WO2010021358A1 - 熱交換隔壁 - Google Patents
熱交換隔壁 Download PDFInfo
- Publication number
- WO2010021358A1 WO2010021358A1 PCT/JP2009/064571 JP2009064571W WO2010021358A1 WO 2010021358 A1 WO2010021358 A1 WO 2010021358A1 JP 2009064571 W JP2009064571 W JP 2009064571W WO 2010021358 A1 WO2010021358 A1 WO 2010021358A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- substrate
- heat exchange
- exchange partition
- pin fins
- partition wall
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/005—Combined with pressure or heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/221—Improvement of heat transfer
- F05D2260/2214—Improvement of heat transfer by increasing the heat transfer surface
- F05D2260/22141—Improvement of heat transfer by increasing the heat transfer surface using fins or ribs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R2900/00—Special features of, or arrangements for continuous combustion chambers; Combustion processes therefor
- F23R2900/03043—Convection cooled combustion chamber walls with means for guiding the cooling air flow
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R2900/00—Special features of, or arrangements for continuous combustion chambers; Combustion processes therefor
- F23R2900/03045—Convection cooled combustion chamber walls provided with turbolators or means for creating turbulences to increase cooling
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T50/00—Aeronautics or air transport
- Y02T50/60—Efficient propulsion technologies, e.g. for aircraft
Definitions
- the present invention relates to a heat exchange partition wall structure, and more particularly to a heat exchange partition wall suitable for cooling a combustor of a gas turbine.
- the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a heat exchange partition wall that can cool the substrate more effectively and further improve the cooling efficiency of the substrate.
- the present invention employs the following means in order to solve the above problems.
- the heat exchange partition according to the present invention includes a substrate and a plurality of pin fins erected on the surface of the substrate, and the heat exchange in which a cooling medium flows in the length direction of the substrate along the surface of the substrate.
- Each of the pin fins is a partition wall, and the whole or a part of the pin fins is inclined rearward so that the top surface is located downstream of the bottom surface.
- the whole or a part of the pin fin is tilted rearward so that the top surface of the pin fin is located downstream of the bottom surface of the pin fin.
- the cooling medium that has passed between the pin fins lined up collides obliquely from the upstream side with respect to the surface of the substrate, and heat is efficiently removed from the surface of the substrate, so that the surface of the substrate is more effective.
- the cooling efficiency of the substrate can be further improved.
- the surface of the substrate includes a concavo-convex surface having a waveform in a cross-sectional view in which concave portions and convex portions are alternately and repeatedly formed along the length direction of the substrate, More preferably, the bottom surface is a downstream inclined surface extending from the top of the convex portion to the downstream side.
- the surface of the substrate is provided with a concavo-convex surface having a waveform in a cross-sectional view in which concave portions and convex portions are alternately and repeatedly formed along the length direction of the substrate.
- the pin fin is formed so that its bottom surface starts from the apex of the convex portion or slightly downstream from the apex of the convex portion, so that the cooling that has passed between the pin fin arranged in the width direction and the pin fin is performed.
- the medium flows in the vicinity of the surface of the substrate along the downstream inclined surface extending from the apex of the convex portion to the downstream side, and then collides with the upstream inclined surface extending from the apex of the convex portion to the upstream side at a larger angle. Since heat is more efficiently removed from the surface of the substrate, the surface of the substrate can be more effectively cooled, and the cooling efficiency of the substrate can be further improved.
- the heat exchange partition according to the present invention includes a substrate and a plurality of pin fins erected on the surface of the substrate, and the heat exchange in which a cooling medium flows in the length direction of the substrate along the surface of the substrate.
- Each of the pin fins is inclined forward or upstream so that the top surface of the pin fin is located upstream of the bottom surface, and the surface of the substrate is Are provided with an uneven surface having a corrugated cross-sectional view in which concave portions and convex portions are alternately and repeatedly formed along the length direction, and each of the pin fins is an upstream inclined surface extending from the apex of the convex portion to the upstream side. Is formed as a bottom surface.
- the whole or a part of the pin fin is tilted forward so that the top surface of the pin fin is located upstream of the bottom surface of the pin fin.
- the cooling medium that has passed between the pin fins lined up collides obliquely from the upstream side with respect to the surface of the substrate, and heat is efficiently removed from the surface of the substrate, so that the surface of the substrate is more effective.
