EP1642075B1 - Exhaust steam line for steam plants - Google Patents

Abstract

The steam drainage line (5) has a number of air-cooled condensation elements connection to a main steam drainage line (10) via individual branch lines (6), with the cross-section of the main steam drainage line reduced in stages after each branch line tap-off point (7). The main steam drainage line is inclined upwards at an angle (W) to the horizontal (H) in the flow direction of the steam.

Description

The invention relates to an exhaust steam line for steam power plants with the features of the preamble of claim 1.

The exhaust steam line of a steam power plant, in particular a steam turbine, serves to guide the exhaust steam from the exit of the steam turbine, that is, from the turbine exhaust steam outlet via a main steam line to branch lines, via which the exhaust steam is fed to individual condensation elements. This is largely done in vacuum operation. The routing of an exhaust steam line for an air-cooled condenser is usually carried out with diameters between 1 m and 10 m.

Within the exhaust steam line occur local flow losses, which are caused by a local change in the flow cross-section or the flow direction. In known exhaust steam lines, despite the stepped reduction of the cross-section of the pipe at the connection point of the branch pipe, there is a pressure loss at the connection opening of the branch pipe to be expected by the exhaust steam flowing freely past this connection opening. From DE-PS 1 945 314 a Abdampfleitung is known, in which the lowest possible pressure loss at the branch points of branch lines should be achieved in that the reduction of the line cross section is achieved by two nested, mutually sealed pipe sections of different diameters, wherein the smaller pipe piece is pushed into the larger to form an annular space so far that the connection opening of the branch line is covered in the larger pipe section in the radial direction. A disadvantage of this embodiment is that the pressure loss can not be reduced to a certain minimum. In principle, losses occur in the area of the connection points during the diversion of the exhaust steam flow. These flow losses are accompanied by pressure losses that occur due to the length of the pipe.

Runs the main steam pipe horizontally near the bottom, must be provided correspondingly long running, upwardly branching outlets. Therefore, the horizontal main exhaust steam line was mounted higher, so that the individual branch lines can be made shorter. However, this entails the need to provide at least two 90 ° deflections within the main steam line, with blade manifolds to be installed to reduce the drag coefficient within the manifold. These can on the one hand have a very high weight of 7 to 20 t and bring to the other an increased installation costs with it.

On this basis, the invention is based on the object of providing an exhaust steam line for steam power plants with reduced assembly and material costs, in which at the same time the pressure loss is as low as possible.

The invention solves this problem by an exhaust steam line with the features of claim 1. The core of the invention is the arrangement of Hauptabdampfleitung at an angle to the horizontal, and so that the main exhaust steam line increases in the flow direction of the exhaust steam, wherein the Abknickwinkel measured between a longitudinal section of the main exhaust pipe and the branch lines is less than 90 ° and the length of the individual branch lines decreases in the flow direction of the exhaust steam.

The basic idea of the new cable routing is based on the principle of the most direct possible connection between the connection of the main exhaust steam line at a low height level to a plurality of connections of the branch pipes to distributor pipes at a higher height level. The rising arrangement of the main steam discharge line has the advantage that the individual branch pipes, although they have a different length from each other, but can be designed to be shorter overall than in an exclusively horizontally extending Hauptabdampfleitung. As a result, the length of the flow path is reduced overall.

The lower material usage leads to weight savings in the exhaust steam line and not least also to savings in costs and also in terms of assembly. Among other things, the cost savings in the assembly result from the fact that the branch lines composed of individual ring segments are made shorter and therefore less welding work must be carried out in order to connect the ring segments to one another. In addition, the total assembly weight is lower, allowing for easier handling. Finally, the foundation loads are lower, so that smaller foundations can be used.

A significant advantage over orthogonally configured arrangements between the main exhaust steam line and the branch lines is that the flow losses leading to pressure losses are reduced. The pressure loss is proportional to the resistance coefficient of the piping system. The drag coefficient is largely determined by the number and design of the manifolds and pipe branches. In the area of the connection points of the branch lines, the resistance coefficient is reduced by the oblique position of the main exhaust steam line according to the invention. Basically, the drag coefficient is the smaller the smaller the kink angle. Of the Abknickwinkel is measured between the cross-sectional plane of the main steam and the cross-sectional plane of a branch line. For parallel cross-sectional planes this angle is 0 °. In the arrangement according to the invention, the usual bending angle of 90 ° is reduced by the angle of inclination of the main exhaust steam line, so that smaller resistance coefficients result at each connection point of a branch line than with a 90 ° deflection. In total, this results in a much lower loss height or a lower pressure drop within the exhaust steam line than in the known orthogonally configured arrangements.

