AU2023266966A1 - Condensation plant - Google Patents

Abstract

The invention relates to a condensation plant (1) with upwardly directed tube bundles (10, 11) for condensing steam, with the following features: a) an air chamber has an upwardly widening trapezoidal cross section with an upper side, a lower side and with two longitudinal sides which are inclined in opposite directions with respect to a vertical V and are formed by the two bundles (10, 11), and end sides (30) which are impermeable for cooling air; b) the upper side has at least one outlet opening for heated cooling air, wherein a fan (18) is situated in the outlet opening, which fan is configured to suck colder cooling air, coming from the outside, through the tube bundles (10, 11) into the air chamber (14); c) the tube bundles (10, 11) have heat exchanger tubes which are connected with their ends to steam distributor lines (8, 9) and to condensate collecting lines (12, 13), wherein one of the steam distributor lines (8, 9) and one of the condensate collecting lines (12, 13) are arranged on each of the two longitudinal sides; d) the tube bundles (10, 11) are each at an angle W1 in a range of from 12° to 18° with respect to a vertical V, wherein the tube bundles (10, 11) run at a first spacing from one another at the steam distributor lines (8, 9) and run at a second spacing A2 from one another at the condensate collecting lines (12, 13), wherein the second spacing is at least 1/3 of the first spacing A1.

Description

Condensation plant

The invention relates to a condensation plant according

to the features of claim 1.

Plants of very large dimensions for the condensation of

turbine steam or process steam have been used for many

years in energy technology fields. The condensation

plants can be considered as a special use of air-cooled

heat exchangers. Air-cooled heat exchangers serve for

cooling fluids by means of ambient air in various

processes of the chemical, petrochemical and power

generation industry. The heat exchangers substantially

consist of heat exchanger tubes which are provided with

ribs on the outside for improving the heat transfer. The

heat transfer to the cooling medium - air by means of

heat exchangers by thermal conduction and convection is

frequently denoted as dry cooling. The heat exchanger

tubes of air-cooled heat exchangers are joined together

by welded-on tube plates to form so-called tube bundles.

A tube bundle can have one or more parallel rows of heat

exchanger tubes.

The steam to be cooled flows to the heat exchanger tubes

by means of steam distributor lines which are arranged

on upper tube plates. The outflow of the condensate and

the distribution of steam which is not yet condensed take

place via condensate collectors which are arranged on

lower tube plates. The cooling medium - air is conveyed

through the heat exchanger bundles by means of fans which

are arranged for suctioning or pressurizing. In the A

shaped design, the fans are located in a pressurizing

arrangement below the heat exchanger bundles which are arranged in the shape of a roof. The heat exchanger bundles, which are arranged in the shape of a roof, together with the fans are supported by a supporting structure. The fans are supported by a fan bridge. The inverted design is denoted as a V-shape. Further structural designs in which vertically arranged bundles are arranged spaced apart from one another and define an air chamber which is polygonal in horizontal cross section should also be mentioned. Structural designs also exist where the tube bundles are arranged approximately horizontally.

The standard A-shaped design with fans located therebelow

makes it possible to connect together a plurality of

individual modules and to arrange adjacent to one another

a plurality of rows of tube bundles arranged in an A

shape. However, this design requires a sufficiently large

amount of intake space below the fans and thus a

correspondingly large footprint, with a correspondingly

large substructure.

The V-shaped arrangement of the bundles permits a

slightly lower-level design and also an arrangement of a

plurality of bundles in rows. Relative to the A-shape,

there is the drawback that the fans have to be mounted

at a relatively high level. The effort of supporting the

fans at greater heights also requires a correspondingly

expensive substructure. The required footprint is exactly

the same size as the A-shape.

