Steam turbine

CROSS REFERENCES TO RELATED APPLICATIONS

This application is based upon and claims the benefit of priority from the prior Japanese Patent Application No. 2007-215769, filed in the Japanese Patent Office on Aug. 22, 2007, the entire content of which is incorporated herein by reference.

BACKGROUND OF THE INVENTION

The present invention relates to a steam turbine and, more particularly, it relates to steam turbine designed to achieve a high efficiency by improving the nozzle box arrangement in the steam inlet section.

Generally, a steam turbine comprises a rotatable turbine rotor, moving blade stages, a casing and nozzle diaphragms. The casing and the nozzle diaphragms constitute as a stationary section. The rotor is rotatably provided in the casing. The nozzle diaphragms are arranged substantially coaxially with the turbine rotor, supported on the casing. The moving blade stages are provided on the turbine rotor so as to rotate together with the turbine rotor. Each of the moving blade stages comprises a plurality of moving blades arranged in the circumferential direction of the turbine rotor.

Each of the nozzle diaphragms comprises a plurality of turbine nozzles arranged in the circumferential direction relative to the turbine rotor and arranged at the upstream side of one of the moving blade stage. A pair of a nozzle diaphragm and a moving blade stage provided at the upstream side of the nozzle diaphragm forms a turbine stage. An ordinary steam turbine has a plurality of turbine stages.

More specifically, nozzle diaphragms, a turbine rotor and moving blade stages are substantially coaxially arranged in the casing. The steam led to a nozzle diaphragm passes through a plurality of turbine nozzles of the nozzle diaphragm and change its flowing direction. Then, the steam flowing out from the nozzle diaphragm is led to a moving blade portion of a moving blade stage that forms a pair with the nozzle diaphragm. The steam drives the moving blade stage and the turbine rotor as it passes between the plurality of moving blades of the moving blade stage.

As pointed out above, an ordinary steam turbine has a plurality of turbine stages. The steam that passes through one turbine stage is led to an adjacent turbine stage. More specifically, a plurality of moving blade stages are provided on the turbine rotor, separated from each other in the axial direction. The nozzle diaphragms are arranged in the casing so as to be placed between the moving blade stages in the axial direction of the turbine rotor. The moving blade portions of a plurality of moving blade stages and the turbine nozzle portions of a plurality of nozzle diaphragms form a steam passage.

Especially, for a high pressure turbine, a nozzle box is provided in the casing to lead the steam introduced in the casing to the turbine nozzles of the first stage, which constitute as a part of the steam passage. Known nozzle boxes include one described in Japanese Patent Application Laid-Open Publication No. 03-066484, the entire content of which is incorporated herein by reference.

Like the casing, the nozzle box constitutes as the stationary section. The nozzle box comprises a plurality of turbine nozzles of the first stage, which are arranged in the circumferential direction, provided at the outlet side of the nozzle box. In other words, the nozzle box and the nozzle diaphragm of the first stage (e.g. the first stage nozzle diaphragm) are arranged integrally and the steam introduced into the nozzle box is led to the steam passage, that includes the first moving blade stage that forms a pair with the first stage nozzle diaphragm provided with the nozzle box.

FIGS. 5 and 6 are schematic axial cross-sectional views of a known steam turbine having a nozzle box. FIG. 5 is a schematic axial cross-sectional view along a vertical direction and FIG. 6 is a schematic axial cross-sectional view along an angle inclined relative to the vertical direction by 45°.

The steam turbine 1 has a casing 2, a turbine rotor 3 rotatably arranged in the casing 2, a nozzle diaphragms 4a1, 4a2, 4a3, . . . that are rigidly secured to the casing 2. The casing 2 includes an outer casing 2a and an inner casing 2b.

