EP2025869B1

Movatterモバイル変換

Info

Publication number: EP2025869B1
Application number: EP07113996A
Authority: EP
Inventors: Maxim Dr. Konter; Anton Soumine; Sergey Vorontsov; Alexander Khanin
Original assignee: Alstom Technology AG
Current assignee: GE Vernova GmbH
Priority date: 2007-08-08
Filing date: 2007-08-08
Publication date: 2010-12-15
Anticipated expiration: 2027-08-08
Also published as: EP2025869A1; CA2638535C; US20090041587A1; DE602007011256D1; CA2638535A1; TW200928075A; SI2025869T1; TWI374214B; ATE491863T1; MX2008010091A

Abstract

A gas turbine rotating blade (1) comprises an internal cooling structure having at least three cooling air passages (5-7) in fluid connection with one another by means of turns (9, 10). An opening (12) provides an outlet for dissolved core material to be removed from the blade following casting of the cooling structure without any residue remaining within. According to the invention, the cooling structure comprises trip strips (13, 15) in the first and second passage (5, 6) with specified ratio of height to distance between trip strips and the trip strips (13) in the first passage being arranged at 90° with respect to the direction of airflow. In a particular embodiment, the trip strips (15) in the second passage (6) are arranged at angle of 45°. The design according to the invention assures sufficient airflow through first and second air passages (5, 6).

Description

Technical field

The present invention relates to cast rotating blades for a gas turbine, and in particular to the design of an internal cooling structure within the blade.

Background art

Turbine blades for gas turbines are designed and manufactured to withstand high temperatures during the gas turbine operation. Such turbine blades comprise an internal cooling structure through which a cooling fluid, typically air, is passed. Cooling air is typically bled from a compressor of the gas turbine engine. This extraction of air however, reduces the overall performance of the engine. In order to minimize the effect on engine performance by minimizing the air consumption and yet assure sufficient cooling of the blade, the internal blade cooling structure is designed for optimal cooling efficiency. Such designs are disclosed for example in US 6,139,269,US 6,634,858 andUS 5,403,159. Each is individually designed having complex arrangements of serpentine cooling structures including several passages extending in the blade longitudinal direction. Some of the passages connect to an inlet opening at the blade root, while other passages connect to an outlet opening at the blade tip or to a further longitudinal passage by means of a turn or bend of approximately 180°. The cooling structures furthermore comprise a multitude of trip strips arranged on the walls of the longitudinal passages, all of which oriented at approximately 45° to the direction of flow through the passage. Turbine blades with internal cooling structure of this type are cast, as a rule, by an investment casting process using a core defining the cooling structure. The core is made of a leachable material such as ceramic. Following the molding process, the ceramic core is removed from the blade by a leaching process.
The leaching process is difficult in regard to the removal of all of the dissolved core material in the region of the 180° turns. A risk remains that residual core material stays behind in the blade cooling channels and obstructs the flow of cooling media through the cooling passage. In order to reduce this risk, an opening is provided in the cooling structure wall in the region of the 180° turn for remaining core material to leach out. In some known gas turbine blades, as disclosed for example inUS 6,634,858, this opening is again closed by means of a plate or plug.