A further advantage is that the main exhaust steam line rises relatively gently from the lower height level of the steam turbine. The bending angle measured in relation to the horizontal lies in the range of 5 ° to 60 ° according to the features of claim 2. Preferably, the angle is in a range of 10 ° to 20 °. Larger angles would have the disadvantage that the resistance coefficient in the transition region from the horizontal length section of the main exhaust steam line to the inclined length section of the main exhaust steam line would have a greater resistance coefficient, so that larger pressure losses occur in good time. The pressure losses at very low Abknickwinkeln, especially at Abknickwinkeln of less than 10 °, are compared to the commonly used 90 ° -Krümmern much lower. In addition, additional redirecting means, such as e.g. Schaufelkrümmer be omitted, whereby the exhaust steam line according to the invention can be designed structurally simpler. Furthermore, there is a better condensate return against the steam flow direction in the main steam line.

The choice of the Abknickwinkels depends on the length of the main steam and the respective plant conditions. It is essential that no 90 ° -Krümmer should be provided within the wiring harness to change the height level of the main steam line, but only bends that are much smaller than 90 °.

In the context of the invention, it is possible that a first main steam line and a second main steam line with opposite slope are connected to a common central line. This corresponds essentially to a V-shaped arrangement of the main steam exhaust pipes with central exhaust steam supply, for which the above-mentioned advantages also apply.

In the embodiment of claim 7, at least one of the branch lines is arranged inclined at an angle to the main exhaust steam line in the flow direction of the exhaust steam. That the upper ends of the branch lines and their junctions are not in the same vertical plane. With this arrangement, the flow losses at the individual connection points are further reduced.

It is considered to be particularly advantageous if the branch line provided at the outer end of the main exhaust steam line is arranged in the same orientation as the main steam line. "Same orientation" in the context of the invention is to be understood as a parallelism or congruence of the longitudinal axes of the main steam line and branch line. In this configuration, the angle of the main exhaust pipe to the horizontal is determined decisively by the horizontal and vertical distance of the last condensation element from the turbine. Since the Hauptabdampfleitung goes without curvature in the end-side branch line, the Hauptabdampfleitung is correspondingly shorter. In this arrangement, the total weight is further reduced in spite of the slightly longer executed last branch line in the sum.

In a further embodiment of the exhaust steam line according to the invention it is provided that at least one branch line is divided into at least two sub-lines. The exhaust steam flowing through the branch line is thereby divided into two partial streams which flow to one condensation element each. Under certain geometric conditions, it is more appropriate to divide the branch line into two sub-lines, instead to provide a further branch line, which would have to be connected directly to the main steam line. The additional branching of the branch line in two or more sub-lines, it is possible to further reduce the cost of materials and to reduce the total assembly weight. Advantageously, the sub-lines are arranged inclined in an angle to the branch line sloping. In this way, the flow losses are kept as low as possible. The bending angles are significantly smaller than 90 °.

The subject of claim 11 is that in the region of at least one connection point of a branch line or a partial line a baffle for the division of the exhaust steam is arranged in Abdampfteilströme. The baffle has the purpose to divide the exhaust steam with the lowest possible pressure losses. Preferably, the pressure losses in each of the exhaust partial streams are identical. In the context of claim 12 it is provided that the ratio of Abdampfteilströme corresponds to the ratio of the following on a connection point distribution pipes. If, for example, a total of five branch lines are branched off from a main exhaust steam line, with equal amounts of the exhaust steam being supplied to the individual distributor pipes, then it is necessary to branch off at the first connection point 1/5 of the exhaust steam flow in the direction of flow. At the next junction, branch off from the reduced partial exhaust steam 1/4. Accordingly, 1/3 and 1/2 at the subsequent connection points. If a branch line is subdivided into two sub-lines, which lead to one distributor pipe in each case, twice the amount of exhaust steam must be supplied to the corresponding branch line.

The inclined wiring of the main exhaust pipe allows a freer cooling air supply below the capacitor elements, which can lead to a lower platform height and thus to reduce the steel construction costs depending on the arrangement. In addition, the accessibility of the system is improved because you can go under the main steam line.