A plurality of moving blade stages 3a1, 3a2, 3a3, . . . are arranged on the turbine rotor 3, which is a rotating section of the steam turbine 1, in the axial direction from the upstream side to the downstream side. Each of the moving blade stages 3a1, 3a2, 3a3 has a plurality of moving blades, the plurality of moving blades of the moving blade stages being denoted respectively by 3b1, 3b2, 3b3, . . . , and rotating force is generated as steam flows, passing through between the rotors 3b1, 3b2, 3b3, . . . .

Nozzle diaphragms 4a1, 4a2, 4a3, . . . that are supported by the inner casing 2b are arranged between the moving blade stages 3a1, 3a2, 3a3, . . . such that they are substantially coaxial and separated from each other in the axial direction. A pair of the nozzle diaphragms 4a1, 4a2, 4a3, . . . and the moving blade stages 3a1, 3a2, 3a3, . . . , respectively, constitutes a turbine stage. A plurality of turbine nozzles 4b1, 4b2, 4b3, . . . are provided in the circumferential direction, respectively, with the nozzle diaphragms 4a1, 4a2, 4a3, . . . .

The nozzle diaphragms 4a1, 4a2, 4a3, . . . are supported by the casing 2 so as to constitute a stationary section of the steam turbine 1. The steam flow flowing through between the plurality of nozzle blades 4b1, 4b2, 4b3 arranged in the circumferential direction is changed its flowing direction so as to be led to the moving blades 3b1, 3b2, 3b3, . . . of the moving blade stages 3a1, 3a2, 3a3, . . . of the pairs. The flow path of the steam including the portions of the turbine nozzles 4b1, 4b2, 4b3, . . . of the nozzle diaphragms 4a1, 4a2, 4a3, . . . and the portions of the moving blades 3b1, 3b2, 3b3, . . . of the moving blade stages 3a1, 3a2, 3a3 constitute as steam passage 8. The steam led to the steam turbine 1 flows through the steam passage 8 from an upstream side to a downstream side.

The steam turbine 1 is provided with a steam inlet pipe 7 and a nozzle box 5 that constitutes as members for introducing steam into the steam passage 8. The nozzle box 5 is a pressure vessel that deals with high temperature and high pressure steam. An inlet section of the nozzle box 5 is connected to the steam inlet pipe 7. A steam outlet section, namely, outlet section, of the nozzle box 5 is integrally provided with the first stage nozzle diaphragm 4a1 and the plurality of turbine nozzles 4b1 that are arranged in the circumferential direction.

The nozzle box 5 is rigidly secured to the casing 2 by a support member 6 arranged on the inner casing 2b. The plurality of first stage turbine nozzles 4b1, integrally arranged in the circumferential direction at the outlet section, serves as the first stage nozzle diaphragm 4a1. The nozzle box 5 is arranged substantially coaxial with the turbine rotor 3.

Thus, the steam led into the nozzle box 5 from the steam inflow pipe 7 is then led to the first stage nozzle diaphragm 4a1 that operates as steam passage 8. The steam led to the steam passage 8 expands as it passes between the turbine nozzles 4b1, 4b2, 4b3, . . . and the moving blades 3b1, 3b2, 3b3, . . . and the thermal energy it has is converted into kinetic energy to drive the moving blade stages 3a1, 3a2, 3a3, . . . and the turbine rotor 3 to rotate.

Note that the support member 6 is a member for supporting the nozzle box 5 in the inner casing . The support member 6 is not arranged entirely along the nozzle box 5 in the circumferential direction as seen in FIG. 6.

Therefore, the pressure of the space around the nozzle box 5 (e.g. a space between the inner casing 2band the turbine rotor 3) is substantially equal to the pressure of the steam passage 8 near the outlet of the first moving blade stage 3a1.

The steam conditions such as the temperature and the pressure of steam flowing into the steam turbine 1 are raised, the pressure of the steam flowing out from the first moving blade stage 3a1 is raised, and then the pressure in a space between the inner casing 2b and the turbine rotor 3 is also raised. Thus, the pressure applied to the internal casing 2b of the casing 2 is increased when applying the high pressure and high temperature steam to the steam turbine 1.