- the cooling efficiency of the substrate can be further improved.
- the surface of the substrate is provided with a concavo-convex surface having a corrugated cross-sectional view in which concave portions and convex portions are alternately and repeatedly formed along the length direction of the substrate.
- the pin fin is formed so that its bottom surface starts from the apex of the convex part or slightly upstream from the apex of the convex part.
- the passing cooling medium flows in the vicinity of the surface of the substrate along the downstream inclined surface extending from the apex of the convex portion to the downstream side, and then, at a larger angle to the upstream inclined surface extending from the apex of the convex portion to the upstream side. Since collision occurs and heat is more efficiently removed from the surface of the substrate, the surface of the substrate can be more effectively cooled, and the cooling efficiency of the substrate can be further improved.
- a plurality of turbulent flow promoting bodies that generate turbulent flow by disturbing the cooling medium flowing near the surface of the substrate are provided on the surface of the substrate.
- the cooling medium flowing near the surface of the substrate along the surface of the substrate is disturbed by colliding with the turbulence promoting body to generate turbulent flow. This effectively removes heat from the pin fin root and the surface of the board, so the pin fin root and the board surface can be cooled more effectively, further improving the cooling efficiency of the board. Can be made.
- the gas turbine combustor according to the present invention includes a heat exchange partition wall with good cooling efficiency.
- the gas turbine combustor according to the present invention since the heat exchange efficiency is improved, the amount of the cooling medium required for exchanging the same amount of heat as compared with the conventional gas turbine combustor is reduced. be able to. Therefore, when combustion air is used as the cooling medium, more combustion air can be introduced into the combustion chamber, the flow rate of combustion air can be increased relative to the flow rate of fuel, and combustion By reducing the temperature and promoting uniform stirring of the combustion gas and non-combustion gas in the combustor to cool rapidly and uniformly, the NO of exhaust gas discharged from the combustor for the gas turbine X concentration can be reduced.
- the gas turbine according to the present invention includes a gas turbine combustor with high heat exchange efficiency.
- the heat exchange efficiency is improved, so that the amount of the cooling medium required for exchanging the same amount of heat as compared with the conventional gas turbine can be reduced. Therefore, when combustion air is used as the cooling medium, more combustion air can be introduced into the combustion chamber, and the flow rate of the combustion air can be increased relative to the flow rate of the fuel. it is possible to reduce the concentration of NO X exhaust gas discharged from the gas turbine.
- the substrate can be cooled more effectively and the cooling efficiency of the substrate can be further improved.
- FIG. 2 It is a figure which shows the structure of the combustor which comprised the heat exchange partition which concerns on this invention. It is sectional drawing which cut the heat exchange partition which concerns on 1st Embodiment of this invention with the plane perpendicular to the surface along the longitudinal direction. It is a figure for demonstrating the arrangement
- Heat Exchange Partition 2 Combustor (Gas Turbine Combustor) 18 Cooling air (cooling medium) 20 substrate 20a surface 21 pin fin 25 heat exchange partition 26 substrate 26a surface 27 recess 28 convex portion 28a downstream inclined surface 28b upstream inclined surface 31 heat exchange partition 32 rib (turbulent flow promoting body) 33 Substrate 35 Heat exchange partition 36 Pin fin 40 Pin fin
- FIG. 1 is a diagram showing a configuration of a combustor having a heat exchange partition according to the present invention
- FIG. 2 is a cross section of the heat exchange partition according to the present embodiment taken along a plane perpendicular to the surface along the longitudinal direction.
- FIG. 3 and FIG. 3 are views for explaining an arrangement state of pin fins erected on the heat exchange partition shown in FIG. 2, and are views cut along a plane perpendicular to the central axis of the pin fins.
- the heat exchange partition wall 1 includes, for example, a compressor (not shown) that compresses combustion air, and injects and burns fuel into high-pressure air sent from the compressor to perform high-temperature combustion.
- Main components are a combustor (gas turbine combustor) 2 that generates gas and a turbine (not shown) that is located downstream of the combustor 2 and is driven by the combustion gas exiting the combustor 2.
- the present invention can be applied to the combustor 2 of the constructed aircraft gas turbine (not shown).
- the combustor 2 includes an outer cylinder 4 and an inner cylinder 6.
- the outer cylinder 4 is provided with an air inlet 9 for taking in the compressed air 11 discharged from the compressor.
