EP1178183B1 - Niederdruckdampfturbine mit Mehrkanal-Diffusor - Google Patents
Niederdruckdampfturbine mit Mehrkanal-Diffusor Download PDFInfo
- Publication number
- EP1178183B1 EP1178183B1 EP01117519A EP01117519A EP1178183B1 EP 1178183 B1 EP1178183 B1 EP 1178183B1 EP 01117519 A EP01117519 A EP 01117519A EP 01117519 A EP01117519 A EP 01117519A EP 1178183 B1 EP1178183 B1 EP 1178183B1
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- EP
- European Patent Office
- Prior art keywords
- diffuser
- channel
- area
- exhaust
- radial
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- 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
- F01D9/00—Stators
- F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
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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
- F01D25/30—Exhaust heads, chambers, or the like
Definitions
- the invention relates to an axially flowed through low-pressure steam turbine with a axial / radial multi-channel diffuser and exhaust steam housing for low-loss guidance of the blasting off steam.
- a diffuser of this type is described in DE 44 22 700.
- the one revealed there Diffuser has one after the last row of blades Low-pressure steam turbine axial flow inlet and a radial Flow outlet on.
- the diffuser is with a view to optimizing the Turbine performance designed by a maximum possible pressure recovery.
- For this are the first sections of the inner and outer diffuser ring respectively with respect to the hub or the blade carrier in a bending angle aligned. This measure serves to homogenize the Total pressure profile above the channel height of the diffuser in the area of the last Blade row.
- the diffuser has a radially outwardly curved Baffle, which divides it into an inner and an outer channel.
- the outer and inner channels are arranged on the flow ribs, which are radial or be flowed diagonally.
- the baffle serves the Redirection as well as the guidance of the outflow.
- the flow ribs the purpose of the support of the baffle and in particular a reduction of the twist in the deceleration zone, which also makes it the optimization of the Contribute pressure recovery.
- realized flow ribs can only at a certain operating load to bring about optimal swirl reduction. at a different operating load, the swirl reduction is not necessarily optimal. A diffuser with this measure therefore only achieves one certain operating load an optimal pressure recovery.
- the Flow ribs and their attachment to the baffles with a relative associated with great design effort.
- the supersonic interferes Slit flow with the remaining subsonic flow.
- EP 581 978 in particular in FIG. 4 of that document, is a multi-channel exhaust gas diffuser for an axial flowed gas turbine with axial flow inlet and radial flow outlet disclosed.
- This multi-channel diffuser faces along its length is three zones.
- the first zone is in the style of a bell-shaped diffuser formed and extends einkanalig of the last row of blades to Exit plane of several flow ribs.
- the diffuser rings also point here Bent angle, which are set so that a homogenization of the Total pressure profile is achieved.
- the second zone faces downstream from the Flow ribs flow guiding rings, which several channels form.
- the third zone serves to strongly divert the exhaust gas flow into radial Direction and then flows into the chimney of the gas turbine.
- the purpose is to use the second-zone guide rings along the length of the third zone continued, where they are curved there.
- the second zone has low Deflection, but high Difffusor Koch on, the third zone large deflection, but only a very modest diffuser effect.
- a low pressure steam turbine it is the object of the present invention for a low pressure steam turbine to provide an axial / radial multi-pass diffuser with exhaust steam housing which achieves improved pressure recovery compared to the prior art diffusers, thereby increasing the efficiency of the low pressure steam turbine.
- the multi-channel diffuser should be optimized for as many operating conditions of the steam turbine as possible and be associated with a reduced design effort.
- the exhaust steam housing should be tuned to the diffuser in terms of turbine performance.
- the three-channel diffuser has three partial diffusers, an inner, middle and outer partial diffuser, which are formed by an inner diffuser ring, an outer diffuser ring and two baffles arranged between the diffuser rings.
- a first portion of the inner diffuser ring is arranged with respect to the hub in an inwardly directed towards the rotor axis bending angle and a first portion of the outer diffuser ring is in a relative to the blade channel at the height of the last blade row outwardly, directed away from the rotor axis bending angle ,
- the inventive axial / radial three-channel diffuser extend in particular the two baffles over the entire length of the diffuser. you are distributed unevenly between the inner and outer diffuser ring so that the area distribution on the three partial diffusers in the entrance surface of the diffuser is uneven. It accounts for the majority of the Entrance surface on the inner and middle part of the diffuser and a small part of the Entrance surface on the outer part of the diffuser.
- the baffles are possible arranged near the last row of blades, wherein the distance between the last blade row and the leading edges of the baffles by the for all Operating conditions permissible minimum distance is determined.
- the diffusion zone of the diffuser is characterized by the following features.
- the ratio of the exit surface to the entrance surface of the individual partial diffusers is greater than two for the middle part of the diffuser and greater than three for the outside Part diffuser.
- For the inner partial diffuser is the corresponding geometric Area ratio in a range of 1.5 to 1.8.
- the ratio of its length to his Channel height in the entrance area at least four.
- the ratio of length to channel height in the entrance surface at least equal to 10
- for the inner partial diffuser is the corresponding Ratio at least equal to 2.5. Due to these relatively large length to channel height ratios the deflections of the partial diffusers are corresponding relatively gently.
