U.S. patent number 3,635,585 [Application Number 04/887,544] was granted by the patent office on 1972-01-18 for gas-cooled turbine blade.
This patent grant is currently assigned to Westinghouse Electric Corporation. Invention is credited to Charles Walter Metzler, Jr..
United States Patent |
3,635,585 |
Metzler, Jr. |
January 18, 1972 |
GAS-COOLED TURBINE BLADE
Abstract
A cooled turbine blade for gas turbines and the like having
passageways for conducting a relatively cool fluid through the
blade to its tip and incorporating a walled cavity at the tip of
the blade. The wall of the cavity has a cutaway portion which
permits the cooling fluid to discharge into a main gas stream
through the turbine at the area of lowest pressure on the blade
surfaces. This permits the flow of fluid from the discharge
orifices of the passageways to be more uniform from the leading to
the trailing edge of the blade and reduces the required gas
pressure on the entire cooling system.
Inventors: |
Metzler, Jr.; Charles Walter
(Springfield, PA) |
Assignee: |
Westinghouse Electric
Corporation (Pittsburgh, PA)
|
Family
ID: |
25391380 |
Appl.
No.: |
04/887,544 |
Filed: |
December 23, 1969 |
Current U.S.
Class: |
416/96R; 416/92;
416/97R |
Current CPC
Class: |
F01D
5/187 (20130101); F01D 5/20 (20130101) |
Current International
Class: |
F01D
5/18 (20060101); F01D 5/14 (20060101); F01D
5/20 (20060101); F01d 005/18 () |
Field of
Search: |
;416/96,97,92,95 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Powell, Jr.; Everette A.
Claims
I claim as my invention:
1. In a turbine blade of the type having a root portion, a tip
portion, leading and trailing edge portions, a low-pressure surface
extending between said leading and trailing edges, a high-pressure
surface continuous with said low-pressure surface and extending
between said leading and trailing edges, and a plurality of
passages of uniform cross-sectional area extending from said root
portion to said tip portion of the blade for conducting a cooling
fluid through the blade; the improvement comprising a walled cavity
at the outermost tip portion of said blade having a bottom at which
said passages terminate and a cutaway portion in its wall extending
between said trailing edge and a point on said low-pressure side
which permits the cooling fluid to discharge into the main gas
stream through the turbine at the point of substantially lowest
pressure on the blade surfaces, and said wall being a continuous
extension of the outer high-pressure and low-pressure surfaces.
2. The improvement of claim 1 wherein said point is opposite the
trailing edge of a next successive turbine blade when said blades
are assembled on a rotor.
3. The improvement of claim 1 wherein the area between the point on
said low-pressure side where said wall terminates and the opposite
wall on the high-pressure side of the blade is substantially
greater than the combined areas of the cross sections of the
passages upstream of said point between said point and said leading
edge.
4. The improvement of claim 1 wherein said blade is of airfoil
construction with a rounded leading edge portion of greater radius
than the trailing edge portion.
Description
BACKGROUND OF THE INVENTION
In constructing turbine blades for gas turbine engines, numerous
difficulties are encountered in their design because of the high
speeds at which such blades operate and because of the high
temperatures to which they are subjected. The temperature of a
blade may be held materially lower than that of the gases in which
it operates by providing cooling passages in the blade extending
from its root to its tip and by conducting a stream of cooling
fluid, such as air, through these passageways to cool the
blade.
Normally, the cooling passages terminate at openings in the extreme
end or tip of the blade. This, however, has several disadvantages.
First, the pressure on the blade at its leading edge is greater
than at its trailing edge. As a result, the cooling fluid in the
passages at the leading edge must discharge into an area of greater
pressure than the passages at the trailing edge, meaning that the
flow of fluid and heat transfer efficiency at the leading edge is
impeded. Secondly, the tip clearance between the end of the blade
and the stationary turbine wall must be greater than it otherwise
would be; and the tolerances become more critical. Finally, the
pressure on the cooling fluid must be increased to the point where
it can be effectively discharged into a high-pressure gas
stream.
SUMMARY OF THE INVENTION
In accordance with the present invention, the foregoing drawbacks
associated with prior art cooling systems are overcome by a
construction wherein the blade is provided with a walled cavity at
its tip. The cooling passages terminate at the bottom of the
cavity; while the extremity of the cavity wall is adjacent the
turbine casing, and, in effect, constitutes the end of the blade. A
portion of the wall is cut away on the low-pressure side of the
blade adjacent its trailing edge such that the passages in the
blade do not discharge into the main turbine gas stream but rather
into a relatively constant pressure area within the cavity.