- the outer wall of the inner cylinder 6 is formed by the shell 12.
- the inner cylinder 6 is provided with a fuel nozzle 8 that injects fuel into the inner cylinder 6, and an air inlet 10 that introduces air into the inner cylinder 6.
- the inside of the shell 12 is covered with a plurality of heat exchange partition walls (also referred to as “panels”) 1.
- the space surrounded by these heat exchange partition walls 1 forms a combustion chamber 16 in which fuel gas and air are mixed and burned.
- the heat exchange partition wall 1 is attached to the shell 12 so that a gap is left between the heat exchange partition wall 1 and the shell 12.
- a gap between the heat exchange partition wall 1 and the shell 12 communicates with a cooling air inlet 17 into which the compressed air 11 flows or a cooling air hole (not shown) formed in the shell 12.
- the downstream side of the combustion chamber 16 is connected to the turbine inlet.
- symbol 18 in FIG. 1 has shown the cooling air (cooling medium) which flows through the clearance gap between the heat exchange partition 1 and the shell 12.
- the heat exchange partition wall 1 includes a substrate 20 and a plurality of pin fins 21 that are regularly erected (provided) on a flat (uneven) surface 20 a of the substrate 20. And.
- Each of the pin fins 21 has a circular (or elliptical) cross-sectional shape taken along a plane perpendicular to the straight line 22 that is the central axis (longitudinal axis) of the surface 20a of the substrate 20 (that is, the substrate 20).
- the height H in the direction perpendicular to the surface 12a of the shell 12 is such that the surface 20a of the substrate 20 and the surface 12a of the shell 12 have a height H in the direction perpendicular to the surface 12a of the shell 12. It is formed so as to be the same as or slightly shorter than the distance between the two (more specifically, to be about four times the radius of the pin fins 21).
- Each pin fin 21 has a rearward inclination angle (with a straight line 22 and a straight line 22) such that the top surface (the surface facing the surface 12 a of the shell 12) is located downstream from the bottom surface (right side in FIG. 3).
- An angle between the surface 20a of the substrate 20 or an angle between the straight line 22 and the surface 12a of the shell 12) ⁇ (45 degrees in the present embodiment) is erected on the surface 20a of the substrate 20.
- the effect of the heat exchange partition 1 which concerns on this embodiment is demonstrated.
- the cooling air 18 flowing through the gap between the surface 12a of the shell 12 and the surface 20a of the substrate 20 passes between the pin fins 21 and the pin fins 21 arranged in the width direction, the flow passage area is 1 ⁇ 2.
- the height H is reduced to the same distance as the distance between the surface 20a of the substrate 20 and the surface 12a of the shell 12, the flow velocity is doubled and a straight line 22 that is the central axis of the pin fin 21 is obtained.
- the direction of the resultant force of the component in the direction orthogonal to this component that is, the direction of obliquely colliding with the surface 20a of the substrate 20 from the upstream side (for example, FIG. 9).
- heat is efficiently removed from the surface 20a of the substrate 20, so that the surface 20a of the substrate 20 can be more effectively cooled, and the cooling efficiency of the substrate 20 can be further improved.
- a part of the cooling air 18 that flows in the vicinity of the surface 20a of the substrate 20 along the surface 20a of the substrate 20 is formed in the vicinity of the back surface of the pin fin 21 (the downstream surface located on the right side in FIG. 2). It is guided to the shell 12 side through the dead water area and flows downstream along the surface 12 a of the shell 12. Then, the cooling air 18 that has flowed downstream along the surface 12 a of the shell 12 collides with the surface 20 a of the substrate 20 again.
- the entire pin fin 21 is tilted rearward so that the top surface of the pin fin 21 is located downstream of the bottom surface of the pin fin 21.
- the cooling air 18 that has passed between the pin fins 21 and the pin fins 21 that collide with each other obliquely collides with the surface 20 a of the substrate 20 from the upstream side, and heat is efficiently taken from the surface 20 a of the substrate 20.
- the surface 20a of the substrate 20 can be cooled more effectively, and the cooling efficiency of the substrate 20 can be further improved.
- FIG. 4 is a cross-sectional view of the heat exchange partition according to the present embodiment, cut along a plane along the longitudinal direction and perpendicular to the surface.
- the heat exchange partition 25 according to the present embodiment is different from that of the first embodiment described above in that a substrate 26 is provided instead of the substrate 20. Since other components are the same as those of the first embodiment described above, description of these components is omitted here.