Figuren 1 und 2

den Stand der Technik bezüglich der Leitungsführung von Abdampfleitungen für luftgekühlte Kondensatoren;

Figuren 3.1 und 3.2

schematische Darstellungen einer ersten und zweiten Ausführungsform der erfindungsgemäßen Abdampfleitung;

Figuren 4 und 5

den Stand der Technik einer Abdampfleitung mit zentraler Dampfzuführung;

Figuren 6.1 und 6.2

zwei Ausführungsformen der erfindungsgemäßen Abdampfleitung in V-förmiger Konfiguration mit zentraler Abdampfzuführung und

Figur 7

eine weitere Ausführungsform der erfindungsgemäßen Abdampfleitung und

Figur 8

eine Variante der Ausführungsform der Figur 7

The invention will be explained in more detail with reference to the embodiments schematically illustrated in the drawings. Show it:

Figures 1 and 2

the prior art regarding the routing of exhaust ducts for air-cooled condensers;

Figures 3.1 and 3.2

schematic representations of a first and second embodiment of the exhaust steam line according to the invention;

FIGS. 4 and 5

the prior art of an exhaust steam line with central steam supply;

Figures 6.1 and 6.2

two embodiments of the exhaust steam line according to the invention in a V-shaped configuration with central exhaust steam supply and

FIG. 7

a further embodiment of the exhaust steam line according to the invention and

FIG. 8

a variant of the embodiment of Figure 7

Figure 1 shows the state of the art an exhaust steam line 1 with a horizontal Hauptabdampfleitung 2 with this perpendicularly upwardly branching branch lines 3. At the upper ends of the branch lines 3 distribution pipes 30 are connected by condensation elements not shown. This configuration of an exhaust steam line 1 has the disadvantage that the individual branch lines 3 are very long and must be supported according to their length. Since compensators are provided in the branch lines 3 for compensation of thermal changes in length, the individual sections of the branch lines 3 must be position-oriented on the steel frame (not shown). The effort for this is not insignificant. The line length is relatively large in the sum, so that considerable tonnages have to be transported. The mounting effort is therefore also high.

In the embodiment of Figure 2, which also belongs to the prior art, a horizontal length portion of the main exhaust pipe 2 is provided in a raised position, so that the individual branch lines 3 can be made shorter. This has the advantage that the correspondingly lighter branch lines 3, despite the inclusion of compensators with less effort are iageorientierbar. On the other hand, an at least two-fold 90 ° bend of the main exhaust duct is required to redirect the exhaust steam emerging in the horizontal direction into the vertical length section and from the vertical length section in turn into the horizontal length section. These deflections by 90 ° would lead to high flow losses without the use of additional blade elbow within the manifold. For larger systems, the mass of such a vane is about 7 - 20 t, which must be raised in the raised position. This high mass is also problematic in terms of earthquake resistance. Since the horizontal length of the main steam line including the vane has a significant mass in the transition to the vertical length of the main steam line, it is necessary to use special support structures in earthquake-prone areas to intercept vertical-acting earthquake shocks.

In the prior art spring supports 4 are used to compensate for the thermally induced change in length to ensure adequate support of the horizontally extending length portion of the main steam line. However, there is a risk that in vertical earthquake shocks, the relatively high mass of the main exhaust pipe and the blade elbow can not be absorbed by the springs of the spring struts, so additional shock brakes must be provided in the form of hydraulic dampers. These shock brakes in combination with The springs of the spring supports 4 form a spring-damper arrangement, which prevents the forces introduced during an earthquake from the main steam line 2 to continue into the steam turbine to which the main steam line 2 is finally connected. The spring supports 4 in combination with the impact brakes are relatively complex components, since they must be provided several times depending on the length of the main steam pipe 2 to ensure a uniform lifting or lowering of the horizontal length portion of the main steam line 2. In Figure 2, the other spring supports 4 are indicated schematically by double broken lines.

FIG. 3.1 shows the exhaust steam line 5 according to the invention, which differs from the embodiments of FIGS. 1 and 2, that is to say from the prior art in that the main steam exhaust line 10 is arranged at an angle W to the horizontal H in the direction of flow of the exhaust steam. In this embodiment, the angle W is 10 °. A total of five branch lines 6 extending vertically upwards are connected to the main exhaust steam line 10, wherein the line cross-section decreases after each connection point 7 of a branch line 6. In this configuration, the right branch line 6 in the image plane is much shorter than the first outgoing branch line 6 in the left half of the picture. Due to the inclined arrangement, the bending angle W1 measured between the rising length section 9 of the main exhaust steam line 10 and the respective branch lines 6 is less than 90 °. In this embodiment, it is 80 °. The resistance coefficients of the pipe branches are therefore smaller than with a 90 ° branch.