Relative to tube bundles which are inclined by

approximately 30° (A-shape or V-shape), the vertical

arrangement of the tube bundles has the drawback that the condensate flowing out downwardly blocks the steam flow more readily when the tube bundle is operated in dephlegmator mode, i.e. when the steam to be condensed flows from bottom to top counter to the outflow direction of the condensate. The flow rate and the quantity of condensable steam are thus limited within the tube bundles which are operated in dephlegmator mode. In the case of inclined tube bundles, as in the A-shape or V shape, the condensate collects in the lower region of the tube due to gravitational force. This results in the flooding of the individual tubes occurring much more rarely, so that even a tube bundle which is operated in dephlegmator mode can be operated at higher steam velocities. By direct comparison, the condensation performance is higher in inclined tube bundles which are operated in dephlegmator mode. Since tube bundles which are operated in condenser mode and in dephlegmator mode are generally combined together, the limiting factor is the tube bundle which is operated in dephlegmator mode.

The object of the invention is to disclose a condensation

plant which permits a high condensation performance and

at the same time is able to be erected cost-effectively.

This object is achieved by a condensation plant having

the features of claim 1.

The subclaims relate to advantageous developments of the

invention.

The condensation plant according to the invention has

upwardly directed tube bundles for condensing steam.

"Upwardly directed" means that the tubes of the tube bundle run from bottom to top. The steam flows from top to bottom. To this end, the condensation plant has an air chamber which widens upwardly. The term "upwardly" is to be understood to mean counter to the force of gravity. A

"vertical" within the meaning of the invention

accordingly runs from top to bottom according to the

force of gravity. The "width" is measured perpendicularly

to the vertical, i.e. in the horizontal direction.

The air chamber has a trapezoidal cross section with a

wider upper side and a narrower lower side and with two

longitudinal sides which are inclined with respect to the

vertical, wherein the longitudinal sides are formed by

the tube bundles. The end sides close the air chamber.

The end sides are impermeable to cooling air.

The cooling air is suctioned through the tube bundles so

that cooling air flows around the outside of the tubes

of the tube bundles. The upper side of the air chamber

has an outlet opening. A fan is situated in the outlet

opening, which fan is designed to suck colder cooling

air, coming from the outside, between the tubes of the

tube bundles, which are in particular ribbed on the

outside, into the air chamber and to convey the air out

of the outlet opening as heated cooling air.

The upwardly directed tube bundles have heat exchanger

tubes which are connected with their upper ends, on the

one hand, to steam distributor lines and are connected

with their lower ends, on the other hand, to condensate

collector lines, wherein one of the steam distributor

lines and one of the condensate collector lines is

arranged on each of the two longitudinal sides. According to the invention, it is provided that the upwardly directed tube bundles are each at an angle ranging from

120 to 180 with respect to a vertical. The steam

distributor lines at the upper ends of the tubes run at

a first horizontal spacing from one another and the

condensate collector lines run at a smaller second

horizontal spacing from one another. The steam

distributor lines run horizontally and the condensate

collector lines run horizontally, wherein a slight

gradient for the condensate outflow is still to be

understood as a horizontal path. This is not a V-shaped

arrangement in which typically an angle of 60° to the

horizontal or 30° to the vertical is used for each tube

bundle. Rather, in the region of their lower ends, i.e.

at the level of the condensate collector lines, the tube

bundles are spaced apart horizontally so that the air

chamber does not describe a triangular or V-shape in

cross section but a trapezium shape which tapers

downwardly. The spacing between the tube bundles in the

lower level of the air chamber is at least a third of the

spacing in the upper region of the tube bundles. The

spacings refer in each case to the center of the tube

plate of the tube bundles. All of the tube bundles have

the same upper spacing and the same lower spacing.

The upwardly directed tube bundles are preferably at an

angle of 15° to the vertical or at an angle of 750 to a

horizontal plane. According to the invention, the fans

are arranged horizontally so that the specified angles

can also refer to a horizontal upper side of the air

chamber.