Therefore, when the pressure of the steam supplied to the steam turbine 1 is specifically raised, particularly the inner casing 2b of the casing 2 has to structurally withstand the force applied with the pressure. Expensive material such as Ni alloy may have to be used as the material of the inner casing 2b in consideration of the thermal resistance of the steam turbine 1 when the temperature is raised among the steam conditions. These would result in higher manufacturing cost.

BRIEF SUMMARY OF THE INVENTION

An object of the present invention is to provide a steam turbine that can reduce force applied to the casing 2.

According to the present invention, there is provided a steam turbine comprising: a stationary section that includes a casing; a turbine rotor that includes a plurality of moving blade stages arranged in an axial direction, each of the moving blade stages being provided with a plurality of moving blades arranged in a circumferential direction, and rotatably provided in the casing; a plurality of nozzle diaphragms, wherein each of the nozzle diaphragms having a plurality of turbine nozzles arranged in the circumferential direction, provided substantially coaxially with the turbine rotor by being secured to the stationary section; and a nozzle box supported on the stationary section, wherein the nozzle box is arranged at an upstream side of the moving blade stages substantially coaxially with the turbine rotor so as to lead steam flowing toward the turbine moving blades, wherein the nozzle box holds at least two stages of the nozzle diaphragms.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and other features and advantages of the present invention will become apparent from the discussion hereinbelow of specific, illustrative embodiments thereof presented in conjunction with the accompanying drawings, in which:

FIG. 1 is a schematic axial cross-sectional view of the first embodiment of steam turbine according to the present invention taken along a plane inclined by 45° from the vertical direction;

FIG. 2 is a schematic axial cross-sectional view of a modified embodiment of the first embodiment taken along a plane inclined by 45° from the vertical direction;

FIG. 3 is a schematic axial cross-sectional view of another modified embodiment of the first embodiment taken along a plane inclined by 45° from the vertical direction;

FIG. 4 is a schematic axial cross-sectional view of yet another modified embodiment of the first embodiment taken along a plane inclined by 45° from the vertical direction;

FIG. 5 is a vertical schematic axial cross-sectional view of a known steam turbine along a vertical direction; and

FIG. 6 is a schematic axial cross-sectional view of the known steam turbine of FIG. 5 along a direction inclined by 45° as to a vertical direction.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Now, the present invention will be described in greater detail by referring to the accompanying drawings that illustrate preferred embodiments of the invention.

FIG. 1 is a schematic axial cross-sectional view of the first embodiment of steam turbine according to the present invention taken along a plane inclined by 45° from the vertical direction. In FIG. 1, the components same as those of the known steam turbine shown in FIGS. 5 and 6 are denoted respectively by the same reference symbols and will not be described any further unless necessary.

The steam turbine 1 of this embodiment has a casing 2, a turbine rotor 3 rotatably arranged in the casing 2 and nozzle diaphragms 4a1, 4a2, 4a3, . . . rigidly secured to the casing 2. The casing 2 includes an outer casing 2a and an inner casing 2b.

Nozzle diaphragms 4a1, 4a2, 4a3, . . . that are supported by the inner casing 2b are arranged between the moving blade stages 3a1, 3a2, 3a3, . . . such that they are substantially coaxial with the turbine rotor 3 and separated from each other in the axial direction. A pair of the nozzle diaphragms 4a1, 4a2, 4a3, . . . and the moving blade stages 3a1, 3a2, 3a3, . . . , arranged adjacent to at a downstream side of the nozzle diaphragms respectively, constitute a turbine stages. A plurality of turbine nozzles 4b1, 4b2, 4b3, . . . are provided in the circumferential direction, respectively with the nozzle diaphragms 4a1, 4a2, 4a3, . . . .

