Controlled flow guides for turbines

Abstract

This application provides a steam turbine. The steam turbine may include a number of controlled flow runners and a number of controlled flow guides. The controlled flow guides may include an upstream passage ratio (W.sub.up/W) of 0.4 to 0.7.

Claims

1. A steam turbine, comprising: a plurality of controlled flow runners; and a plurality of controlled flow guides; the plurality of controlled flow guides defines an upstream passage ratio (W.sub.up/W) of 0.4 to 0.7.

2. The steam turbine of claim 1, wherein the upstream passage ratio (W.sub.up/W) is 0.6.

3. The steam turbine of claim 1, wherein the plurality of controlled flow guides comprises a pitch to width ratio of more than 1.9.

4. The steam turbine of claim 1, wherein the plurality of controlled flow guides comprises a suction side acceleration rate of 0.05 to 0.25 bar/mm.

5. The steam turbine of claim 1, wherein the plurality of controlled flow guides comprises a suction side acceleration rate of 0.2 bar/mm.

6. The steam turbine of claim 1, wherein each respective pair of the plurality of controlled flow guides comprises a throat therebetween.

7. The steam turbine of claim 6, wherein each respective pair of the plurality of controlled flow guides comprises a Mach number distribution (M.sub.1/M.sub.2) upstream of the throat of more than 1.01.

8. The steam turbine of claim 6, wherein each respective pair of the plurality of controlled flow guides comprises a Mach number distribution upstream (M.sub.1/M.sub.2) of the throat of 1.07.

9. The steam turbine of claim 1, wherein the plurality of controlled flow guides comprises a deflection angle of between 25 degrees to 38 degrees.

10. The steam turbine of claim 1, wherein the plurality of controlled flow guides comprises a deflection angle of 30 degrees.

11. The steam turbine of claim 1, wherein the plurality of controlled flow guides is attached to a casing.

12. The steam turbine of claim 1, wherein the plurality of controlled flow guides comprises a plurality of first stage controlled flow guides.

13. The steam turbine of claim 1, wherein the plurality of controlled flow guides comprises a plurality of second stage controlled flow guides.

14. The steam turbine of claim 1, wherein the plurality of controlled flow guides comprises a retrofit.

15. The steam turbine of claim 1, wherein the plurality of controlled flow runners is attached to a disc.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a schematic diagram of a steam turbine.

(2) FIG. 2 is a schematic diagram of a portion of a steam turbine showing a number of turbine stages.

(3) FIG. 3 is a plan view of a number of controlled flow guides and controlled flow runners that may be used in the steam turbine of FIG. 2.

(4) FIG. 4 is a plan view of a number of controlled flow guides as described herein and compared to a known controlled flow guide.

(5) FIG. 5 is a chart showing Mach number distributions.

DETAILED DESCRIPTION

(6) Referring now to the drawings, in which like numerals refer to like elements throughout the several views, FIG. 1 shows a schematic diagram of an example of a steam turbine 10. Generally described, the steam turbine 10 may include a high pressure section 15 and an intermediate pressure section 20. Other pressures in other sections also may be used herein. An outer shell or casing 25 may be divided axially into an upper half section 30 and a lower half section 35. A central section 40 of the casing 25 may include a high pressure steam inlet 45 and an intermediate pressure steam inlet 50. Within the casing 25, the high pressure section 15 and the intermediate pressure section 20 may be arranged about a rotor or disc 55. The disc 55 may be supported by a number of bearings 60. A steam seal unit 65 may be located inboard of each of the bearings 60. An annular section divider 70 may extend radially inward from the central section 40 towards the disc. The divider 70 may include a number of packing casings 75. Other components and other configurations may be used.