The air chamber with the trapezoidal cross section

permits a relatively low-level design. The lower spacing

between the tube bundles is selected to be sufficiently

great that the footprint is of a sufficient width that

the condensation plant can stand securely, and namely

with a supporting structure which has to extend only from

the floor to the lower side. The installation area for

the condensation plant according to the invention is

significantly smaller than in plants with vertical

bundles in which the smallest spacing between the

vertical bundles and thus the width of the footprints is

defined by the diameter of the fan which is located

between two vertical bundles.

The erection of the condensation plant is also simpler.

Base plates or foundations can be arranged in a more

space-saving manner. Struts and supports are shorter.

Material and transport weight are saved. The handling of

the components is simpler.

The condensation plant according to the invention uses

an angle of preferably 150 to the vertical or 750 to the

horizontal for the tube bundles on both sides, since this

angle achieves relatively small pressure losses of the

cooling air flowing through, as in a vertical

installation of the tube bundles, but is not associated

with the drawbacks of being readily flooded when operated

in dephlegmator mode. The oblique position in an angular

range of ca. 15°+/-3°, in particular 15°+/-1°, improves

the outflow of condensate even in tube bundles which are

operated in dephlegmator mode and thus permits greater

flow rates of condensate and steam. Such a condensation

plant is thus very efficient and requires less use of material. With this approach, it is assumed by comparison that the effort required for a fan platform and for the fan is relatively great, as in a vertical arrangement of the bundles. The slight extra effort for a closed lower side is negligible in comparison with the advantage which can be achieved by a smaller installation area. A drive for the fans can also be arranged above or below the lower side which facilitates access for maintenance purposes.

The condensation plant according to the invention is

provided, in particular, for the condensation of steam,

in particular the condensation of water vapor, wherein

it is possible to use fans having diameters of preferably

24 to 32 feet. Accordingly, the upper spacing between the

tube bundles in the region of the steam distributor lines

is preferably ca. 9000 to 12000 mm.

A further advantage of the invention is that the air

chamber can be formed in a modular design from a plurality

of air chamber modules. Each air chamber module is

provided with a fan. The individual air chamber modules

are connected together on their end sides. The horizontal

steam distributor lines and the horizontal condensate

collector lines of the air chamber modules are also

connected together so that a row of individual air

chamber modules which are located in series in a linear

manner forms an extended and extendable air chamber. The

adjacent end sides of the individual air chamber modules

are generally closed and separated by a trapezoidal

partition wall. If all of the fans are always operated

at the same rotational speed, the partition walls can be

dispensed with. If a fan were to be faulty, however, the outlet opening of the faulty fan would have to be closed in an air-tight manner, so that no air would be suctioned by the further fans through the outlet opening into the corresponding air chamber module or into the air chamber bypassing the tube bundles.

Each of the fans is located in a fan ring which forms and

defines the outlet openings in the upper side. The fan

ring is preferably arranged between the steam distributor

lines so that, on the one hand, the overall height of the

condensation plant remains low and, on the other hand, a

maximum large outlet opening is provided for the cooling

air. The lower the overall height, the smaller the

construction machines, in particular cranes, which are

required in order to erect such condensation plants.

The spacing between the steam distributor lines is

largely determined by the diameter of the fan ring. At

the same time, the fan ring also determines the length

of an air chamber module. Thus each air chamber module

is substantially square at the level of the steam

distributor lines. Due to the oblique position of the

tube bundles, the cross section in the region of the

condensate collector lines arranged therebelow is

rectangular.

The condensation plant can be arranged on a framework.

This is particularly advantageous when the condensation

plant is installed at ground level, i.e. not on a

building. The installation on the framework thus permits

the geodetic emptying of the condensate collector into a

condensate collection tank which can be arranged below

the framework. A required inflow height is also achieved to at least one condensate pump which is arranged below the condensate collection tank.

If the condensation plant, however, is installed at a

higher level, for example mounted on a flat roof of a

machine house, optionally the framework can be completely

dispensed with.