Furthermore, by virtue of the fact that the wall of the cavity is
cut away adjacent to the trailing edge of the blade on its
low-pressure side, the cavity is exposed to the lowest discharge
pressure possible with a minimum disturbance to the main flow
through the turbine. Thus, the pressure on the cooling system can
be reduced and, at the same time, the flow of fluid through the
cooling passages from the leading edge of the blade to its trailing
edge is essentially the same throughout.
The above and other objects and features of the invention will
become apparent from the following detailed description taken in
connection with the accompanying drawings which form a part of this
specification.
DESCRIPTION OF THE PREFERRED EMBODIMENT
FIG. 1 is a fragmentary elevational view of a turbine rotor having
the blades of the invention thereon;
FIG. 2 is a top view taken substantially along line II--II of FIG.
1, but on a larger scale, showing the walled cavity tip
construction of the blades of the invention;
FIG. 3 is a cross-sectional development view through the curved
center of a blade taken substantially along line III--III of FIG.
2; and
FIG. 4 is a perspective view of the blade tip of the invention.
With reference now to the drawings, and particularly to FIG. 1,
there is shown, by way of example, part of a gas turbine rotor
structure including a rotor shaft 10 which is connected to a rotor
disc 12 projecting radially from the shaft axis. The rim 14 of the
disc 12 is formed with a continuous series of transverse "side
entry" recesses 16, each of which is broadly V-shaped but having
sidewalls formed with adjacent secondary transverse serrations or
grooves 17.
The turbine blades 18, as perhaps best shown in FIGS. 2 and 4, have
the usual airfoil shape with rounded leading edges 20, thin
trailing edges 22 and curved profiles. The blade root 24 (FIG. 1)
is in the form of a triangular elongated block with the blade 18
integral with its one side and the two other sides having adjacent
transverse grooves therein, which grooves conform to and are
adapted to register with the grooves 17 formed in the transverse
recesses 16 of the disc rim 14, thus forming the well-known "fir
tree" base connection. Attachment is made by sliding the blade root
into the disc rim recess so that the grooves and ridges of the two
parts are in cooperative engagement. Suitable means, not shown, are
provided for maintaining the roots 24 within their cooperating
recesses 16. Furthermore, suitable means, not shown, but well
within the skill of the art, are provided for conducting a cooling
fluid such as air up through the root portions 24 and into radial
passages extending through each of the blades 18.
The radial passageways 26 are shown in FIGS. 2, 3 and 4 and extend
all the way from the root 24 to the tip or outer radial extremity
of each blade. The lower sides of the blades 18 as viewed in FIG. 2
are referred to as the high-pressure sides 29 and are those sides
against which hot gases under pressure are directed in order to
cause the rotor to turn in the direction of arrow 30 shown in FIG.
1. The other side 32 of each blade also extends between the leading
and trailing edges 20 and 22 and is referred to as the low-pressure
side. Hot gases, in passing through the blades, generally follow
the path of arrows 34. The point of highest pressure on the blades
is at the high-pressure side 29 adjacent the leading edge 20. As
the gas travels from the leading to the trailing edge of the blade,
it expands and its pressure reduces. Consequently, the point of
lowest pressure is at the low-pressure side 32 near the throat area
B.
In accordance with the present invention, the tip of each blade 18
is provided with a walled cavity, generally indicated by the
reference numeral 36 in FIGS. 2-4, which is formed by a wall 38
extending along the top of the high-pressure side 29 from the
trailing edge 22 to the leading edge 20 and thence along
approximately one-half the length of the low-pressure side 32 to
point A which is just downstream of the throat B between the
trailing edge 22 of one blade and the low-pressure side of the
following blade. The radial passageways 26 terminate at the bottom
37 of the cavity 36, as perhaps best shown in FIG. 3. In this
manner, the gas discharges into an area within the cavity 36 of
relatively constant pressure, meaning that the pressure which gases
issuing from the passageways 26 at the leading edge 20 experience
is approximately the same as that experienced by the gas leaving
the passageways 26 adjacent the trailing edge 22. The depth of the
cavity 36 is adjusted to provide an area at C which is
substantially greater than the combined area of the cross sections
of the cooling passages 26 upstream of point A. This permits the
discharge pressure for the upstream holes to approach the pressure
at point A, approximately the lowest pressure on the blade
surface.
The present invention thus provides a means for attaining a uniform
flow of cooling fluid through radial passages in a turbine blade
from its leading to its trailing edge, independent of operating tip
clearances between the blade tip and the stationary turbine walls.
At the same time, the cooling air enters the main stream through
the turbine in more nearly the correct direction for mixing with
the main gas stream, thereby reducing mixing losses. Although the
invention has been shown in connection with a certain specific
embodiment, it will be readily apparent to those skilled in the art
that various changes in form and arrangement of parts may be made
to suit requirements without departing from the spirit and scope of
the invention.
* * * * *