(7) During operation, the high pressure steam inlet 45 receives high pressure steam from a steam source. The steam may be routed through the high pressure section 15 such that work is extracted from the steam by rotation of the disc 55. The steam exits the high pressure section 15 and then may be returned to the steam source for reheating. The reheated steam then may be rerouted to the intermediate pressure section inlet 50. The steam may be returned to the intermediate pressure section 20 at a reduced pressure as compared to the steam entering the high pressure section 15 but at a temperature that is approximately equal to the temperature of the steam entering the high pressure section 15. Accordingly, an operating pressure within the high pressure section 15 may be higher than an operating pressure within the intermediary section 20 such that the steam within the high pressure section 15 tends to flow towards the intermediate section 20 through leakage paths that may develop between the high pressure 15 and the intermediate pressure section 20. One such leakage path may extend through the packing casing 75 about the disc shaft 55. Other leaks may develop across the steam seal unit 65 and elsewhere.

(8) FIGS. 2 and 3 show a schematic diagram of a portion of the steam turbine 100 including a number of stages 110 positioned in a steam or hot gas path 120. A first stage 130 may include a number of circumferentially-spaced first-stage controlled flow guides 140 and a number of circumferentially-spaced first-stage controlled flow runners 150. The controlled flow guides 140 and the controlled flow runners 150 may have a pitch 160, a throat 170, and a back surface deflection angle 180, wherein the pitch 160 is defined as the distance in the circumferential direction between corresponding points on adjacent guides 140 and adjacent runners 150, the throat 170 is defined as the shortest distance between surfaces of adjacent guides 140 and adjacent runners 150, and the back surface deflection angle (BSD) 180 is defined as the uncovered turning, that is the change in angle between suction surface throat point and suction surface trailing edge blend point.

(9) The first stage 130 may include a first-stage shroud 190 extending circumferentially and surrounding the first-stage controlled flow runners 150. The first-stage shroud 190 may include a number of shroud segments positioned adjacent one another in an annular arrangement. In a similar manner, a second stage 200 may include a number of second-stage controlled flow guides 210, a number of second-stage controlled flow runners 220, and a second-stage shroud 230 surrounding the second-stage controlled flow runners 220. The controlled flow guides 140 may have an Impulse Technology Blading (ITB) guide design. The controlled flow guides 140 may be original equipment or a retrofit. Any number of stages and corresponding guides and runners may be included. Other embodiments may have different configurations.

(10) Referring to FIG. 4, a controlled flow guide 140 as may be described herein is shown with a known guide 240 superimposed thereon in dashed lines for a comparison therewith. As can be seen, the controlled flow guides 140 may have a very high pitch to width ratio given a width reduction of more than about thirty percent or so as compared to the known guide 240. The area reduction may run from about 25 percent to about 50 percent or so. The pitch to width ratio may be more than about 1.9 or so. Such a ratio may reduce overall profile losses. The back surface deflection angle 180 may be more than about 25 degrees to about 38 degrees or so with about 30 degrees preferred. The high forward leading edge sweep off-loads the endwall sections and reduces secondary flow and losses. The upstream passage ratio (W.sub.up/W) 250 may be relatively short in the range of about 0.4 to 0.7 or so with about 0.6 preferred.

(11) The design provides a very high suction side acceleration rate. As is shown in FIG. 5, a suction side acceleration rate (dp/ds) 260 may be in the range of 0.05 to 0.25 bar/mm or so with about 0.2 bar/mm preferred. The suction side acceleration 260 may have a surprising, non-intuitive upstream bump 270 in the Mach number distribution (M.sub.1/M.sub.2) upstream of the throat 170, with the distribution in the range of about 1.01 to about 1.2 or so with about 1.07 preferred.

(12) This very high initial acceleration on the suction surface thus gives smaller droplet sizes, reduced thermodynamic wetness losses, and reduced consequential wetness losses. The gain in dry stage efficiency may be about 0.2% and wetness losses may be reduced by about 20% as compared to conventional designs. The overall design may safely approach or even somewhat exceed a conventional boundary layer shape factor and the like.

(13) It should be apparent that the foregoing relates only to certain embodiments of this application and resultant patent. Numerous changes and modifications may be made herein by one of ordinary skill in the art without departing from the general spirit and scope of the invention as defined by the following claims and the equivalents thereof.