The nozzle diaphragms 4a1, 4a2, 4a3, . . . are supported by the casing 2 so as to constitute a stationary section of the steam turbine 1. The steam flow flowing through between the plurality of turbine nozzles 4b1, 4b2, 4b3, . . . , arranged in the circumferential direction, is changed its direction so as to be led to the moving blades 3b1, 3b2, 3b3, . . . of the adjacently arranged moving blade stages 3a1, 3a2, 3a3, . . . of the pairs. The flow path of the steam including the portions of the turbine nozzles 4b1, 4b2, 4b3, . . . of the nozzle diaphragms 4a1, 4a2, 4a3, . . . and the portions of the moving blades 3b1, 3b2, 3b3, . . . of the moving blade stages 3a1, 3a2, 3a3 constitute as a steam passage 8. The steam led to the steam turbine 1 flows through the steam passage 8 from an upstream side to a downstream side.

A shaft sealing device 12 is provided between the turbine rotor 3 and the inner casing 2b to seal the shaft so as to prevent steam in the vicinity of the turbine rotor 3 from leaking to the space outside the inner casing 2b. The shaft sealing device 12 comprises a main body and a plurality of packing heads that circumferentially engage with the main body.

An anti-leakage steam seal 11 is arranged between the first stage nozzle diaphragm 4a1 and the first moving blade stage 3a1. The anti-leakage steam seal 11 reduces the flow of steam leaking from the steam passage 8 between the first stage nozzle diaphragm 4a1 and the adjacently arranged moving blade stage 3a1.

The steam turbine 1 is provided with a nozzle box 5 that introduces steam into the steam passage 8. The nozzle box 5 is secured to the inner casing 2b in the space 10 between the turbine rotor 3 and the inner casing 2b, substantially coaxial with the turbine rotor 3. The nozzle box 5 constitutes as a stationary section of the steam turbine 1.

The nozzle box 5 is a pressure vessel that deals with high temperature and high pressure steam. Like the known steam turbine shown in FIG. 5, a steam inlet pipe (not shown) is connected to the steam inlet section of the nozzle box 5.

At the outlet section of the nozzle box 5, namely a steam outlet section of the nozzle box 5, constitutes as part of the steam passage 8, a plurality of first stage turbine nozzles 4b1 are arranged in the circumferential direction. In other words, the first stage nozzle diaphragm 4a1 is structurally integrally provided at the outlet section of the nozzle box 5.

The outer peripheral side member of the nozzle box 5 extends to the downstream side in the axial direction. A hook section is provided in the axial direction at the downstream side of the extended outer peripheral side member of the nozzle box 5. The hook section is engaged with the second stage nozzle diaphragm 4a2. A plurality of second stage turbine nozzles 4b2 are arranged in the circumferential direction on the second stage nozzle diaphragm 4a2. The second stage turbine nozzles 4b2 are secured to the nozzle box 5, having the second stage nozzle diaphragm 4a2 therebetween.

In other words, the nozzle box 5 holds at least two stages of the nozzle diaphragms 4a1, 4a2, 4a3, . . . in this embodiment.

Thus, the steam led from the steam inlet pipe 7 into the nozzle box 5 is then led to the steam passage 8 from the outlet section of the nozzle box 5. The steam led to the steam passage 8 expands as it passes through between the turbine nozzles 4b1, 4b2, 4b3, . . . and the moving blades 3b1, 3b2, 3b3, . . . and converts its thermal energy into kinetic energy so as to drive the moving blade stages 3a1, 3a2, 3a3, . . . and the turbine rotor 3.

With this arrangement, the pressure in a space 10 between the turbine rotor 3 and the inner casing 2b, where the nozzle box 5 is arranged, (e.g. a space 10 around the nozzle box 5) is substantially equal to the pressure of the steam passage 8 at the downstream side of the second moving blade stage 3a2 because the outer peripheral side member of the nozzle box 5 extends to the second stage nozzle diaphragm 4a2.

Therefore, according to this embodiment, the pressure in the space 10 around the nozzle box 5 can be reduced, when compared to the conventional steam turbine having a nozzle box 5 provided only with the first stage nozzle diaphragm 4a1 as shown in FIG. 5.