Another advantage is that the Abknickwinkel W2 existing between the horizontal length section 8 and the increasing length section 9 of the main exhaust pipe 10 leads to very low resistance coefficients within this bend, so that the assembly of a vane bend is not required. The exhaust steam can at reduced total length of Lines without the use of vane elbows at the same time reduced pressure losses are supplied to the condensation elements not shown at the upper ends of the branch lines 6.

The rising length section 9 of the main exhaust pipe 10 is mounted on pendulum supports 11. The pendulum supports 11 compensate for acting in the longitudinal direction of the rising length portion 9 thermal length changes. Elaborate spring struts and shock brakes are not required in this arrangement. The rising length section 9 does not exert any inadmissible forces on the steam turbine in the case of vertically acting earthquake loads, so that the constructional outlay for an exhaust steam line 5 configured according to the invention is lower overall. Due to the rising course of the main exhaust steam line 10, a freer air inlet below the platform of the air-cooled condensation elements is possible. In addition, the accessibility to the entire system is improved. In the embodiment of FIG. 1, very long paths often had to be covered, since the direct route was blocked by the main exhaust steam line 2 arranged near the bottom. In the arrangement according to the invention, it is possible to pass under the main steam discharge line 10. Another advantage is the reduced attack surface of the exhaust steam line 5 for wind loads. It becomes clear that, in the case of the routing of FIGS. 3.1 and 3.2, a lower attack surface is present overall than in the embodiment of FIG. 1 or 2.

The embodiment of Figure 3.2 differs from that of Figure 3.1 in that the individual branch lines 6 ', 6 ", 6'" are not aligned perpendicular to the horizontal, but also extend obliquely rising. In this embodiment, the pitch of the rising length portion 9 of the main exhaust pipe or the angle W is set so that the branch pipe 6 "located at the outer end of the rising length portion 9 has the same orientation as the rising length portion 9 of the main exhaust pipe Although the angle W is greater than the horizontal H in FIG. 3.2, it is larger than in the embodiment FIG. 3.1, so that slightly higher flow losses occur in the transition region from the horizontal length section 8 to the rising length section 9, but the angle of deflection between the rising length section 9 and the branch lines 6 ', 6 ", designated W3', W3", is smaller than in the embodiment 3.1, so that these flow losses at the connection points 7 of the individual branch lines 6 ', 6 "are considerably less, both individually and in total Significant material and weight savings, thus also lower assembly weights and lower assembly costs are possible resulting in lower intrinsic, wind, earthquake and foundation loads.

Each located between two connection points 7 portion of the rising length portion 9 is supported by a support 11 '. In principle, the bending angles W3 ', W3 "to the outer end of the rising length section 9 can become smaller and even approach zero, as FIG. 3.2 shows.

In the prior art also exhaust steam lines 12, 13 are known, as shown in Figures 4 and 5. These embodiments essentially correspond to the mirrored on a vertical axis arrangements of Figures 1 and 2 with the difference that here a total of 4 to 12 branch lines are provided, which are connected via the respective transversely departing branches of Hauptabdampfleitungen 14 to a central line 15. In Figure 5, the already explained in Figure 2 spring supports 4 are also drawn in this embodiment. The disadvantages were explained with reference to FIGS. 1 and 2 and also apply to this embodiment.

In the embodiment according to the invention of FIG. 6.1, a central line 16 is likewise provided, from which in each case a main waste steam line 17 to the right and a main waste steam line 18 to the left with opposite directions Slope gone. The individual Hauptabdampfleitungen 17, 18 are in turn supported by supports 11, in particular pendulum supports. For the advantages of this embodiment, reference is made to the description of Figure 3.1, which also applies to this variant of the exhaust steam line 19 according to the invention.

Basically, the pendulum supports 11 can also be replaced by fixed supports with a Teflon stainless steel Gleitfuß.