- the surface 26a of the substrate 26 has a waveform in a cross-sectional view in which concave portions 27 and convex portions 28 are alternately and repeatedly formed along the length direction of the substrate 26 (that is, the horizontal direction in FIG. 4).
- a concave and convex surface is provided, and the concave portion 27 and the convex portion 28 each extend along the width direction (direction perpendicular to the paper surface in FIG. 4).
- Each pin fin 21 has a downstream inclined surface 28a that extends (extends) downstream from the apex of the convex portion 28 as a bottom surface. That is, each pin fin 21 is formed such that the bottom surface thereof starts from the top of the convex portion 28 or slightly downstream from the top of the convex portion 28.
- FIG. 5 to FIG. 8 are diagrams showing the calculation results of CFD.
- FIG. 5 shows no clearance (gap between the surface 12a of the shell 12 and the top surface of the pin fin 21) and unevenness (of the surface 26a of the substrate 26).
- FIG. 6 shows a clearance of 0.3 (0.3 times the radius of the pin fin 21) and an unevenness level of 1.
- FIG. 7 shows no clearance and an unevenness level of 2 when FIG. Indicates a calculation result when the clearance is 0.3 and the degree of unevenness is 2.
- the degree of unevenness 1 is, as shown in FIG. 9, a straight line 22 (see FIG.
- the degree of unevenness 2 is that the inclination of the downstream inclined surface 28 a extending from the apex of the convex portion 28 to the downstream side is along a straight line 22 (see FIG. 2) that is the central axis of the pin fin 21.
- the direction component is “1”, the component orthogonal to this component is “4”, and it is formed along the direction of the resultant force of these components.
- FIG. 4 a part of the cooling air 18 (see FIG. 4) that flows along the surface 12a of the shell 12 in the vicinity of the surface 12a of the shell 12 (Shown by a broken line in the figure), and a part of the cooling air 18 (see FIG. 4) that has flowed along the surface 12a of the shell 12 approximately in the middle between the surface 12a of the shell 12 and the surface 26a of the substrate 26 (see FIG. 4).
- the degree of unevenness ie, the steeper slope of the downstream inclined surface 28a
- the shorter the distance ie, for a short time
- a part of the cooling air 18 that flows in the vicinity of the surface 26a of the substrate 26 along the surface 26a of the substrate 26 is indicated by the backside of the pin fin 21. (The downstream surface located on the right side in the figure) is passed to the surface 12a of the shell 12 through the dead water area formed in the vicinity, and flows in the vicinity of the surface 12a of the shell 12 along the surface 12a of the shell 12.
- the cooling air 18 (refer FIG. 4) which flowed in the surface 12a vicinity of the shell 12 along the surface 12a of the shell 12 becomes a flow shown with a broken line in a figure, and collides with the surface 26a of the board
- the cooling air 18 (see FIG. 4) that has collided with the surface 26a of the substrate 26 flows for a while along the surface 26a of the substrate 26 in the vicinity of the surface 26a of the substrate 26, and then becomes a flow indicated by an alternate long and short dash line in the drawing. Then, it is guided to the vicinity of the surface 12 a of the shell 12 and flows in the vicinity of the surface 12 a of the shell 12 along the surface 12 a of the shell 12.
- the surface 26a of the substrate 26 has a waveform in a cross-sectional view in which the concave portions 27 and the convex portions 28 are alternately and repeatedly formed along the length direction of the substrate 26.
- An uneven surface is provided, and the pin fin 21 is formed so that its bottom surface starts from the apex of the convex portion 28 or slightly downstream from the apex of the convex portion 28.
- the cooling air 18 that has passed between the pin fins 21 arranged side by side flows in the vicinity of the surface 26a of the substrate 26 along the downstream inclined surface 28a that spreads from the apex of the convex portion 28 to the downstream side. Since the upper side inclined surface 28b (see FIG.
- FIGS. 11 and 12 A third embodiment of the heat exchange partition according to the present invention will be described with reference to FIGS. 11 and 12.