As a result, the force acting on the casing 2, particularly the inner casing 2b, can be reduced. Thus, the steam turbine 1 may be made light weight and the material cost of the steam turbine 1 can be reduced.

The second stage nozzle diaphragm 4a2 is provided separately with the nozzle box 5 in this embodiment. The nozzle diaphragm 4a2 may alternatively be provided integrally with the nozzle box 5 like the first stage nozzle diaphragm 4a1. In this case, the outer peripheral member of the nozzle box 5 extending downstream side and the outer ring of the nozzle diaphragm 4a2 are structurally integrated with each other.

In this embodiment, the inner casing 2b, as a stationary section, may be rigidly secured to the nozzle box 5 by a bulkhead 9 as shown in FIG. 1. More specifically, the bulkhead 9 is arranged along the entire periphery of the nozzle box 5 in the circumferential direction, as a sealing that divides the space around the nozzle box 5, which is formed between the turbine rotor 3 and the inner casing 2b, into two spaces including an inner space 10a and an outer space 10b. The inner space 10a is located inside relative to the steam passage 8 and the outer space 10b is located outside relative to the steam passage 8. In other words, the inner space 10a means a space including an inner peripheral side (inner side) of the nozzle box 5, and the outer space 10b means a space including at least an outer peripheral side (outer side) of the nozzle box. The outer peripheral side of the nozzle box 5 includes outer peripheral side of the steam passage 8. With this arrangement, the flow of steam between the inner space 10a and the outer space 10b can be blocked by the bulkhead 9 that is a sealing arranged between the nozzle box 5 and the stationary section other than the nozzle box 5. Further advantages with the bulkhead 9 are described below.

As described above, the anti-leakage steam seal 11 is arranged between the first stage nozzle diaphragm 4a1 (e.g. the outlet section of the nozzle box 5) and the first moving blade stage 3a1 to reduce leakage of steam from steam passage 8.

However, when the difference between the pressure in the steam passage 8 at the outlet section of the first stage nozzle diaphragm 4a1 and the pressure in the space 10 around the nozzle box 5, which is the pressure in the steam passage 8 at the downstream of the second moving blade stage 3a2 in FIG. 1, is large, the steam flowing out from the first stage nozzle diaphragm 4a1 arranged at the nozzle box 5 may bypasses to the downstream side via the space 10 around the nozzle box 5, regardless of the effect of the anti-leakage steam seal 11.

The steam bypassing the space 10 around the nozzle box 5 cannot be efficiently utilize in the steam turbine 1 because it is leaked from the steam passage 8 and bypasses to the downstream side. In other words, as the rate of steam leaks out through the anti-leakage steam seal 11 rises, the efficiency of the steam turbine 1 decreases. This problem becomes significant in a turbine having a large degree of reaction where the pressure difference between the outlet of the first stage turbine nozzles 4b1 and the outlet of the first moving blade stage 3a1 is large.

However, in this embodiment as shown in FIG. 1, the bulkhead 9, as the sealing, is arranged around the nozzle box 5 to divide the space 10 around the nozzle box 5 into the inner space 10a and the outer space 10b. The steam flow between those spaces 10a and 10b, which include a bypass flow from an outlet portion of the first stage nozzle diaphragm 4a1 to an outlet portion of the moving blade stage 3a1 via the space 10 around the nozzle box 5, can be prevented.

Thus, this embodiment is additionally provided with a bulkhead 9, and the space 10 around the nozzle box 5 is divided into the inner space 10a and the outer space 10b relative to the steam passage 8. Therefore, most of the steam flowing out from the first stage nozzle diaphragm 4a1 arranged at the outlet section of the nozzle box 5 can be led to the first moving blade stage 3a1 along the steam passage 8. As a result, the thermal energy of the steam flowing out from the first stage nozzle diaphragm 4a1 can be efficiently converted into kinetic energy to improve the efficiency of the steam turbine 1.