The embodiment of Figure 6.2 differs from that of Figure 6.1, inter alia, in that the angle W between the horizontal H and the Hauptabdampfleitungen 17, 18 is increased. The angle W is chosen so that the respective last or end-side branch line 6 "'runs in alignment with the main exhaust steam line 17, 18. That is to say that the outer branch line 6"' has become part of the main exhaust steam line 17, 18. A further difference is that the central branch lines 6 "of the individual main exhaust steam lines 17, 18 do not run perpendicular to the horizontal H, as is the case in Figure 6.1, but are also inclined, the angle between the main steam exhaust line 17, 18 and these branch lines 6 In comparison with the embodiments of FIGS. 4 and 5, it can be seen that the bending angle W3 "is significantly smaller than 90 ° and is also reduced again compared to the embodiment of FIG. 6.1. Also in this embodiment, the shorter and therefore lighter exhaust steam lines 6, 6 ", 6 '" contribute to further reduced intrinsic, wind, earthquake and foundation loads. The assembly weights are also reduced again.

FIG. 7 shows an embodiment of an exhaust steam line 20 in which the angle W between the horizontal H and the main exhaust steam line 21 is increased compared to the previous embodiments. The Hauptabdampfleitung 21 is connected directly to a central line 22 without a horizontally extending center piece. The angle W is in turn chosen so that the last or end-side branch line 6 "'in alignment with the main exhaust steam line 21 runs. Since the Hauptabdampfleitung 21 increases relatively steeply in this embodiment, the Abknickwinkel W2 between the vertically upwardly from the main steam outlet 21 outgoing branch lines 6, 6a and the Hauptabdampfleitung 21 is very small, so that the flow losses in the connection points 7 of Hauptabdampfleitung 21 are low. The special feature of this embodiment is that the branch line 6a is divided into two sub-lines 23, 24, each sub-line 23, 24 leading to a respective condensation element, not shown. The branch line 6a extends from the main steam line 21, starting initially vertically up to a junction 7a. From this connection point 7a branches off in a Abknickwinkel W4 the sub-line 24, while the other sub-line 23 is continued in a straight extension of the branch line 6a vertically upwards. Through the additional part of line 24, a further branch line is saved, which would have to be performed on the Hauptabdampfleitung 21. In particular, in the case of steeper exhaust steam lines 21, it is therefore expedient to provide additional ramifications or partial lines to the individual branch lines.

Figure 8 shows an enlarged section of the embodiment of Figure 7. In contrast to the previous embodiment, baffles 25, 26, 27 are integrated into the connection points 7, 7a. The baffles 25, 26, 27 serve to divide the Abdampfstroms in Abdampfteilströme corresponding to the ratio of the following on a connection point 7, 7a distribution pipes. In the exemplary embodiment of FIGS. 7 and 8, a total of four distributor tubes of the condensation elements are fed with exhaust steam. Accordingly, there is a division of the exhaust steam in a ratio of 1: 1 at each connection point. The uniform distribution is achieved in that the baffles 25, 26, 27 are already mounted in front of the respective connection points 7, 7a within the main steam line 21 and the branch line 6a. A circular cross-section of the main exhaust steam line 21 and the branch line 6a is thereby divided into two semicircles. Differs the cross section of Hauptabdampfleitung 21 and the branch line 6a from a circular cross-section from, there is an area equal division. The respective baffle 25, 26, 27 is preferably designed such that an areal same division is realized both in front of the respective connection point 7, 7a and in the region of the respective connection point 7, 7a. It is essential that the pressure losses of Abdampfteilströme in the region of the connection points 7, 7a are almost equal and the Abdampfmenge is divided into equal parts.

In the embodiment shown, the respective baffles 25, 26, 27 configured angled. The respective front length region 28 of the individual baffles 25, 26, 27 has a length L which corresponds to the diameter D ₁ , D ₂ , D _{3 of} the main steam line 21 and the exhaust steam line 6 a in front of the respective connection point 7, 7 a. The beginning of a connection point 7, 7a is defined as the intersection of the central longitudinal axes of the respective branch line 6, 6a with the main exhaust steam line 21 or as the intersection of the part line 24 with the branch line 6a. It can be seen that the straight course of the respectively front longitudinal sections 28 of the baffles 25, 26, 27 extends beyond this point of intersection, before the respective rear longitudinal section 29 is attached at an angle. The starting point of the rear longitudinal section 29 is selected so that the flow cross sections in the region of the connection points 7, 7a are as equal as possible.