- the ratio of the exit surface to the entry surface of the entire diffuser is about two.
- the exhaust steam housing of the diffuser is designed so that the size the area of the dividing plane between the upper and lower half of the Abdampfgeffeuses on the size of the exit surfaces of the partial diffusers is tuned.
- the two baffles serve to separate the diffuser channel into three partial diffusers, in which the Beschaufelungsabströmung is performed.
- the effected Flow guidance is the better the more part diffusers at the same Total diffuser are present.
- more friction losses and higher barriers the more baffles are arranged.
- the one chosen here Number, three partial diffusers and two baffles has the advantage that a optimized flow control with reasonable friction losses at the Surfaces of the baffles and obstructions is effected.
- the baffles and partial diffusers cause a guidance and stabilization of the Beschaufelungsabströmung and a deflection in a radial direction. Since the baffles extend over the entire length of the diffuser, this guide is further supported. The radial extent of the partial diffusers further serves to reduce the tangential velocity in a natural way. The partial diffusers are thereby optimal for all operating conditions with regard to the reduction of the tangential velocity. Furthermore, the design effort for the baffles is relatively small and for the reduction of the tangential speed no further constructive measures such as diversion and flow ribs are necessary.
- the flow guidance and stabilization is further brought about in particular by the distribution of the diffuser inlet surface on the three partial diffusers.
- a large part of the inlet surface is omitted on the inner and middle channel, whereby the majority of the flow is guided by the blading to Abdampfgephaseuse.
- the small part of the entry surface is accounted for by the outer channel, through which the supersonic gap flow and the flow influenced by the gap flow are taken up by the turbine and meridionally deflected and shielded from the majority of the flow to the exhaust steam housing. This shielding avoids flow interferences between most of the flow and the high energy gap flow which would affect the diffuser effect.
- the minimum distance between the last row of blades and the leading edges of the baffles further contributes to optimum shielding of the slit flow and to avoid flow interference and streamline convergence.
- the ratio of length to channel height of each partial diffuser of 2.5 and more allows a gentle deflection from the axial, or diagonal, to the radial flow direction, which prevents the separation of the delayed flow, even with a ratio of the exit surface to inlet surface of 1.6.
- the design of the inventive diffuser is based on an inverse Design process, where initially the prevailing flow fields be determined. After that, the ideal ones are made of them Flow fields are calculated and the geometry of the diffuser due to this ideal flow fields is determined.
- this three-channel diffuser designed for limit load conditions. At limit load was a Flow field for which a three-channel diffuser with an orientation of the Beginning tangent of his baffles according to the invention the highest Achieved pressure recovery.
- This interpretation also provides the advantage that a higher turbine power at the same Condenser pressure is achieved or that the same turbine performance at higher Condenser pressure is achieved and thereby a smaller, cheaper Cooling system for the steam turbine is required.
- the blocksstangenten the baffles are in an angular range around the first break points of the baffles and a Referenzusingstangente, at least approximately through the first break point of the baffle and through the intersection of the rectilinear approximated boundaries of the blade channel.
- Partial diffuser In a further particular embodiment of the invention is attributable to the outer Partial diffuser accounts for the total flow inlet area of the diffuser Range of 10-12%. The remaining entrance area is 55-60% on the inner Partial diffuser and distributed to 30-35% on the middle part of the diffuser.
- the distance between the leading edges of the baffles and the trailing edge of the last blade is 4% of the total height of the row of tracks.
- the leading edges of the baffles are formed profiled at the flow inlet of the diffuser, whereby a gentle acceleration when entering the partial diffusers is effected.
- the diffusion zone of the diffuser is characterized as follows.
- the baffles are each supported by struts or struts extending from the inner and outer diffuser rings to the two baffles.
- the middle part of the diffuser remains free of supports and thus has minimal flow disturbances and losses.
- exhaust steam zone of the diffuser is on End baffle between the inner and middle part diffuser in a radial Extension arranged a Abdampfleitblech.
- This Abdampfleitblechblech causes a better flow distribution in the exhaust steam housing, whereby the Minimized flow losses and the capacitor applied uniformly becomes.
- FIG. 1 shows a three-channel diffuser as part of a low-pressure steam turbine. It leads the blading outflow into an exhaust steam housing 20. From the low-pressure steam turbine, the rotor 1 with rotor axis 2 and a rotor blade 3 of the last blade row are shown.
- the three-channel diffuser is limited by an inner diffuser ring 4 and an outer diffuser ring 5.
- the outer diffuser ring 4 is connected to the blade carrier 7.
- the inner and outer diffuser ring 4 and 5 have in the region of the trailing edge of the blade 3 bending angle ⁇ N or ⁇ Z, whereby, as shown in Figures 1a and 1b, the angle ⁇ N by the first section 4 'of the inner diffuser ring 4 and an extension of the hub 6 and the angle ⁇ Z by the extension of the last section 7 'of the blade carrier 7 and the first portion 5' of the outer diffuser ring 5 are formed.
- These buckling angles are for example 10-20 ° and contribute to the fact that the most homogeneous possible total pressure profile is achieved at the outlet of the last blade row.
- the diffuser has in its interior two baffles 8 and 9, which divide the diffuser into three sub-channels, an inner partial diffuser 10, a central partial diffuser 11 and an outer partial diffuser 12.