Summary of invention

It is the object of the invention to provide a gas turbine rotating blade with an internal cooling structure having a design that allows improved and more cost efficient manufacturability over those of the state of the art while, at least, maintaining the existing cooling performance of the internal cooling structure.
A gas turbine rotating blade comprises an internal cooling structure having at least three cooling passages extending in the blade longitudinal direction, at least one inlet opening in the region of the blade root, and at least one outlet opening in the region of the blade tip leading from a cooling passage out of the blade. The blade furthermore comprises in its root region a plenum for cooling air, the inlet opening extending from this plenum to a cooling passage. The first cooling passage extends, in the direction of cooling fluid, from the blade root region to the blade tip region. The second cooling passage extends from the tip to the root region. First and second cooling passages are in fluid connection with one another in the region of the blade tip by means of a bend or turn in the region of the blade tip. The third cooling passage again extends from the root to the tip, while second and third cooling passages are in fluid connection with one another by means of a turn or bend in the region of the blade root.
US 4,728,400 discloses a gas turbine blade having several cooling passages, of which a first cooling passage comprises trip strips arranged at a 90° angle to the direction of cooling flow through the passage.
In order for a core material to be removed from the bend by leaching out with a reduced risk of core material remaining in the bend, an opening is provided in the cooling structure wall extending from the plenum to the bend or turn in the blade root region from the second to the third cooling passage. The opening provides a direct fluid connection from the bend to the root of the blade and to the exterior of the blade. In particular, the opening and root region of the blade is such that a liquid fluid is allowed to flow directly and essentially in the longitudinal blade direction out of the blade internal cooling structure. This allows the fluid core material to exit the blade completely without having to pass through any back turns or dead zones. Thus, it is prevented that fluid core material remains in the structure as residual fluid. The flow of cooling air through the internal cooling structure when the blade is in operation is thus assured.
For purposes of simplified and thus cost efficient manufacture of the gas turbine rotating blade, the opening at the bend or 180° turn of the internal structure is not closed up again prior to the operation of the blade in the turbine. Since said opening at the 180° turn has an effect on the aerodynamics of the internal cooling structure and distribution of the cooling air, the design of the cooling passages is adapted and optimized accordingly in view of cooling function and efficiency.
According to the invention, the first cooling passage extending, in the direction of cooling fluid from the plenum in the root region to the tip region of the blade, comprises a plurality of turbulators or trip strips arranged at an angle of 90±10° to the direction of flow of the cooling fluid. Additionally, the second cooling passage, in fluid connection with the first cooling passage by means of a turn, comprises a plurality of trip strips or turbulators. Finally, in combination with the specific orientation of the trip strips in the first cooling passage, the trip strips in the first and second cooling passages are arranged and dimensioned such that the ratio between their height and the distance between adjacent trip strips is 10 ± 2.
Further according to the invention, the trip strips in the second cooling passage are arranged at an angle of 45° ± 10° in relation to the flow direction. In an exemplary embodiment of the invention, the third cooling passage comprises a plurality of trip strips arranged at an angle of 45° ± 10° from the direction of flow to the direction of the trip strip.
As mentioned above, the opening at the turn from the second to the third passage affects the cooling air distribution in the cooling structure. In particular, a non-plugged opening at that location would result in a reduction of the airflow from the plenum in the root region through the first and second passage and an increase of airflow from the plenum through the opening directly to the third passage. The design measures according to the invention in the form of a particular arrangement of trip strips in the first and second passage allow an optimization of the cooling airflow and re-establishment of the airflow through the first and second passage. It thereby assures sufficient and uniform cooling of the entire blade. The design of the trip strips according to the invention allows compensation of very small hydraulic pressure losses from the beginning of the first passage to the beginning of the third passage. Compensation of the low-pressure losses is achieved by pumping forces in the first and second passages due to a convective temperature increase of the cooling air along these passages.
The flow dynamics of the cooling air are elaborated in connection with the following figures.
As mentioned above, the design of the blade cooling structure according to the invention allows for optimized manufacturing due to the opening provided in the turn near the root of the blade. The design requires no measures following the casting for closing of the opening. The specific design of the trips strips in the cooling passages compensates for hydraulic pressure losses and thereby assures sufficient cooling within the first and second passages. The design therefore allows improved and simplified manufacturing while maintaining cooling performance.

Brief description of the drawings

Figure 1 shows an exemplary gas turbine blade, to which the invention may be applied;
figure 2 shows a cross-sectional view of the blade offigure 1 along II-II showing an internal blade cooling structure according to the invention;
figures 3a and 3b show respectively, a cross-section of trip strips along IIIa-IIIa infigure 2 and trip strips in detail, in particular the arrangement and parameters of the trip strips in the first cooling passage of the blade cooling structure;
figures 3c and 3d show respectively, a cross-section of trip strips along IIIc-IIIc infigure 2 and trip strips in detail, in particular the arrangement and parameters of trip strips in the second cooling passage of the blade cooling structure.