If the condensation plant is arranged on a framework, the

space defined by the framework and/or the framework

itself are preferably located entirely below the lower

side of the air chamber. The term "below" is to be

understood to mean that the surface of the lower side is

projected onto the floor on which the condensation plant

is mounted. The footprint thus defined has a width which,

as a result, is smaller than the spacing between the

steam distributor lines. The width of the footprint of

the condensation plant can correspond substantially to

the width at the level of the condensate collector lines.

The condensate collector lines adjoin the lower side of

the air chamber at the side and protrude on both sides

slightly over the lower side of the air chamber.

In such condensation plants, preferably tube bundles

having a length ranging from 7000 mm to 11000 mm are

used, wherein the length is measured from an upper tube

end to a lower tube end.

The object of being able to erect condensation plants on

smaller installation areas, or to create plants with

smaller footprints, is substantially achieved by the

condensation plant according to the invention. The

reduction of the installation area can be up to 50%. At the same time, the extent of the steel structure required for installing a condensation plant, in comparison with

A-shaped or V-shaped tube bundle arrangements, is reduced

by approximately 30% by weight. The oblique position of

the tube bundles by ca. 150 limits the risk of flooding

in tube bundles which are operated in dephlegmator mode.

With such a condensation plant, more steam can be

condensed with the same energy consumption for the fans

and with at the same time a reduced overall height than

in a standard A-shape or V-shape which require a larger

installation area. The condensation plant according to

the invention thus achieves the object according to the

invention of reducing costs and improving the

condensation performance in a particularly advantageous

manner.

The invention is described in more detail hereinafter

with reference to exemplary embodiments which are shown

in the purely schematic drawings, in which:

figure 1 shows a condensation plant connected to a

turbine;

figure 2 shows a condensation plant in a side view;

figure 3 shows a condensation plant in a plan view;

figure 4 shows further embodiments of condensation

plants in a side view and

figure 5 shows a perspective view of a condensation

plant.

Figure 1 shows a condensation plant 1 for condensing

steam 2 which is supplied to the condensation plant 1 as

exhaust steam from a power plant arrangement. The steam

2 is condensed in the condensation plant 1. The

condensate 3 is collected in a condensate collection tank

33 and supplied therefrom to an evaporator 4 in a closed

circuit by means of condensate pumps 34. The hot steam 5

from the evaporator flows into a turbine 6 which drives

a generator 7. The steam 2 from the turbine is supplied

in turn to the condensation plant 1. This circuit is

merely one example of a possible application for using

such a condensation plant 1.

The condensation plant 1 of figure 1 is shown in a highly

simplified manner in vertical cross section. The steam 2

flows in the steam distributor lines 8, 9 which are

arranged at the top and which are connected to the upper

tube plates of rectangular tube bundles 10, 11. The steam

2 flows through the tubes of the tube bundles 10, 11 from

top to bottom in the direction of the condensate

collector lines 12, 13 which are arranged at a lower

level and which are connected to lower tube plates of the

tube bundles 10, 11, wherein the condensate 3 is

collected in the condensate collector lines 12, 13 and

supplied back to the power plant arrangement.

The tube bundles 10, 11 are inclined by 150 relative to

a vertical V-shape. The vertical in this case is the

central longitudinal plane of the trapezoidal

condensation plant 1. The tube bundles 10, 11 define

between one another an air chamber 14 which tapers

downwardly on both sides and relative to the central

longitudinal plane. The condensate collector lines 12,

13 are spaced apart in the horizontal direction. The

condensate collector lines run horizontally, as do the

steam distributor lines 8, 9. The air chamber 14 is closed

by a lower side 15 between the condensate collector lines

12, 13. Cooling air 16 can pass into the air chamber 14

only in the direction of the illustrated arrows and is

conveyed out of the air chamber 14 on an upper side 17

by a fan 18 (fig. 3) which is arranged in a fan ring 19.

Heated cooling air flows upwardly in the direction of the

upwardly facing arrow.