- 11 is a cross-sectional view of the heat exchange partition according to the present embodiment, taken along a plane perpendicular to the surface of the heat exchange partition along the longitudinal direction thereof
- FIG. 12 is an arrangement state of ribs erected on the heat exchange partition shown in FIG. It is the figure for demonstrating, Comprising: It is the figure which looked at the board
- the heat exchange partition wall 31 according to this embodiment includes the substrate 33 in which a plurality of ribs 32 are erected on the surface 26 a of the substrate 26. Different from that of form. Since other components are the same as those of the second embodiment described above, description of these components is omitted here.
- the rib (turbulence promoting body) 32 is adjacent to the upstream inclined surface 28 b that extends (extends) from the apex of the convex portion 28 to the upstream side, and the axis in the longitudinal direction thereof is adjacent.
- a part of the cooling air 18 (see FIG. 11) that flows in the vicinity of the surface 26 a of the substrate 33 along the surface 26 a of the substrate 33 collides with the rib 32.
- the turbulent flow generates heat and efficiently removes heat from the root portion of the pin fin 21 and the surface 26a of the substrate 33. Therefore, the root portion of the pin fin 21 and the surface 26a of the substrate 33 are more removed. It is possible to effectively cool, and the cooling efficiency of the substrate 33 can be further improved.
- FIG. 13 is a cross-sectional view of the heat exchange partition according to the present embodiment, cut along a plane along the longitudinal direction and perpendicular to the surface.
- the heat exchange partition wall 35 according to the present embodiment is different from that of the second embodiment described above in that a pin fin 36 is provided instead of the pin fin 21. Since other components are the same as those of the second embodiment described above, description of these components is omitted here.
- Each pin fin 36 has a forward tilt angle (straight line 37 and shell 12 so that the top surface (the surface facing the surface 12a of the shell 12) is located upstream of the bottom surface (left side in FIG. 13) and tilts forward.
- the substrate 26 with an angle formed by the surface 12a or an angle formed by the straight line 37 and the surface 26a of the substrate 26 (45 degrees in this embodiment). That is, each pin fin 36 has an upstream inclined surface 28b that extends (extends) upstream from the apex of the convex portion 28 as a bottom surface.
- each pin fin 36 is formed such that its bottom surface starts from the apex of the convex portion 28 or slightly upstream from the apex of the convex portion 28.
- FIGS. 14 the results of experiments conducted under the conditions shown in FIG. 14 using the naphthalene sublimation method are shown in FIGS.
- the heat exchange partition wall 1 described in the first embodiment in which the pin fins 21 are erected on the surface 20a of the substrate 20 with a backward inclination angle ⁇ 45 degrees (in FIG. 15, “ ⁇ 45 ° plane”).
- a heat exchange partition wall (a heat exchange partition wall indicated by a “+ 45 ° plane” in FIG. 15), a rear tilt angle ⁇
- the heat exchange partition wall 25 described in the second embodiment (the heat exchange partition wall indicated by “ ⁇ 45 ° wavefront” in FIG. 15), in which the pin fins 21 are erected on the downstream inclined surface 28a of the substrate 26 at 45 degrees ),
- the heat exchange partition wall 35 described in the fourth embodiment (with a “+ 45 ° wavefront” in FIG.
- the density of the pin fins when the pin fins are viewed from the downstream side that is, the projected area of the pin fins projected onto the surface orthogonal to the surface 12a of the shell 12 is reduced, and the reduction of the channel area between the pin fins is suppressed. by. And by suppressing the reduction
- the heat exchange partition wall 25 described in the second embodiment in which the pin fins 21 are erected on the downstream inclined surface 28a of the substrate 26 with a rearward inclination angle ⁇ 45 degrees (“ ⁇ ” in FIG. 15).
- the heat exchange partition wall 35 described in the fourth embodiment, in which the pin fins 36 are erected on the upstream inclined surface 28b of the substrate 26 with a forward tilt angle ⁇ 45 degrees.
- the described heat exchange partition wall 25 heat exchange partition wall indicated by “ ⁇ 45 ° (wave)” in FIG. 15
- the heat exchange partition wall having a good cooling efficiency is provided and the heat exchange efficiency is improved.
- the amount of cooling air required to exchange the same amount of heat can be reduced compared to the amount of combustion air, more combustion air can be introduced into the combustion chamber 16 and combustion relative to the fuel flow rate. it is possible to increase the flow rate of the use air, it is possible to reduce the concentration of NO X exhaust gas discharged from the combustor 2.
- the gas turbine combustor having good heat exchange efficiency since the gas turbine combustor having good heat exchange efficiency is provided, the same amount of heat is exchanged as compared with the conventional gas turbine.