- the baffles are supported by supports 13 which extend from the inner and outer diffuser rings 4 and 5 to the baffles. For reasons of strength, the first supports 13 in the direction of flow are thicker than the second supports and each of round cross-section.
- the middle partial diffuser 10 is in particular free of supports.
- the baffles are distributed over the channel height of the diffuser with respect to the total pressure profile so that a flow-mechanically optimal surface distribution is achieved on the three sub-channels.
- the first baffle 8 is arranged so that the inner partial diffuser 10 has a flow inlet surface which is, for example, approximately 60% of the flow inlet area of the entire diffuser.
- the second baffle 9 is further arranged so that the central part of the diffuser 11, for example, has a flow inlet area of about 30% of the total flow inlet area.
- the outer partial diffuser 12 has a flow inlet area of, for example, approximately 10% of the total flow inlet area.
- the diffuser exit surface is designed so that the ratio of the exit surface to the entry surface of the entire diffuser, ie its upper and lower half, is approximately 2. In the case of the individual partial diffusers, the geometric relationships from outlet to inlet surface behave as follows. For example, for the inner partial diffuser 10, the ratio of the exit surface S12 in the upper half of the diffuser to the entrance surface S11 is approximately 1.3.
- the ratio of exit surface S13 in the lower half of the diffuser is greater to the entrance surface S11 and is approximately 1.6.
- the exit surface S13 of the inner partial diffuser 10 is therefore located in the lower half of the diffuser more outward than in the upper half. (Although it is actually located in the lower half of the diffuser, it is also marked S13 in this figure and in FIG. 4.)
- the ratio of the exit surface S22 to the entry surface S21 is approximately 2.1.
- the ratio of the exit surface S32 to the entry surface S31 is approximately 3.3. Such area ratios are the prerequisite for the efficiency of the turbine can be significantly increased.
- the diffuser is with a view to a gentle flow of the flow low curvature in relation to the channel height designed.
- the three Partial diffusers have a large length-to-channel height ratio for this purpose.
- the inner partial diffuser 10 is larger than 2.7 in the lower half of the diffuser.
- the Ratios in the example shown are greater than 4.4 or greater than twelve.
- the inner and outer diffuser ring and the two baffles have in their Cross section for manufacturing reasons, several straight sections, due to the large length-to-channel height ratios in gentle Tilt angles to each other. These gentle angles of inclination allow an improved guidance of the blading outflow. It will be through especially flow interference and flow separation avoided. Due to the relatively large radial extent of the diffuser and the Partial diffusers also become a natural removal of tangential velocities without the help of additional flow ribs or other measures to Reductions in tangential velocities achieved.
- the three partial diffusers have a gentle deflection due to their radial extent.
- the total deflection of each partial diffuser is designated by the angles ⁇ 1 , ⁇ 2 and ⁇ 3 in the center line 15 of the individual partial diffusers 10, 11 and 12, respectively. These angles are for example about 70 °, 36 °, and 47 °.
- the baffles 8 and 9 are approximately formed so that the extension of their initial tangent form the intersection A.
- the straight-line approximated hub-side and housing-side boundary of the blade channel passes through this intersection A.
- the starting tangents of the baffles 8 and 9 are aligned in the embodiment shown with respect to the rotor axis 2 in angles ⁇ 1 and ⁇ 2 .
- the intersection point A between the straight-line approximated hub-side and housing-side boundaries of the blading channel via the turbine end stage and the beginning tangents of the guide plates 8 and 9 form an at least approximately common point of intersection.
- the initial tangent of the baffle 8 with the straight-line approximated hub-side boundary forms an angle in the range of ⁇ 1 + 8 °.
- the beginning tangent of the guide plate 9 forms an angle in the range of ⁇ 2 ⁇ 4 °.
- This geometric design of the baffles with respect to the boundaries of the blading channel also applies to other housing contours and blade types, such as completely conical rectilinear housing contours, for housing contours where the section extends cylindrically or nearly cylindrically over the last row of blades.
- this geometry is not only applicable to blades with tip seal but also with blades with Deckbändem. In this case, the housing-side boundary of the blade channel passes through the intersection of the trailing edge of the last blade and the shroud.
- the initial members of the Baffles 8, 9 in an angular range around the first points of intersection B and C of the Baffles 8 and 9 and the reference tangents by the Intersections B and C and lead through the intersection A.
- the diffuser rings 4 and 5 and baffles 8 and 9 are made in the example shown from several straight sections, at small angles of inclination to each other standing joined together. Instead of sections are also continuous curved baffles and diffuser rings feasible.
- the partial diffusers 10 and 11 are arranged so that a major part of the flow from the blading through these two partial diffusers flows into the exhaust steam housing 20.
- a stable guidance of the main part of the flow in the region of the middle part of the diffuser is the most sensitive due to the prevailing Mach numbers on obstructions.
- the pillar-free central partial diffuser 11 thereby carries that part of the main flow without further disturbances.
- the high-energy, supersonic gap flow from the last blade row enters the outer partial diffuser 12, the channel height of which is determined in relation to the prevailing gap flow.
- the gap flow is guided by the outer partial diffuser 12 separately from the main part of the flow in the exhaust steam housing 20.