An essential element of the condensation plant according

to the invention is the trapezoidal air chamber 14 which

tapers downwardly with its side walls 27, which are

arranged mirror-symmetrically to the central

longitudinal plane in the center of the condensation

plant. The trapezoidal shape is defined downwardly by the

lower side 15 and upwardly by the upper side 17 running

parallel to the lower side 15. Figure 2 shows such a

condensation plant 1 in side view and partially in

section. In addition to figure 1, a motor 20 and a gear

mechanism 21 can be identified in the region of the lower

side 15. A shaft 22 leads vertically upwardly from the

gear mechanism 21 and drives the fan 18. As a result, the

maintenance of the fan 18 is simpler than with a drive

which is arranged above the heat exchanger bundles. The

term "fan" relates primarily to an axial fan

characterized by a hub and and fan blades which are

fastened thereto and which convey the air flow. In this

structural design, the fan drive consisting of the motor

20 and the gear mechanism 21 is located inside the air

chamber 14.

The upwardly directed tube bundles 10, 11 are located

with their lower ends on the condensate collector lines

12, 13. The condensate collector lines 12, 13 have feet

35, which are located on the main longitudinal members

36 of a framework 23. The gap between a lower edge 37 of

the condensate collector lines 12, 13 and the main

longitudinal members 36 is sealed in an air-tight manner

by closing plates 38. The two main longitudinal members

36 are connected together via cross members. The entire

plane between the main longitudinal members 36 is closed

in an air-tight manner via a bottom plate. The gear

mechanism 21 and the motor 20 are arranged above this

plane. So that the gear mechanism 21 and the motor 20 are

supplied with cold air for cooling, it is provided to

arrange a hood above the motor 20 and the gear mechanism

21 and to remove the bottom plate below the motor 20 and

the gear mechanism 21. Thus cold ambient air can cool the

motor 20 and the gear mechanism and can then be suctioned

into the air chamber 14 via openings in the hood.

Figures 1 and 2 show a framework 23 which is located

below the lower side 15 of the condensation plant 1. In

the side view of figure 2, three supports 24, 25, 26 can

be identified. The central support 25 is arranged in the

longitudinal region of the vertical V-shape. The load

path from the fan to the central support is particularly

short. Further supports 24, 26 are arranged on the ends.

Three supports which can be stabilized by additional

struts are located on each longitudinal side 27 (figure

5).

In the plan view of figure 3, it can be identified that

the condensation plant 1 has a substantially rectangular cross section due to the dimension of the fan ring 19 at the upper end of the tube bundles 10, 11. The view of the upper side, which is also closed, i.e. impermeable to air, has been dispensed with. Figure 3 also shows a spacing Al as the horizontal spacing between the upper ends of the tube bundles 10, 11 and a second spacing A2 between the lower ends of the tube bundles 10, 11 at the level of the associated condensate collector lines 12,

13. The spacings Al, A2 are measured between the

respective upper or lower tube plates of the tube bundles

10, 11. The spacings Al, A2 are identical between all of

the tube bundles 10, 11.

The second spacing A2 is at least a third of the first

spacing Al so that lower ends of the tube bundles 10, 11

and the condensate collector lines 12, 13 are always

arranged at a relatively large spacing from one another

due to the small oblique position of the tube bundles in

an angular range of 15°+/-1°. If the angle were

approximately double the size, the condensate collector

lines might be located directly adjacent to one another,

as in a V-shaped arrangement, but then the supports would

have to be provided as far as the steam distributor lines

so that the condensation plant would be sufficiently

supported on the longitudinal sides. This is not

necessary here. Self-supporting tube bundles are used.

Figure 2 shows a condensation plant 1 with all of the

features required for operation. In order to provide

larger condensation plants, the structural design of

figure 2 can serve as an individual module which is

extended by further structurally identical air chamber

modules. Figure 4 shows a plurality of such air chamber modules which are connected in series in a linear design and which form a common condensation plant 1. To this end, the steam distributor lines 9 and condensate collector lines 13 of the air chamber modules 28 have been connected together. Structural designs with two, three, four or more individual air chamber modules 28 are possible. A plurality of rows directly adjacent to one another, such as in A-shaped or V-shaped air condensers, are not provided since the intake space for the cooling air between the steeper tube bundles 10, 11 is significantly smaller. Thus the condensation plant according to the invention is suitable, in particular, for applications in which a lower condensation performance is sufficient.