- the amount of cooling air required for the fuel can be reduced, more combustion air can be introduced into the combustion chamber 16, and the flow rate of the combustion air relative to the flow rate of the fuel can be increased.
- the exhaust gas discharged from the aircraft gas turbine The NO X concentration can be reduced.
- the pin fin 21 according to the present invention is not limited to one having a circular (or elliptical) cross-sectional shape cut by a plane orthogonal to the straight line 22 (see FIG. 2) that is the central axis thereof. Any shape such as a square or a semicircle may be used. Further, the pin fin according to the present invention is not limited to the one in which the central axis viewed from the outer side in the width direction exhibits the straight line 22 (see FIG. 2). For example, the pin fin 40 having a shape as shown in FIG.
- the shell 12 on the surface 12a side tilts backward to the downstream side, or a pin fin that tilts in the opposite direction to the pin fin 40, that is, only a part of the shell 12 on the surface 12a side tilts forward to the upstream side.
- It may be a pin fin.
- the height H of the pin fin 21 according to the present invention is not limited to four times the radius, and may be arbitrarily long or short.
- the distance between the centers of the adjacent pin fins 21 and the pin fins 21 according to the present invention is not limited to four times the radius, and may be arbitrarily long or short. It may be weakened.
- the arrangement of the pin fins 21 according to the present invention is not limited to the equilateral triangle arrangement as shown in FIG. 3, and it is narrowed even if it is arbitrarily deformed and the interval in the flow direction is widened. It may be. Furthermore, the unevenness of the bottom surface is not limited to 1 or 2, and may be more uneven or close to a flat surface.
- the rib 32 may be provided on the upstream inclined surface 28b extending from the apex of the convex portion 28 to the upstream side.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Cooling Or The Like Of Electrical Apparatus (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
しかしながら、基板は、耐熱性には優れているが、熱伝導率のよくない耐熱合金(例えば、ニッケル基)で製作されるのが一般的であり、基板をより効果的に冷却し、基板の冷却効率をさらに向上させることが求められていた。