- the large length-to-channel height ratio cause a stabilization of the Diffuser flow and a homogenization and lowering of the Total pressure profile at the height of the last row of blades. This will be the Increased pressure recovery of the diffuser and an increase in efficiency of reached all the low-pressure steam turbine.
- the baffles 8 and 9 extend at the entrance to the diffuser to near the blade row. They are preferably arranged as close as allow the axial, thermal movements of the blade row and a necessary for the various operating conditions safety distance without causing a scratch.
- the distance a between the leading edges of the baffles 8 and 9 and the trailing edge of the last blades 3 is 4% of the total height h w of the last blade row.
- the leading edges of the baffles 8 and 9 are formed profiled to allow a smooth flow entry with the least possible overspeeding in the partial diffusers.
- the leading edges for example, as shown in Figure 2, formed gently pointed, for example according to the form NACA 65, wherein the profiling length e is three times the thickness ⁇ .
- the baffles are made as thin as possible, so that the Mach numbers rise as slightly as possible. For this purpose, their thickness is for example about 5% of the channel height of the middle part of the diffuser eleventh
- This Abdampfleitblech 8 ' causes an improvement in the flow in the exhaust steam housing 20 and a homogenization of the flow in the condenser.
- the Abdampfleitblech 8 ' has a gentle total deflection ⁇ L of about 50 °. This deflection is realized in this embodiment by two sections, the total length of the channel height in the exit plane is in a ratio of about 0.7.
- FIG. 3 shows a cross section through the exhaust steam housing 20 with an upper one Half 21 and a lower half 22, separated by a dividing plane 23 from each other are separated.
- the turbine steam passing through the exit surface of the upper half the diffuser enters the upper half 21 of the exhaust steam housing 20, flows then down through the parting plane 23 in the lower half 22 and from there through the exit surface 24 of the exhaust steam housing in the connected there Capacitor.
- the exhaust steam housing is designed in coordination with the diffuser so that the Exit surface 24 of the exhaust steam housing 20 about 15% larger than that Total exit surface of the diffuser is. This grants a reserve area in the Dividing level for possible obstructions in the outflow.
- the sum of the exit surfaces of the partial diffusers 11 and 12 the upper half of the diffuser is approximately equal to the surface 25 in the parting plane 23, which between the exhaust steam housing and the Abdampfleitblech 8 'of the Guide plate 8 is formed and hatched in the figure with solid lines is.
- half of the exit surface S12 of the inner partial diffuser 10 over the entire Rotation of the diffuser equal to the hatched area 26 with dashed lines.
- the approximation of these surfaces causes the diffuser outflow of the Partial diffusers 11 and 12 at the exit from the diffuser in the exhaust steam housing experiences as equal a large flow area and no bottlenecks. This in turn has a positive effect on the pressure recovery.
- FIG. 5 shows a variant of the three-channel diffuser with exhaust steam housing according to the invention, which is optimized in comparison with the configuration of FIG.
- the optimized diffuser with exhaust steam housing is designed, in particular with regard to the inner partial diffuser, so that the outlet surface S12 'of the inner partial diffuser 10 is defined further outside in comparison to the configuration of FIG. If the exit surface S12 'lies further outside as indicated by the dashed line, the ratio of the exit surface to the entry surface of that partial diffuser increases and the efficiency of the turbine is correspondingly increased.
- the exit surface S12 ' is defined such that the ratio of its area to the entrance surface S11 increases to approximately 1.8, which is a significant increase over the ratio of approximately 1.3 in the variant of FIG.
- the wall 21 'or hood of the upper half of the exhaust steam housing in comparison to the wall 21 of the exhaust steam housing of Figure 1 is placed radially further outside.
- the baffle 27 'of the exhaust steam housing is placed axially further out. Accordingly, the deflection angle ⁇ 1 decreases compared to the deflection angle in Figure 1 to about 60 °.
- Figure 6 shows this variant in the parting plane 23 between the upper and lower half of the diffuser. It also shows how the coordination of the dimensions of the exhaust steam housing and the sizes of the outlet surfaces of the partial diffusers are coordinated.
- the diffuser is designed so that half of the exit surface S12 'of the inner partial diffuser 10 over the entire rotation of the diffuser is approximately equal to the dashed hatched area 28 in the parting plane 23 between upper and lower half of the diffuser.
- the surface 28 is formed by the axially further outwardly disposed baffle 27 ', the radially further outside placed hood 21', a turbine-facing wall 31 and the Abdampfleitblech 8 '.
- the surface 28 is finally closed by a fictitious axially extending line 30 between the Abdampfleitblech 8 'and the wall 31. Further, the sum of the exit surfaces S22 and S32 of the other two partial diffusers is approximately equal to the solidified hatched area 29 in the parting plane. This surface 29, the Abdampfleitblech 8 ', through the line 30, the wall 31 is formed. Further, in this case, the exit surface S13 'in the lower half of the diffuser falls in the same place as the exit surface S12' for the upper half of the diffuser.