The perspective view of figure 5 shows a further

condensation plant 1. The framework 23 has additional

diagonally running struts 29 which are placed in the

lower region on the supports 24, 25, 26 and run obliquely

upwardly to the lower side of the air chamber. The air

chamber located in the interior can be entered via a

maintenance access point 31 which is the size of a room

door into an end side 30 which is also closed.

In the perspective view, the second air chamber module

28 of a total of four structurally identical air chamber

modules 28 has one or more tube bundles 11 which are

operated in dephlegmator mode. While the steam flows from

top to bottom in the direction of the condensate

collector lines 12, 13 via the steam distributor lines

8, 9 which are arranged at the top in the remaining air

chamber modules 28, it is provided that uncondensed steam

flows from below via the condensate collector lines 12,

13 into the tube bundle 11 of the second air chamber

module 28 and is condensed as completely as possible

therein. Any residual gases and uncondensed vapors are

suctioned off in a suction unit 32. In this structural

design, therefore, three air chamber modules 28 which

operate in condenser mode are used and combined with an

air chamber module 28 which is operated in dephlegmator

mode.

A preferred alternative to the structural design of

figure 5 provides that every 2 to 4 or more air chamber

modules in a row has an identical number of tube bundles

which are operated in dephlegmator mode at the same

location. Each air chamber module preferably has a

proportion of approximately 16% to approximately 20% of

tubes or tube bundles which are operated in dephlegmator

mode. This has the advantage that the diameter of the

condensate collector lines via which the steam flows into

these tubes or this tube bundle can be kept small.

Regarding the dimensioning of the condensation plant 1,

on the one hand, reference should be made to the tube

bundles 10, 11 which are inclined relative to the

vertical V by the angle Wi. The angle Wi is 150. The

condensation plant 1 has a length L2 which is measured

in the longitudinal direction of the steam distributor

lines 9, 10 running horizontally in the region of the

upper tube plates and which is a multiple of the length

Li of an individual air chamber module (figure 2). The

footprint G, which is occupied by the framework 23, has

a width Bl. The width Bi of the footprint G corresponds

to the width B2 of the condensation plant 1 at the level

of the condensate collector lines 12, 13 arranged therebelow and running horizontally in the region of the lower tube plates. The spacing Al at the level of the steam distributor lines 8, 9 is approximately double the size.

Reference signs:

1 - Condensation plant

2 - Steam

3 - Condensate 4 - Evaporator

5 - Hot steam

6 - Turbine

7 - Generator 8 - Steam distributor line

9 - Steam distributor line

10 - Tube bundle

11 - Tube bundle

12 - Condensate collector line

13 - Condensate collector line

14 - Air chamber

15 - Lower side of 14

16 - Cooling air

17 - Upper side of 14

18 - Fan

19 - Fan ring

20 - Motor

21 - Gear mechanism

22 - Shaft

23 - Framework

24 - Support

25 - Support

26 - Support

27 - Longitudinal side of 14

28 - Air chamber module

29 - Strut

30 - End side of 14

31 - Maintenance access in 30

32 - Suction at 11

33 - Condensate collection tank

34 - Condensate pump

35 - Foot

36 - Main longitudinal member

37 - Lower edge of 12, 13

38 - Closing plate

Al - Spacing between the upper ends of the tube bundles

at the steam distributor lines

A2 - Spacing between the lower ends of the tube bundles

at the condensate collector lines

Bi - Width of footprint G of 1

B2 - Width of 1 at the level of the condensate

collector lines

G - Footprint

Li - Length of 28

L2 - Length of 1

V - Vertical

Wi - Angle

Claims (1)