The bulkhead 9, which is a sealing, is integrally arranged with the nozzle box 5 in this embodiment. Alternatively, it may be integrally arranged with the inner casing 2b between the nozzle box 5 and some other stationary section of the steam turbine 1. Still alternatively, it may be arranged separately with the nozzle box 5 and the inner casing 2b as long as it is arranged between the nozzle box 5 and some other stationary section of the steam turbine 1 and can prevent the flow of steam between the inner space 10a and the outer space 10b.

FIGS. 2 through 4 show modified embodiments of this embodiment. Note that FIGS. 2 through 4 are schematic axial cross-sectional views of the modified embodiments of this embodiment taken along a plane inclined by 45° from the vertical direction. Note that the components of these modified embodiments that are same as those of the steam turbine 1 shown in FIG. 1 are denoted respectively by the same reference symbols and will not be described in greater detail.

In each of the steam turbines 1 of the modified embodiments of this embodiment shown in FIGS. 2 and 3, the space 10 formed around the nozzle box 5 between the turbine rotor 3 and the inner casing 2b is divided by a sealing other than a bulkhead 9 shown in FIG. 1 into an inner space 10a located inside relative to the steam passage 8 and an outer space 10b located outside relative to the steam passage 8. Otherwise, these modified embodiments are the same as the first embodiment shown in FIG. 1.

In the embodiment described in FIG. 1, the bulkhead 9 is provided as a sealing dividing the space 10 into the inner space 10a and the outer space 10b. In these modified embodiments shown in FIGS. 2 and 3, the bulkhead 9 is replaced by a nozzle box sealing device 13 as a sealing. In other words, in each of these modified embodiments, the space formed around the nozzle box 5 between the turbine rotor 3 and the inner casing 2b is divided by a nozzle box sealing device 13 into the inner space 10a located inside relative to the steam passage 8 and the outer space 10b located outside relative to the steam passage 8. The inner space 10a means a space including an inner peripheral side (inner side) of the nozzle box 5, and the outer space 10b means a space including at least an outer peripheral side (outer side) of the nozzle box. The outer peripheral side of the nozzle box 5 includes outer peripheral side of the steam passage 8.

Particularly, in the modified embodiment shown in FIG. 2, the nozzle box sealing device 13 comprises a casing side sealing device 13a which seals a gap between the nozzle box 5 and the inner casing 2b, and a rotor side sealing device 13b which seals a gap between the nozzle box 5 and the main body of the shaft sealing device 12. Therefore, steam do not flow from the inner space 10a to the outer space 10b and vice versa. This arrangement provides advantages similar to those of the first embodiment of FIG. 1.

In the other modified embodiment shown in FIG. 3, the nozzle box sealing device 13 comprises a packing head 13c, which seals a gap between the nozzle box 5 and the turbine rotor 3, and a groove section 13d circumferentially provided on an outer surface of the nozzle box 5 facing to the turbine rotor 3. The packing head 13c comprises a plurality of segments arranged in the circumferential direction inserted into the groove section 13d of the nozzle box 5 for engagement. Thus, as a whole, the gap between the nozzle box 5 and the turbine rotor 3 is sealed along the entire periphery of the turbine rotor 3.

With this arrangement, the packing head 13c can be readily replaced with new ones when steam leaks due to degradation with time of the packing head 13c. Thus, the maintainability of the packing head 13c is improved. The modified embodiment of FIG. 3 has two nozzle box sealing devices 13, each having a packing head 13c and a groove section 13d, that are arranged in series in the axial direction. However, the number of nozzle box sealing devices may be made one or more than two appropriately depending on the required pressure difference between the inner space 10a and the outer space 10b.

The other modified embodiment shown in FIG. 4 further modifies the modified embodiment of FIG. 3. In the first embodiments including modified embodiments shown in FIGS. 1 through 3, the nozzle box 5 holds the first stage turbine nozzles 4b1 and the second stage turbine nozzles 4b2. In this further modified embodiment shown in FIG. 4, the nozzle box 5 further holds the third stage turbine nozzles 4b3.