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Description
Diese Aufgabe ist durch einen axial/radialen Dreikanal-Diffusor mit Abdampfgehäuse gemäss Anspruch 1 gelöst. Der Dreikanal-Diffusor weist drei Teildiffusoren auf, einen inneren, mittleren und äusseren Teildiffusor, die durch einen inneren Diffusorring, einen äusseren Diffusorring und zwei zwischen den Diffusorringen angeordneten Leitbleche gebildet sind. Ein erstes Teilstück des inneren Diffusorrings ist dabei bezüglich der Nabe in einem nach innen, zur Rotorachse hin gerichteten Knickwinkel und ein erstes Teilstück des äusseren Diffusorrings ist in einem bezüglich dem Schaufelkanal auf der Höhe der letzten Laufschaufelreihe nach aussen, von der Rotorachse weg gerichteten Knickwinkel angeordnet.
Die radiale Erstreckung der Teildiffusoren dient weiter der Reduktion der Tangentialgeschwindigkeit auf natürliche Weise. Die Teildiffusoren sind dadurch für alle Betriebsbedingungen bezüglich der Reduktion der Tangentialgeschwindigkeit optimal. Ferner ist der konstruktive Aufwand für die Leitbleche relativ klein und für die Reduktion der Tangentialgeschwindigkeit sind keine weiteren konstruktiven Massnahmen wie Umlenkungs- und Strömungsrippen notwendig.
Der minimale Abstand zwischen der letzten Schaufelreihe und den Vorderkanten der Leitbleche trägt weiter zur optimalen Abschirmung der Spaltströmung und zur Vermeidung von Strömungsinterferenzen und Stromlinienkonvergenzen bei.
Das Verhältnis von Länge zu Kanalhöhe jedes Teildiffusors von 2.5 und mehr ermöglicht eine sachte Umlenkung von der axialen, oder diagonalen, zur radialen Strömungsrichtung, was die Ablösung der verzögerten Strömung, selbst bei einem Verhältnis der Austrittsfläche zu Eintrittsfläche von 1.6, verhindert.
In einer ersten besonderen Ausführung der Erfindung liegen die Anfangstangenten der Leitbleche in einem Winkelbereich um die ersten Knickpunkte der Leitbleche und um eine Referenzanfangstangente, die zumindest näherungsweise durch den ersten Knickpunkt des Leitblechs und durch den Schnittpunkt der geradlinigen approximierten Grenzen des Schaufelkanals führen.
In einer weiteren Ausführung sind die Vorderkanten der Leitbleche am Strömungseintritt des Diffusors profiliert ausgebildet, wodurch eine sanfte Beschleunigung beim Eintritt in die Teildiffusoren bewirkt wird.
Die Leitbleche sind jeweils durch Streben oder Stützen getragen, die sich vom inneren und äusseren Diffusorring zu den beiden Leitblechen erstrecken. Der mittlere Teildiffusor bleibt dabei frei von Stützen und weist dadurch minimale Strömungsstörungen und Verluste auf.
Die Leitbleche sind über der Kanalhöhe des Diffusors mit Rücksicht auf das Totaldruckprofil so verteilt, dass eine strömungsmechanisch optimale Flächenverteilung auf die drei Teilkanäle erzielt wird. Das erste Leitblech 8 ist so angeordnet, dass der innere Teildiffusor 10 eine Strömungseintrittsfläche besitzt, die beispielsweise circa 60% der Strömungseintrittsfläche des gesamten Diffusors ist. Das zweite Leitblech 9 ist weiter so angeordnet, dass der mittlere Teildiffusor 11 beispielsweise eine Strömungseintrittsfläche von circa 30% der gesamten Strömungseintrittsfläche besitzt. Hierdurch entfällt der Grossteil der Gesamteintrittsfläche auf die beiden ersten Kanäle 10 und 11. Der äussere Teildiffusor 12 besitzt hingegen eine Strömungseintrittsfläche von beispielsweise circa 10% der gesamten Strömungseintrittsfläche.
Die Diffusoraustrittsfläche ist so ausgelegt, dass das Verhältnis der Austrittsfläche zur Eintrittsfläche des gesamten Diffusors, also seiner oberen und unteren Hälfte, circa 2 beträgt.
Bei den einzelnen Teildiffusoren verhalten sich die geometrischen Verhältnisse von Austritts- zu Eintrittsfläche wie folgt.
Für den inneren Teildiffusor 10 beispielsweise beträgt das Verhältnis der Austrittsfläche S12 in der oberen Hälfte des Diffusors zur Eintrittsfläche S11 circa 1.3.
Für den mittleren Teildiffusor 11 baträgt das Verhältnis der Austrittsfläche S22 zur Eintrittsfläche S21 circa 2.1.
Für den äusseren Teildiffusor beträgt das Verhältnis von Austrittsfläche S32 zur Eintrittsfläche S31 circa 3.3 . Solche Flächenverhältnisse sind die Voraussetzung dafür, dass der Wirkungsgrad der Turbine wesentlich gesteigert werden kann.
Diese geometrische Auslegung der Leitbleche in Bezug auf die Grenzen des Beschaufelungskanals gilt auch für weitere Gehäusekonturen und Schaufeltypen, wie zum Beispiel für vollständig konisch geradlinige Gehäusekonturen, für Gehäusekonturen, bei denen das Teilstück über der letzten Laufschaufelreihe zylindrisch oder nahezu zylindrisch verläuft. Weiter ist diese Geometrie nicht nur bei Laufschaufeln mit Spitzendichtung sondern auch bei Laufschaufeln mit Deckbändem anwendbar. In diesem Fall verläuft die gehäuseseitige Grenze des Schaufelkanals durch den Schnittpunkt von Hinterkante der letzten Laufschaufel und dem Deckband.