1. Claims

   1. A condensation plant (1) with upwardly directed tube

   bundles (10, 11) for condensing steam (2), with the

   following features:

   a) an air chamber (14) has an upwardly widening

   trapezoidal cross section with an upper side (17),

   a lower side (15) and with two longitudinal sides

   (27) which are inclined in opposite directions with

   respect to a vertical (V) and are formed by the tube

   bundles (10, 11), and end sides (30) which are

   impermeable to cooling air (16);

   b) the upper side (17) has at least one outlet opening

   for heated cooling air (16), wherein a fan (18) is

   situated in the outlet opening, which fan is

   configured to suck colder cooling air (16), coming

   from the outside, through the tube bundles (10, 11)

   into the air chamber (14);

   c) the tube bundles (10, 11) have heat exchanger tubes

   which are connected with their ends to steam

   distributor lines (8, 9) and to condensate collector

   lines (12, 13), wherein one of the steam distributor

   lines (8, 9) and one of the condensate collector

   lines (12, 13) is arranged on each of the two

   longitudinal sides (27);

   d) the tube bundles (10, 11) are each at an angle (W1)

   ranging from 12° to 18° with respect to a vertical

   (V) , wherein the tube bundles (10, 11) run at a

   first spacing (Al) from one another at the steam distributor lines (8, 9) and run at a second spacing

   (A2) from one another at the condensate collector

   lines (12, 13), wherein the second spacing (A2) is

   at least 1/3 of the first spacing (Al).

   2. The condensation plant (1) as claimed in claim 1,

   characterized in that the tube bundles (10, 11) are

   arranged at an angle of 15°+/-1° to the vertical

   (V).

   3. The condensation plant (1) as claimed in claim 1 or

   2, characterized in that the first spacing (Al)

   ranges from 9000 mm to 12000 mm.

   4. The condensation plant (1) as claimed in one of

   claims 1 to 3, characterized in that the air chamber

   (14) is formed in a modular design from a plurality

   of air chamber modules (28), wherein each air

   chamber module (28) has a fan (18) and wherein the

   air chamber modules (28) are connected together on

   their end sides (30), so that the steam distributor

   lines (8, 9) and the condensate collector lines (12,

   13) of the air chamber modules (28) are connected

   together.

   5. The condensation plant (1) as claimed in one of

   claims 1 to 4, characterized in that each fan (18)

   is arranged in a fan ring (19) and the fan ring (19)

   is arranged between the steam distributor lines (8,

   9).

   6. The condensation plant (1) as claimed in claim 5,

   characterized in that a diameter of the fan ring

   (19) determines the first spacing (Al) between the

   steam distributor lines (8, 9) and also the length

   (Li) of an air chamber module (14), wherein each air

   chamber module (14) has a substantially square cross

   section at the level of the steam distributor lines

   (8, 9).

   7. The condensation plant (1) as claimed in one of

   claims 1 to 6, characterized in that in the raised

   position the air chamber (14) is arranged on a

   framework (23) which is located below the lower side

   (15) of the air chamber (14) and defines a width

   (B1) of a footprint (G) of the condensation plant

   (1) which is smaller than the spacing (Al) between

   the tube bundles (10, 11) at the steam distributor

   lines (8, 9).

   8. The condensation plant (1) as claimed in claim 7,

   characterized in that the width (B1) of the

   footprint (G) corresponds to the width (B2) of the

   condensation plant (1) at the level of the

   condensate collector lines (12, 13).

   9. The condensation plant (1) as claimed in one of

   claims 1 to 8, characterized in that the tube

   bundles (10, 11) have a length ranging from 7000 to

   11000 mm.

   4 V 17 8 9 27 27 16 10 14 11

   12 13 6 7 15 3 33

   34

   1 V Fig. 1 19 17

   9 28

   11

   27

   13

   22 35 37 38 36 21 23 20 15

   26 24 25 Fig. 2 L1

   A1 A2

   13

   10 9 27 1

   Fig. 3

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   28 28

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   1

   Fig. 4

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   28 29

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