Best modes for carrying out the invention

Figure 1 shows a rotatinggas turbine blade 1 extending longitudinally from ablade root 2 to ablade tip section 3.
Figure 2 shows the internal cooling structure of the blade having aplenum 4 within the root region for cooling air entering the cooling structure, a plurality of at least three longitudinal cooling passages 5-7 extending from theplenum 4 at theroot 2 to thetip 3, from thetip section 3 to theroot 2, and from the root to thetip section 3, respectively. The longitudinal passages are in fluid connection with one another by means ofturns 9 and 10 of approximately 180°.
The airflow passes, as indicated by arrows, from theplenum 4 through an inlet opening 8 at the beginning of the first cooling passage 5 (position A) to the end of the first passage at the tip of the blade (position B), and around aturn 9 of approximately 180°. It then flows along thesecond cooling passage 6 to a further 180° turn 10 (position C) connecting thesecond cooling passage 6 with thethird cooling passage 7. The cooling air finally flows through thethird cooling passage 7 to the tip of the blade and exits the cooling structure through an outlet opening 11 at the tip of the blade.
At theturn 10 near the root of the blade, an opening orchannel 12 is provided for leaching out core material after casting and allowing all of the dissolved core material to run out of the cooling structure via theplenum 4 such that no core material remains in theturn 10. Theopening 12 is left open during operation of the gas turbine. Through thisopening 12, cooling air could pass more readily from theplenum 4 directly to thethird cooling passage 7 rather than through first andsecond cooling passages 5 and 6. However, due to the particular design of the first and second cooling passages according to the invention, the pressure drop between position A and position B is such that a cooling airflow is assured throughpassages 5 and 6.
A pressure loss is due to hydraulic resistance and depends on the square of the air velocity, the shape of the channel, the degree of smoothness of the passage walls as well as the shape of turbulators or trip strips. The features according to the invention result in that the air pressure at position C at the beginning of thethird passage 7 is lower than at position A at the beginning of thefirst passage 5.
Additionally, a pumping effect occurs due to the rotation of the blade during turbine operation. Due to the pumping effect the air pressure increases with increasing radius of the passage, specifically in proportion to the difference of the squares of the radii at a given angular speed. In thefirst passage 5 therefore, the pressure increases with increasing radius from position A to position B. In thesecond passage 6, the pressure decreases with decreasing radius from position B to position C, decreasing by the same magnitude as it increased inpassage 5. The final effect would therefore be zero. Additionally however, a heat flux is picked up by the cooling air from the heat convective walls of the passages increasing the temperature of the cooling air. As a result, the temperature of the cooling air in thesecond passage 6 is higher than in thefirst passage 5. This temperature change also affects the pumping effect in the first and second passages. The higher temperature in the second passage results in that the pumping effect along thesecond passage 6 is smaller than in thefirst passage 5. Therefore, the pressure at position B is lower compared to that at position A, resulting in an effective cooling airflow alongpassages 5 and 6.
As mentioned above, the hydraulic resistance of a cooling passage depends from, among others, on the design of the passage, in particular the design of the turbulators or trip strips 13 and 15.Figure 2 shows an embodiment of the invention comprising in thefirst cooling passage 5 turbulators or trip strips 13 arranged at 90±10° in relation to the direction of cooling flow, as indicated by the arrow.Figure 3a shows in cross-section the parameters of the trip strips. Each trip strip has a height h measured from thewall 14 of thepassage 5, and eachtrip strip 13 is arranged at a distance d from the adjacent trip strip. The height h and distance d are at a ratio of 10±2. The trip strips are shown having a rectangular shape. However, they can be of any other aerodynamically suitable cross-sectional shape as well.Figure 3b shows the orientation of the trip strips in relation to the direction of cooling air flow indicated by the angle α. The angle α is 90°± 10°.
Figure 2 further shows thesecond cooling passage 6 having trip strips 15. Similarly as inpassage 5, the trip strips 15 inpassage 6 are designed having a height h measured from thewall 16 of thepassage 6 and distance d between them such that the ratio of height h to distance d is 10±2, as shown infigure 3c. Height h is measured from the wall of the passage, and distance d is measured between adjacent trip strips along the direction of cooling airflow.
The trip strips 15 in coolingpassage 6 as shown infigure 2 are at a greater distance from each other compared to the distance between adjacent trip strips 13 inpassage 5. However, the essential design features of cooling passages in order to assure a sufficient cooling air flow throughpassages 5 and 6 are the specific angular orientation of the trip strips inpassage 5 and the ratio of height h to distance d between adjacent trip strips of 10±2 for bothpassages 5 and 6.
A further design feature, which enhances the cooling performance includes the specific angular orientation of the trip strips inpassage 6. The trip strips are arranged at an angle β of 45±10° in relation to the direction of airflow, as shown infigure 3d.
Thethird passage 7 can also comprise turbulators 17 of any design in order to enhance cooling efficiency along that passage. In the exemplary embodiment shown, they are arranged at an inclination angle δ to the direction of airflow, the angle being 45±10° in relation to the direction of airflow.

Terms used in Figures

1: rotating blade
2: blade root
3: blade tip
4: plenum for cooling air
5: first cooling air passage
6: second cooling air passage
7: third cooling air passage
8: inlet opening
9: turn
10: turn
11: outlet opening
12: outlet opening for core material
13: trip strips in first passage
14: cooling passage wall
15: trip strips in second passage
16: wall of second cooling passage
17: trip strips in third passage
h: trip strip height
d: distance between adjacent trip strips
α: orientation angle of trip strips 13
β: orientation angle of trip strips 15
δ: orientation angle of trip strips 17
A: position at beginning of coolingpassage 5
B: position at end of coolingpassage 5
C: position at bend fromsecond passage 6 tothird passage 7

Claims

Rotating blade (1) for a gas turbine comprising a blade root (2) and blade tip (3) and an internal cooling structure comprising
a first cooling air passage (5) extending essentially in the longitudinal direction of the blade from a plenum (4) in the blade root (2) to the blade tip (3), a second cooling air passage (6) extending from the blade tip (3) to the blade root (2) and a third cooling air passage (7) extending from the blade root (2) to the blade tip (3), the first passage (5) being in fluid connection with the second passage (6) by means of a first turn (9) and the second passage (6) being in fluid connection with the third passage (7) by means of a second turn (10),
and the cooling structure further comprising an opening (12) extending from the second turn (10) to the plenum (4) providing a direct outlet for fluids from the blade,
and the first and second cooling air passages (5, 6) each comprising a plurality of trip strips (13, 15), the trip strips (13) in the first cooling passage (5) being arranged at an angle (α) of 90±10°to the direction of cooling fluid flow in that first passage (5),
characterized by
the trip strips (15) in the second passage (6) being arranged at an angle (β) of 45°± 10° in relation to the airflow direction,
and additionally, the trip strips (13, 15) in the first and second passages (5, 5) have a height (h) and a distance(d) between adjacent trip strips (13, 15), the ratio between the height (h) and the distance (d) being 10 ± 2.
Rotating blade (1) according to claim 1
characterized by
the third passage (7) comprising a plurality of trip strips (17) arranged at an angle (δ) of 45° ± 10°.