Die hochenergetische, supersonische Spaltströmung aus der letzten Laufschaufelreihe hingegen gelangt in den äusseren Teildiffusor 12, wobei dessen Kanalhöhe in Relation zur vorherrschenden Spaltströmung bestimmt ist. Die Spaltströmung wird durch den äusseren Teildiffusor 12 separat vom Hauptteil der Strömung in das Abdampfgehäuse 20 geführt.
Weiter ist die Summe der Austrittsflächen S22 und S32 der beiden anderen Teildiffusoren ungefähr gleich der durchzogen schraffierten Fläche 29 in der Trennebene. Diese Fläche 29 wird das Abdampfleitblech 8', durch die Linie 30, die Wand 31 gebildet.
Ferner fällt die Austrittsfläche S13' in der unteren Hälfte des Diffusors in diesem Fall auf die gleiche Stelle wie die Austrittsfläche S12' für die obere Hälfte des Diffusors.
- 1
- Rotor
- 2
- Rotorachse
- 3
- Laufschaufel
- 4, 4'
- innerer Diffusorring, erstes Teilstück des inneren Diffusorrings
- 5
- äusserer Diffusorring
- 5'
- erstes Teilstück des äusseren Diffusorrings
- 6
- Nabe
- 7
- Schaufelträger
- 7'
- letztesTeilstück des Schaufelträgers
- 8
- erstes Leitblech
- 8'
- Abdampfleitblech
- 9
- zweites Leitblech
- 10
- innerer Teildiffusor
- 11
- mittlerer Teildiffusor
- 12
- äusserer Teildiffusor
- 13
- Stützen oder Streben
- 15
- geometrische Mittellinie der Teildiffusoren
- ε1 , ε2
- Neigungswinkel der Anfangstangente der Leitbleche bezüglich Rotorachse
- 1, 2, 3
- Umlenkungswinkel der Teildiffusoren
- N
- Knickwinkel des inneren Diffusorrings
- Z
- Knickwinkel des äusseren Diffusorrings
- L
- Umlenkwinkel des Abdampfleitblechs
- a
- Abstand Laufschaufel-Vorderkante Leitblech
- hw
- Länge der letzten Laufschaufelreihe
- e
- Profilierungslänge der Leitblechvorderkanten
- δ
- Dicke der Leitbleche
- 20
- Abdampfgehäuse
- 21,21'
- obere Hälfte des Abdampfgehäuses, Haube oder Wand
- 22
- untere Hälfte des Abdampfgehäuses
- 23
- Trennebene
- 24
- Austrittsfläche aus dem Abdampfgehäuse
- 25
- Durchströmfläche der Trennebene für Teildiffusoren 11 und 12
- 26
- Durchströmfläche der Trennebene für Teildiffusor 10
- 27,27'
- Prallwand
- 28
- Durchströmfläche der Trennebene für Teildiffusor 10 in weiterer Variante
- 29
- Durchströmfläche der Trennebene für Teildiffusoren 11 und 12 in weiterer Variante
- 30
- Hilfstrennlinie
- 31
- der Turbine zugewandte wand des Abdampfgehäuses
- S11
- Eintrittsfläche in inneren Teildiffusor 10
- S12
- Austrittsfläche aus dem inneren Teildiffusor 10 in der oberen Hälfte des Diffusors
- S12'
- Austrittsfläche aus dem inneren Teildiffusor 10 in der oberen Hälfte des Diffusors in der weiteren Variante
- S13
- Austrittsfläche aus dem inneren Teildiffusor 10 in der unteren Hälfte des Diffusors
- S13'
- Austrittsfläche aus dem inneren Teildiffusor 10 in der unteren Hälfte des Diffusors in der weiteren Variante
- S21
- Eintrittsfläche in den mittleren Teildiffusor 11
- S22
- Austrittsfläche aus dem mittleren Teildiffusor 11
- S31
- Eintrittsfläche in den äusseren Teildiffusor 12
- S32
- Austrittsfläche aus dem äusseren Teildiffusor 12
Claims (15)
- Axial/radialer Dreikanal-Diffusor mit Abdampfgehäuse für Niederdruckdampfturbine, welcher den Beschaufelungsabdampf in das Abdampfgehäuse (20) führt, mit einem inneren Diffusorring (4), einem äusseren Diffusorring (5) und zwei Leitblechen (8, 9), welche den Diffusor in drei Teildiffusoren, einen inneren Teildiffusor (10), einen mittleren Teildiffusor (11) und einen äusseren Teildiffusor (12) aufteilen,
wobei der innere Diffusorring (4) bezüglich der Nabe der Niederdruckdampfturbine in einem Knickwinkel (N) und der äussere Diffusorring (5) bezüglich dem letzten Teilstück (7') des Schaufelträgers (7) der Niederdruckdampfturbine in einem Knickwinkel (Z) angeordnet sind,
dadurch gekennzeichnet, dass
die zwei Leitbleche (8, 9) sich über die gesamte Länge des Diffusors erstrecken, und die zwei Leitbleche (8,9) zwischen dem inneren Diffusorring (4) und dem äusseren Diffusorring (5) so verteilt sind, dass auf den inneren und mittleren Teildiffusor (10, 12) 88-90% der Eintrittsfläche des Diffusors und 10-12% der Eintrittsfläche auf den äusseren Teildiffusor (12) entfällt,