本発明に係る熱交換隔壁は、基板と、この基板の表面上に立設された複数のピンフィンとを備え、前記基板の表面に沿って前記基板の長さ方向に冷却媒体が流される熱交換隔壁であって、前記ピンフィンはそれぞれ、その頂面が、その底面よりも下流側に位置するように、全体または一部が下流側に後傾している。
また、本発明に係る熱交換隔壁によれば、基板の表面には、当該基板の長さ方向に沿って、凹部と凸部とが交互に繰り返し形成された断面視波形の凹凸面が設けられているとともに、ピンフィンは、その底面が凸部の頂点から、または凸部の頂点よりもわずかに上流側から始まるように形成されており、これにより、幅方向に並ぶピンフィンとピンフィンとの間を通過した冷却媒体は、凸部の頂点から下流側に拡がる下流側傾斜面に沿って基板の表面近傍を流れた後、凸部の頂点から上流側に拡がる上流側傾斜面に、より大きな角度で衝突し、基板の表面からさらに効率よく熱が奪われることとなるので、基板の表面をさらに効果的に冷却することができて、基板の冷却効率をより一層向上させることができる。
したがって、冷却媒体として燃焼用空気が利用される場合には、より多くの燃焼用空気を燃焼室内に導入することができ、燃料の流量に対する燃焼用空気の流量を増大させることができて、燃焼温度を低減するとともに燃焼器内部での燃焼ガス・非燃焼ガスの攪拌一様化を促進して急速にかつ一様に冷却することにより、当該ガスタービン用燃焼器から排出される排気ガスのNOX濃度を低減させることができる。
したがって、冷却媒体として燃焼用空気が利用される場合には、より多くの燃焼用空気を燃焼室内に導入することができ、燃料の流量に対する燃焼用空気の流量を増大させることができて、当該ガスタービンから排出される排気ガスのNOX濃度を低減させることができる。
2 燃焼器(ガスタービン用燃焼器)
18 冷却空気(冷却媒体)
20 基板
20a 表面
21 ピンフィン
25 熱交換隔壁
26 基板
26a 表面
27 凹部
28 凸部
28a 下流側傾斜面
28b 上流側傾斜面
31 熱交換隔壁
32 リブ(乱流促進体)
33 基板
35 熱交換隔壁
36 ピンフィン
40 ピンフィン
図1は本発明に係る熱交換隔壁を具備した燃焼器の構成を示す図、図2は本実施形態に係る熱交換隔壁を、その長手方向に沿うとともにその表面に垂直な平面で切った断面図、図3は図2に示す熱交換隔壁に立設されたピンフィンの配列状態を説明するための図であって、ピンフィンの中心軸線と直交する平面で切った図である。
一方、内筒6の外壁はシェル12によって形成されている。内筒6には、内筒6の内部に燃料を噴射する燃料ノズル8が設置されており、内筒6の内部に空気を導入する空気入口10が設けられている。
なお、図1中の符号18は、熱交換隔壁1とシェル12との間の隙間を流れる冷却空気(冷却媒体)を示している。
各ピンフィン21は、基板20の表面20aを底面とし、その中心軸線(長手方向軸線)である直線22と直交する平面で切った断面形状が円形(または楕円形)を呈する(すなわち、基板20の表面20aに平行な平面で切った断面形状が楕円形を呈する)筒状の部材であり、シェル12の表面12aに垂直な方向の高さHが、基板20の表面20aとシェル12の表面12aとの間の距離と同一か、またはわずかに短くなるように(より詳しくは、ピンフィン21の半径の約4倍となるように)形成されている。
また、各ピンフィン21は、その頂面(シェル12の表面12aと対向する面)が、その底面よりも下流側(図3において右側)に位置して後傾するよう、後傾角(直線22と基板20の表面20aとのなす角または直線22とシェル12の表面12aとのなす角)α(本実施形態では45度)をもって基板20の表面20a上に立設されている。
シェル12の表面12aと基板20の表面20aとの間の隙間を流れてきた冷却空気18は、幅方向に並ぶピンフィン21とピンフィン21との間を通過する際、その流路面積が1/2(高さHが基板20の表面20aとシェル12の表面12aとの間の距離と同一の場合)に絞られることにより、その流速が2倍になるとともに、ピンフィン21の中心軸線である直線22に沿う方向の成分と、この成分と直交する方向の成分との合力の方向、すなわち、基板20の表面20aに対して上流側から斜めに衝突する方向に進んでいくことになる(例えば、図9参照)。
これにより、基板20の表面20aから効率よく熱が奪われることとなるので、基板20の表面20aをより効果的に冷却することができて、基板20の冷却効率をさらに向上させることができる。
そして、シェル12の表面12aに沿って下流側に流れていった冷却空気18は、基板20の表面20aに再び衝突することとなる。
図4に示すように、本実施形態に係る熱交換隔壁25は、基板20の代わりに、基板26を備えているという点で上述した第1実施形態のものと異なる。その他の構成要素については上述した第1実施形態のものと同じであるので、ここではそれら構成要素についての説明は省略する。
また、各ピンフィン21は、凸部28の頂点から下流側に拡がる(延びる)下流側傾斜面28aを底面としている。すなわち、各ピンフィン21は、その底面が凸部28の頂点から、または凸部28の頂点よりもわずかに下流側から始まるように形成されている。
ここで、凹凸度1とは、図9に示すように、凸部28の頂点から下流側に拡がる下流側傾斜面28aの傾斜が、ピンフィン21の中心軸線である直線22(図2参照)に沿う方向の成分を「1」、この成分と直交する方向の成分を「2」とし、これら成分の合力の方向に沿うように形成されていることをいう。