REFERENCE NUMBERS

1 -

exhaust steam

2 -

main steam

3 -

branch line

4 -

spring pieces

5 -

exhaust steam

6 -

branch line
6 '- branch line
6 "branch line
6 "branch pipe

6a -

branch line

7 -

junction

7a -

junction

8th -

horizontal length section

9 -

increasing length section

10 -

main steam

11 -

Pendulum support or Teflon stainless steel sliding foot

11 '-

support

12 -

exhaust steam

13 -

exhaust steam

14 -

main steam

15 -

Central line

16 -

Central line

17 -

main steam

18-

main steam

19 -

exhaust steam

20 -

exhaust steam

21 -

main steam

22 -

Central line

23 -

subline

24 -

subline

25 -

baffle

26 -

baffle

27 -

baffle

28 -

front length range v. 25, 26, 27

29 -

rear length range v. 25, 26, 27

30 -

manifold

D ₁ -

Diameter v. 21

D ₂ -

Diameter v. 21

D ₃ -

Diameter v. 6a

H -

horizontal

L -

length

W -

angle

W1 -

sharp angle

W2 -

sharp angle

W3 -

sharp angle

W3 '-

sharp angle

W3 "-

sharp angle

W4 -

sharp angle

Claims (12)

1. Exhaust steam line for steam power plants, the steam power plants having a plurality of in particular air-cooled condensation elements, with a main exhaust steam line (10, 17, 18, 21) to which are connected at least two branch lines (6, 6', 6", 6"', 6a) which each lead to a condensation element, the line cross section of the main exhaust steam line (10, 17, 18, 21) being reduced in size in terms of line cross section downstream of a connecting point (7) of a branch line (6, 6', 6", 6"', 6a), characterized in that the main exhaust steam line (10, 17, 18, 21) is arranged so as to rise at an angle (W) to the horizontal (H) in the flow direction of the exhaust steam, the bend angle (W1, W2, W3, W3', W3") measured between a longitudinal section (9) of the main exhaust steam line (10, 17, 18, 21) and the branch lines (6, 6' , 6" , 6"' , 6a) being less than 90°, and the length of the individual branch lines (6, 6', 6", 6"', 6a) decreasing in the flow direction of the exhaust steam.
2. Exhaust steam line according to Claim 1, characterized in that the angle (W) is in a range from 5° to 60°.
3. Exhaust steam line according to Claim 1 or 2, characterized in that the angle (W) is in a range from 10° to 20°.
4. Exhaust steam line according to one of Claims 1 to 3, characterized in that a first main exhaust steam line (17) and a second main exhaust steam line (18) of opposing gradient are connected to a common central line (16).
5. Exhaust steam line according to one of Claims 1 to 4, characterized in that the main exhaust steam line (10, 17, 18) is mounted on supports (11) which have compensation means for compensating for thermal length variations of the main exhaust steam line (10, 17, 18).
6. Exhaust steam line according to Claim 5, characterized in that the supports (11) have a pendulum section or a sliding section which can compensate for length variations of the main exhaust steam line (10, 18, 19).
7. Exhaust steam line according to one of Claims 1 to 6, characterized in that at least one of the branch lines (6', 6", 6"') is arranged so as to rise obliquely in the flow direction of the exhaust steam at a bend angle (W3, W3', W3") relative to the main exhaust steam line (10, 17, 18).
8. Exhaust steam line according to one of Claims 1 to 7, characterized in that an end branch line (6"') of the main exhaust steam line (17, 18, 21) has the same orientation as the main exhaust steam line (17, 18, 21).
9. Exhaust steam line according to one of Claims 1 to 8, characterized in that at least one branch line (6a) is divided into at least two sub-lines (23, 24).
10. Exhaust steam line according to Claim 9, characterized in that at least one sub-line (24) is arranged so as to rise obliquely at a bend angle (W4) relative to the branch line (6a).
11. Exhaust steam line according to one of Claims 1 to 10, characterized in that a metal guide plate (25, 26, 27) for dividing the exhaust steam flow into partial exhaust steam flows is arranged in the region of at least one connecting point (7, 7a) of a branch line (6, 6' , 6", 6"', 6a) or of a sub-line (23, 24).
12. Exhaust steam line according to Claim 11, characterized in that the ratio of the partial exhaust steam flows corresponds to the ratio of the distributor pipe (30) downstream of a connecting point (7, 7a).

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