More specifically, as shown in FIG. 4, the outer peripheral side member of the nozzle box 5 of the steam turbine extends to the downstream side in the axial direction. Two hook sections are provided at the extended portion, and the second stage nozzle diaphragm 4a2 and the third stage nozzle diaphragm 4a3 are engaged respectively with the two hook sections. A plurality of second stage turbine nozzles 4b2 and a plurality of third stage turbine nozzles 4b3 are circumferentially provided respectively with the second stage nozzle diaphragm 4a2 and the third stage nozzle diaphragm 4a3. Thus, in this modified embodiment, the second stage turbine nozzles 4b2 and the third stage turbine nozzles 4b3 are secured to the nozzle box 5 respectively, having the second stage nozzle diaphragm 4a2 and the third stage nozzle diaphragm 4a3 therebetween. Otherwise, the configuration of this modified embodiment is the same as that of the modified embodiment of the first embodiment shown in FIG. 3.

With this arrangement, the pressure of the outer space 10b of the space around the nozzle box 5 is substantially equal to the pressure of the steam passage 8 at the outlet of the third moving blade stage 3a3. As a result, the pressure of the outer space 10b can be further reduced, so that the wall thickness of the inner casing 2b can be reduced accordingly.

In this modified embodiment shown in FIG. 7, the second and third stage nozzle diaphragms 4a2, 4a3 are arranged separately with the nozzle box 5, and the second stage and third stage turbine nozzles 4b2, 4b3 are held by the nozzle box 5 respectively by having nozzle diaphragms 4a2, 4a3 therebetween. However, the arrangement is not limited to those, and the second stage and third stage nozzle diaphragms 4a2, 4a3 may be integrally formed with the outer peripheral member of the nozzle box 5 extended to the downstream side in the axial direction.

Only the first through third stage turbine nozzles 4b1, 4b2, 4b3 are held by the nozzle box 5 in the modified embodiment shown in FIG. 4. Alternatively, the fourth and the subsequent turbine nozzles 4b4, . . . may also be held by the nozzle box 5.

The nozzle box sealing device 13 including the packing head 13c and the groove section 13d is provided as a sealing for dividing the space around the nozzle box 5 into the inner space 10a and the outer space 10b in the modified embodiment of FIG. 4. However, alternatively, the nozzle box sealing device 13 may two members including a casing side sealing device 13a, which seals a gap between the nozzle box 5 and the inner casing 2b and a rotor side sealing device 13b, which seals a gap between the nozzle box 5 and the main body of the shaft sealing device 12 as shown in FIG. 2. Alternatively, the nozzle box sealing device 13 may be replaced by a bulkhead 9 as shown in FIG. 1.

Number	Name	Date	Kind
3746463	Stock et al.	Jul 1973	A
4362464	Stock	Dec 1982	A
4498301	Tsubouchi	Feb 1985	A
4550569	Isa et al.	Nov 1985	A
4884934	Ikeda et al.	Dec 1989	A
5215436	Puzyrewski	Jun 1993	A
5392513	Mazzola et al.	Feb 1995	A
5411365	Mazzola et al.	May 1995	A
6341937	Magoshi et al.	Jan 2002	B1
20090053048	Kawakami et al.	Feb 2009	A1
20090068001	Kawakami	Mar 2009	A1

Number	Date	Country
846 696	Aug 1952	DE
759 486	Mar 1953	DE
10 04 202	Mar 1957	DE
1 094 201	Apr 2001	EP
1 096 110	May 2001	EP
1 098 070	May 2001	EP
790 654	Feb 1958	GB
1 010 300	Nov 1965	GB
1 073 415	Jun 1967	GB
51-065102	May 1976	JP
56-109602	Aug 1981	JP
59-206602	Nov 1984	JP
61-085502	May 1986	JP
61-138804	Jun 1986	JP
3-066484	Oct 1991	JP
2006-104951	Apr 2006	JP
2008-075645	Apr 2008	JP

Steam turbine

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