und die Anfangstangenten der Leitbleche (8,9) und die gehäuseseitige Grenze des Schaufelkanals der letzten Stufe die geradlinig approximierte nabenseitige Grenze des Schaufelkanals näherungsweise in einem gemeinsamen Punkt schneiden. - Axial/radialer Dreikanal-Diffusor nach Anspruch 1
dadurch gekennzeichnet, dass
das Verhältnis der Austrittsfläche (S22) zur Eintrittsfläche (S21) des mittleren Teildiffusors (11) mindestens zwei, das Verhältnis der Austrittsfläche (S32) zur Eintrittsfläche (S31) des äusseren Teildiffusors (12) mindestens drei und das Verhältnis der Austrittsfläche (S12) zur Eintrittsfläche (S11) des inneren Teildiffusors (10) zumindest in der unteren Hälfte des Diffusors im Bereich von 1.5 bis 1.8 liegt. - Axial/radialer Dreikanal-Diffusor nach Anspruch 2
dadurch gekennzeichnet, dass
für jeden Teildiffusor (10, 11, 12) zumindest in der unteren Hälfte des Diffusors das Verhältnis seiner Länge zu seiner Kanalhöhe in der Eintrittsebene mindestens gleich 2.5 ist. - Axial/radialer Dreikanal-Diffusor nach Anspruch 3
dadurch gekennzeichnet, dass
das Verhältnis der Gesamtaustrittsfläche zur Gesamteintrittsfläche des Dreikanal-Diffusors circa zwei beträgt. - Axial/radialer Dreikanal-Diffusor nach Anspruch 4
dadurch gekennzeichnet, dass
die Eintrittsfläche (S11) des inneren Teildiffusors (10) 55-60%, die Eintrittsfläche (S21) des mittleren Teildiffusors (11) 30-35% und die Eintrittsfläche (S31) des äusseren Teildiffusors (12) 10-12% der Gesamteintrittsfläche des Diffusors beträgt. - Axial/radialer Dreikanal-Diffusor nach Anspruch 5,
dadurch gekennzeichnet, dass
die Anfangstangenten der Leitbleche (8, 9) jeweils in einem Winkelbereich von 8° um die ersten Knickpunkte (B, C) der Leitbleche (8,9) und um eine Referenzanfangstangente liegen, die durch die ersten Knickpunkte (B,C) der Leitbleche (8,9) und durch den Schnittpunkt (A) der geradlinig approximierten naben- und gehäuseseitigen Grenzen des Schaufelkanals der Endstufe führen. - Axial/radialer Dreikanal-Diffusor nach Anspruch 6
dadurch gekennzeichnet, dass
der Abstand (a) zwischen den Vorderkanten der Leitbleche (8, 9) und der Hinterkante der letzten Laufschaufel circa 4% der gesamten Höhe (hw) der Laufreihe beträgt. - Axial/radialer Dreikanal-Diffusor nach Anspruch 7
dadurch gekennzeichnet, dass
die Vorderkanten der Leitbleche (8, 9) profiliert ausgebildet sind. - Axial/radialer Dreikanal-Diffusor nach Anspruch 8
dadurch gekennzeichnet, dass
die Leitbleche (8, 9) durch Stützen (13) getragen sind, die sich vom inneren Diffusorring (4) und äusseren Diffusorring (5) zu den Leitblechen (8, 9) erstrecken und stromabwärts einen zunehmenden Durchmesser aufweisen, und der mittlere Teildiffusor (11) frei von Stützen ist. - Axial/radialer Dreikanal-Diffusor nach Anspruch 9
dadurch gekennzeichnet, dass
an dem Leitblech (8), das zwischen dem inneren Teildiffusor (10) und dem mittleren Teildiffusor (11) angeordnet ist, in einer radialen Verlängerung ein Abdampfleitblech (8') angeordnet ist. - Axial/radialer Dreikanal-Diffusor nach Anspruch 10
dadurch gekennzeichnet, dass
die Leitbleche (8, 9) eine Dicke (δ) aufweisen, die circa 5% der Kanalhöhe des mittleren Teildiffusors (11) beträgt. - Axial/radialer Dreikanal-Diffusor nach einem der vorangehenden Ansprüche 1-11
dadurch gekennzeichnet, dass
die Summe der Austrittsfläche (S22) des mittleren Teildiffusors (11) und der Austrittsfläche (S32) des äusseren Teildiffusors (12) ungefähr gleich jener Fläche (25) in der Trennebene (23) zwischen der oberen und unteren Hälfte des Diffusors ist, welche zwischen der Haube (21) des Abdampfgehäuses (20) und dem Abdampfleitblech (8') zwischen dem inneren Teildiffusor (10) und mittleren Teildiffusor (11) gebildet wird. - Axial/radialer Dreikanal-Diffusor nach Anspruch 12
dadurch gekennzeichnet, dass
