reaction on the roots of the rotor blades 40. Accordingly, it is possible to control the distribution of degree of reaction in the blade height direction in the rotor blades 40.
Here, the configuration of the rotor blade 40 described above can also be applied to the stationary blade 52. Similar to the configuration illustrated in
By curving the stationary blade 52 as above, it is possible to intentionally control the distribution of pressure in the blade height direction, similar to the above-described rotor blade 40. For example, in the stationary blade 52 curved so as to make the center portion in the blade height project toward the suction side, it is possible to intentionally generate a velocity in a radial direction directed from the center of blade to the root side and the tip side. Accordingly, a force that presses the flow of steam against the diaphragm inner ring 51 side and the diaphragm outer ring 50 side can be controlled. For this reason, it is possible to change a distribution in the blade height direction of the pressure P2 at the inlet of the rotor blades 40.
Note that the steam turbine of the present embodiment can also be designed to have a configuration in which the configuration of the second embodiment is added to the configuration of the third embodiment.
According to the embodiments described above, it becomes possible to reduce the loss caused in accordance with the flow of steam, and to realize the improvement of efficiency.
While certain embodiments have been described, these embodiments have been presented by way of example only, and are not intended to limit the scope of the inventions. Indeed, the novel embodiments described herein may be embodied in a variety of other forms; furthermore, various omissions, substitutions and changes in the form of the embodiments described herein may be made without departing from the spirit of the inventions. The accompanying claims and their equivalents are intended to cover such forms or modifications as would fall within the scope and spirit of the inventions.
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