Patent Grant
7946820
The present invention relates to a rotating blade for a steam turbine and, more particularly, to a rotating blade for a steam turbine with optimized geometry capable of increased operating speeds.
The steam flow path of a steam turbine is formed by a stationary cylinder and a rotor. A number of stationary vanes are attached to the cylinder in a circumferential array and extend inward into the steam flow path. Similarly, a number of rotating blades are attached to the rotor in a circumferential array and extend outward into the steam flow path. The stationary vanes and rotating blades are arranged in alternating rows so that a row of vanes and the immediately downstream row of blades form a stage. The vanes serve to direct the flow of steam so that it enters the downstream row of blades at the correct angle. The blade airfoils extract energy from the steam, thereby developing the power necessary to drive the rotor and the load attached to it.
The amount of energy extracted by each row of rotating blades depends on the size and shape of the blade airfoils, as well as the quantity of blades in the row. Thus, the shapes of the blade airfoils are an important factor in the thermodynamic performance of the turbine, and determining the geometry of the blade airfoils is an important portion of the turbine design.
As the steam flows through the turbine, its pressure drops through each succeeding stage until the desired discharge pressure is achieved. Thus, the steam properties—that is, temperature, pressure, velocity and moisture content—vary from row to row as the steam expands through the flow path. Consequently, each blade row employs blades having an airfoil shape that is optimized for the steam conditions associated with that row. However, within a given row, the blade airfoil shapes are identical, except in certain turbines in which the airfoil shapes are varied among the blades within the row in order to vary the resonant frequencies.
The blade airfoils extend from a blade root used to secure the blade to the rotor. Conventionally, this is accomplished by imparting a fir tree shape to the root by forming approximately axially extending alternating tangs and grooves along the sides of the blade root. Slots having mating tangs and grooves are formed in the rotor disc. When the blade root is slid into the disc slot, the centrifugal load on the blade, which is very high due to the high rotational speed of the rotor, is distributed along portions of the tangs over which the root and disc are in contact. Because of the high centrifugal loading, the stresses in the blade root and disc slot are very high. It is important, therefore, to minimize the stress concentrations formed by the tangs and grooves and maximize the bearing areas over which the contact forces between the blade root and disc slot occur. This is especially important in the latter rows of a low pressure steam turbine due to the large size and weight of the blades in these rows and the presence of stress corrosion due to moisture in the steam flow.
In addition to the steady centrifugal loading, the blades are also subject to vibration.
The low pressure section rotating turbine blades are typically designed and optimized to cover a given operating speed as required by the different applications. Main operating parameters are annulus area, rotating speed, mass flow capability, and for the last stage blade, condensing pressure.
The difficulty associated with designing a steam turbine blade is exacerbated by the fact that the airfoil shape determines, in large part, both the forces imposed on the blade and its mechanical strength and resonant frequencies, as well as the thermodynamic performance of the blade. These considerations impose constraints on the choice of blade airfoil shape so that, of necessity, the optimum blade airfoil shape for a given row is a matter of compromise between its mechanical and aerodynamic properties.
It is therefore desirable to provide a row of steam turbine blades that provides good thermodynamic performance while minimizing the stresses on the blade airfoil and root due to centrifugal force and avoiding resonant excitation.
In an exemplary embodiment, a rotating blade for a steam turbine includes a root section and an airfoil section contiguous with the root section. The airfoil section is shaped to optimize aerodynamic performance while providing optimized flow distribution and minimal centrifugal and bending stresses. The blade also includes a tip section continuous with the airfoil section, and a cover formed as part of the tip section. The cover defines a radial seal that serves to minimize tip losses.
In another exemplary embodiment, a rotating blade for a steam turbine includes a root section and an airfoil section contiguous with the root section. The airfoil section is shaped to optimize aerodynamic performance while providing optimized flow distribution and minimal centrifugal and bending stresses. The blade also includes a tip section continuous with the airfoil section and having a tip width, and a cover formed as part of the tip section. The cover is wider than the tip width such that at speed, the cover engages an adjacent cover of an adjacent blade. The cover also defines a radial seal that serves to minimize tip losses. The blade is configured such that an exit annulus area of the blade is 0.248 m2, an operating speed range of the blade is between 5625 and 11250 rotations per minute, and a maximum mass flow of the blade is 30.9 kg/s.
With reference to
An airfoil 10 extends from the root section 2, and a tip section 4 is continuous with the airfoil section 10. As shown in
In order to accommodate operating speeds that range from 5625 to 11250 rotations per minute with a maximum mass flow of 30.9 kg/s and an exit annulus area of 0.248 m2, computational fluid dynamics were performed in order to optimize airfoil geometry. Mass flow and annulus area are important design parameters as is appreciated by those of ordinary skill in the art. An “exit annulus area” is an area of annular shape formed on the bottom by the top of the blade dovetail and on the top by the underside of the cover. The optimized geometry can accommodate the higher operating speeds while avoiding associated increases in stress and frequency concerns. In particular, the airfoil section 10 is provided with an optimal pitch to width ratio. Moreover, a thickness distribution along the airfoil section 10 is modified from a convention construction to optimize performance. Still further, the curvature of the airfoil section 10 is adjusted to lower pressure and shock losses as a result of the high speed operation. Stacking of airfoil sections is optimized to minimize vane root local stress caused by the centrifugal twist of the blade.
As shown in
The steam turbine rotating blade described herein affords significantly enhanced aerodynamic and mechanical performance and efficiencies while also including covers having radial sealing to minimize tip losses, minimal centrifugal and steam bending stresses, a continuously coupled cover design to minimize vibratory stresses, reduced efficiency losses, and optimized flow distribution. As such, the turbine blades can be run efficiently at higher operating speeds.
While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiments, it is to be understood that the invention is not to be limited to the disclosed embodiments, but on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.
| Number | Name | Date | Kind |
|---|---|---|---|
| 5267834 | Dinh et al. | Dec 1993 | A |
| 5277549 | Chen et al. | Jan 1994 | A |
| 5480285 | Patel et al. | Jan 1996 | A |
| 5509784 | Caruso et al. | Apr 1996 | A |
| 6575700 | Arai et al. | Jun 2003 | B2 |
| Number | Date | Country | |
|---|---|---|---|
| 20090022600 A1 | Jan 2009 | US |