die Austrittsfläche (S12) des inneren Teildiffusors (10) in der oberen Hälfte des Diffusors in einem Verhältnis von circa 1.3 zur Eintrittsfläche (S11) des inneren Teildiffusors (10) steht und die Austrittsfläche (S12) des inneren Teildiffusors (10) über die gesamte Rotation des Dreikanal-Diffusors gleich der Hälfte der Fläche (26) in der Trennebene (23) zwischen der oberen Hälfte (21) und der unteren Hälfte (22) des Abdampfgehäuses (20) ist, die von der Prallwand (27), der Haube (21) des Abdampfgehäuses (20) und dem Leitblech (8) zwischen dem inneren und mittleren Teildiffusor (11,12) und dem Abdampfleitblech (8') gebildet wird. - Axial/radialer Dreikanal-Diffusor nach einem der vorangehenden Ansprüche 1-11
dadurch gekennzeichnet, dass
die Austrittsfläche (S12') des inneren Teildiffusors (10) in der oberen Hälfte des Diffusors in einem Verhältnis von circa 1.8 zur Eintrittsfläche (S11) des inneren Teildiffusors (10) steht und die Austrittsfläche (S12') des inneren Teildiffusors (10) in der oberen Hälfte des Diffusors über die gesamte Rotation des Dreikanal-Diffusors ungefähr gleich der Hälfte der Fläche (28) in der Trennebene (23) zwischen der oberen Hälfte (21) und der unteren Hälfte (22) des Abdampfgehäuses (20) ist, die von der Prallwand (27') und der Haube (21') des Abdampfgehäuses (20), vom Abdampfleitblech (8') sowie einer axialen Linie (30), die vom Abdampfleitblech (8') zu einer zur Turbine gewandten Wand (31) des Abdampfgehäuses (20) führt, gebildet wird
und die Summe der Austrittsfläche (S22) des mittleren Teildiffusors (11) und der Austrittsfläche (S32) des äusseren Teildiffusors (12) über die gesamte Rotation ungefähr gleich der Hälfte der Fläche (29) in der Trennebenen (23) zwischen der unteren und oberen Hälfte des Abdampfgehäuses (20) ist, die durch das Abdampfleitblech (8'), durch die der Turbine zugewandten Wand (31) des Abdampfgehäuses (20) und durch die axiale Linie (30) von dem Abdampfleitblech (8') zur der Turbine zugewandten Wand (31) gebildet wird. - Axial/radialer Dreikanal-Diffusor nach einem der vorangehenden Ansprüche 11-14
dadurch gekennzeichnet, dass
die Gesamtaustrittsfläche des Dreikanal-Diffusors etwa 15% kleiner ist als die Austrittsfläche (24) des Abdampfgehäuses (20).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10037684 | 2000-07-31 | ||
DE10037684A DE10037684A1 (de) | 2000-07-31 | 2000-07-31 | Niederdruckdampfturbine mit Mehrkanal-Diffusor |
Publications (3)
Publication Number | Publication Date |
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EP1178183A2 EP1178183A2 (de) | 2002-02-06 |
EP1178183A3 EP1178183A3 (de) | 2003-07-23 |
EP1178183B1 true EP1178183B1 (de) | 2005-05-11 |
Family
ID=7651095
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EP01117519A Expired - Lifetime EP1178183B1 (de) | 2000-07-31 | 2001-07-20 | Niederdruckdampfturbine mit Mehrkanal-Diffusor |
Country Status (4)
Country | Link |
---|---|
US (1) | US6533546B2 (de) |
EP (1) | EP1178183B1 (de) |
JP (1) | JP4791658B2 (de) |
DE (2) | DE10037684A1 (de) |
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-
2000
- 2000-07-31 DE DE10037684A patent/DE10037684A1/de not_active Withdrawn
-
2001
- 2001-07-20 EP EP01117519A patent/EP1178183B1/de not_active Expired - Lifetime
- 2001-07-20 DE DE50106175T patent/DE50106175D1/de not_active Expired - Lifetime
- 2001-07-30 JP JP2001230396A patent/JP4791658B2/ja not_active Expired - Fee Related
- 2001-07-31 US US09/917,906 patent/US6533546B2/en not_active Expired - Lifetime
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DE102010044819B4 (de) | 2009-09-14 | 2022-12-15 | General Electric Technology Gmbh | Axialturbine und ein Verfahren zum Abführen eines Stroms von einer Axialturbine |
CN102373960A (zh) * | 2010-08-20 | 2012-03-14 | 通用电气公司 | 毂部流道轮廓 |
CN102373960B (zh) * | 2010-08-20 | 2016-03-02 | 通用电气公司 | 涡轮设备 |
Also Published As
Publication number | Publication date |
---|---|
DE10037684A1 (de) | 2002-02-14 |
US20020127100A1 (en) | 2002-09-12 |
DE50106175D1 (de) | 2005-06-16 |
US6533546B2 (en) | 2003-03-18 |
JP2002081301A (ja) | 2002-03-22 |
EP1178183A2 (de) | 2002-02-06 |
JP4791658B2 (ja) | 2011-10-12 |
EP1178183A3 (de) | 2003-07-23 |
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