また、凹凸度2とは、図10に示すように、凸部28の頂点から下流側に拡がる下流側傾斜面28aの傾斜が、ピンフィン21の中心軸線である直線22(図2参照)に沿う方向の成分を「1」、この成分と直交する方向の成分を「4」とし、これら成分の合力の方向に沿うように形成されていることをいう。
なお、基板26の表面に凹凸がない場合、すなわち、第1実施形態のところで説明した図2に示す基板20では、シェル12の表面12aに沿ってシェル12の表面12a近傍を流れてきた冷却空気18(図4参照)の一部、およびシェル12の表面12aに沿ってシェル12の表面12aと基板20の表面20aとの略真ん中を流れてきた冷却空気18(図4参照)の一部が、基板20の表面20aに衝突するまでの距離が本実施形態のものよりも長くなり、かつ、衝突の角度が本実施形態のものよりも小さくなる。
一方、基板26の表面26aに衝突した冷却空気18(図4参照)は、基板26の表面26aに沿って基板26の表面26a近傍を暫く流れた後、図において一点鎖線で示す流れとなって、シェル12の表面12a近傍に導かれ、シェル12の表面12aに沿ってシェル12の表面12a近傍を流れていくこととなる。
図11および図12に示すように、本実施形態に係る熱交換隔壁31は、基板26の表面26aに複数のリブ32が立設された基板33を備えているという点で上述した第2実施形態のものと異なる。その他の構成要素については上述した第2実施形態のものと同じであるので、ここではそれら構成要素についての説明は省略する。
図13に示すように、本実施形態に係る熱交換隔壁35は、ピンフィン21の代わりに、ピンフィン36を備えているという点で上述した第2実施形態のものと異なる。その他の構成要素については上述した第2実施形態のものと同じであるので、ここではそれら構成要素についての説明は省略する。
なお、図14中の傾きθ=-45とは、後傾角α=45度をもって基板20の表面20a上または基板26の下流側傾斜面28a上にピンフィンが立設されていることを意味し、傾きθ=+45とは、前傾角β=45度をもって基板20の表面20a上または基板26の上流側傾斜面28b上にピンフィンが立設されていることを意味している。
また、図16から図18中に示す「Nu」は、冷却空気(流体)18と基板(20または26)との間の熱伝達の強さを指示する無次元数(ヌセルト数)である。
また、本発明に係るピンフィンは、幅方向外側から見た中心軸線が直線22(図2参照)を呈するものに限定されるものではなく、例えば、図19に示すような形状を有するピンフィン40、すなわち、シェル12の表面12a側の一部のみが下流側に後傾するピンフィンや、ピンフィン40と逆方向に傾斜するピンフィン、すなわち、シェル12の表面12a側の一部のみが上流側に前傾するピンフィンであってもよい。
さらに、本発明に係るピンフィン21の高さHは、半径の4倍に限定されるものではなく、任意に長くても短くても良い。
さらにまた、本発明に係る隣接するピンフィン21とピンフィン21との中心間の間隔は、半径の4倍に限定されるものではなく、任意に長くても短くても良く、より下降速度を強めたり、弱めたりしたものであってもよい。
さらにまた、本発明に係るピンフィン21の配置は、図3に示したような正三角形配置に限定されるものではなく、任意に変形して流れ方向の間隔が広がったものであっても、狭まったものであっても良い。
さらにまた、底面の凸凹度は1または2に限定されるものではなく、より凸凹しても平面に近くしたものであってもよい。
Claims (6)
- 基板と、この基板の表面上に立設された複数のピンフィンとを備え、前記基板の表面に沿って前記基板の長さ方向に冷却媒体が流される熱交換隔壁であって、
前記ピンフィンはそれぞれ、その頂面が、その底面よりも下流側に位置するように、全体または一部が下流側に後傾していることを特徴とする熱交換隔壁。 - 前記基板の表面は、前記基板の長さ方向に沿って、凹部と凸部とが交互に繰り返し形成された断面視波形の凹凸面を備えており、
前記ピンフィンはそれぞれ、前記凸部の頂点から下流側に拡がる下流側傾斜面を底面として形成されていることを特徴とする請求項1に記載の熱交換隔壁。 - 基板と、この基板の表面上に立設された複数のピンフィンとを備え、前記基板の表面に沿って前記基板の長さ方向に冷却媒体が流される熱交換隔壁であって、
前記ピンフィンはそれぞれ、その頂面が、その底面よりも上流側に位置するように、全体または一部が上流側に前傾しているとともに、
前記基板の表面は、前記基板の長さ方向に沿って、凹部と凸部とが交互に繰り返し形成された断面視波形の凹凸面を備えており、
前記ピンフィンはそれぞれ、前記凸部の頂点から上流側に拡がる上流側傾斜面を底面として形成されていることを特徴とする熱交換隔壁。 - 前記基板の表面に、当該基板の表面近傍を流れてきた冷却媒体を攪乱させることにより乱流を発生させる乱流促進体が複数設けられていることを特徴とする請求項1から3のいずれか一項に記載の熱交換隔壁。
- 請求項1から4のいずれか一項に記載の熱交換隔壁を具備してなることを特徴とするガスタービン用燃焼器。
- 請求項5に記載のガスタービン用燃焼器を具備してなることを特徴とするガスタービン。
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