HU220430B - Air-cooled condenser - Google Patents

Abstract

The condenser has a vapour distribution chamber (23) and a condensate collecting chamber(24) with condensate and air extraction (6,8) connections. The chambers (23,24) are connected by multiple finned tubes (17) arranged in parallel with the fins on the air side. Each tube (17) has two parallel flat side walls with exterior closings connecting the side walls. Longitudinal separation walls (18) connected to the side walls divide the interior of each tube (17) into long parallel flow channels (19). The walls (18) have breakthrough perforations (27) allowing the flow of the condensing medium between neighbouring channels (19).

Description

Scope of the description is 14 pages (including 7 pages)

EN 220 430 B1

Technical area

The present invention relates to the condensation of an air cooled condenser vapor medium, preferably water vapor.

The former technique

Capacitors are widely used in the processing, chemical and energy industries. A special type of capacitors is an air-cooled condenser, which usually operates under vacuum. In particular, physical processes in air-cooled condensers are described in order to understand the operation of the air-cooled condenser 10 according to the invention.

The physical processes as well as the prior art are described for power steam condensers, water vapor condensation, but the invention is not limited to capacitors of this type, but can be used in other cases and other vapor-containing media where air-cooled capacitors are required.

Air-cooled condensers generally consist of a large number of parallel 20 ducted ducted pipes. The processes in the parallel tubes are essentially the same, so it is sufficient to describe the processes in a single tube.

Fig. 1 is a schematic cross-sectional drawing of a known air-cooled condenser, the capacitor having a distribution chamber 14, a condensate collection chamber 16 at a lower height, and condenser pipes 1 connected in parallel with each other, of which only one is illustrated.

The cross-sectional shape of the condenser tubes 1 may be different, in practice circular, elliptical, or flat (with a cross-sectional condenser tube having a cross-section. The condenser tube 1 flows in the direction of the condensing water vapor in the direction of the 2 arrows, and the condenser tube on its axis). the cooling air flows in a direction perpendicular to 3 arrows.

Since the condensation water condenser condenser 1 has a high heat transfer coefficient, it can reach

23260 W / m ² K, and the air-side heat transfer coefficient is low, 58-81 W / m ² K, in order to increase the efficiency of the heat exchange, it is advisable to increase the air surface, which in practice has 4 ribs.

In the condenser tube 1, not only pure water vapor enters the direction of the arrow 2, but also very small amounts of non-condensable gases, especially air. Some of the non-condensable gases, such as volatile alkalizers and dissociation products, are brought by water vapor, but most of it is released into the water vapor due to leaks in the technological system. For a properly constructed and maintained steam turbine, the amount of non-condensable gas entering the condenser, especially air, entering the condenser, is 0.005-0.01% by weight.

Although this amount is very small in relation to water vapor, it will become apparent later that the presence of non-condensing gases will significantly affect the operation of the condenser.

Water vapor condensate and non-condensable gases must be removed continuously. 6 condensate and 10 condensate pumps are used to drain the condensate 5 collected in the condensate collecting tank 16, and a mixture of non-condensable gases and some residual vapor 7 passes through a suction line 9 to a vacuum pump 9.

During the condensation, the major physical characteristics such as the partial pressure of the air, the evaporation of steam and the heat transfer coefficient of the steam side are negligible until 97-99% of the steam is condensed. Only the volume and flow rate of the vapor-air mixture 7 are exceptions, which are inversely proportional to the amount of condensed steam. For example, if 97% of the steam is condensed, the flowing volume and the flow rate are only 3% of the values at the entry point.

However, the remaining 3%, but especially the condensation of the last 0.5% of steam, due to the presence of non-condensable gases, shows very significant changes in the individual parameters as shown in the following table.

Remaining steam 3% 0.6% 0.06% 0.01 Partial pressure of air / non-condensing gases 24 Pa 120 Pa 1200 Pa 5000 Pa Kondenzátortér-aláhűlés 0.04 ° C 0.2 ° C 2 ° C 10 ° C Reduction of the heat transfer coefficient of the vapor 10% 43% 82% 82% Volume of flowing vapor-air mixture 3% 0.625% 0.065% 0.015%

It can be seen that at the condensation of the remaining 3% steam, the partial pressure of the air increases significantly, as a result of which the condensation temperature decreases, in other words, the condensation of the condenser space increases. Due to the increase in air concentration at the end of the condensation, the heat transfer coefficient of the vapor is significantly reduced. The volume of flowing vapor-air falls to a fraction of the value at entry.

Because of the changes listed above, it is common practice to divide the capacitor into a main capacitor 11 and a post-cooler 15, as shown in Figure 2, where 80-90% of the steam in the main condenser 11 is condensed, and in the after-cooler 15 a portion of the residual steam is condensed. condensed or under the mixture. The main capacitor 11 and the aftercooler 15 are connected to a condensate collecting chamber, which, on the one hand, passes through all the mains2

HU 220 430 Β1 condensate outlet 15, and collects condensate 5 through conduit 6 to condensate pump 10.

The design of the main capacitor A corresponds to the condenser tube 1 of Fig. 1, i.e., the steam and the condensate 5 flow down in one direction, while in the aftercooler 15 the mixture is flowing upwards and the condensate 5 downwards against the mixture 7. This is necessary because, as shown above, at the end of the condensation process, the undercompression of the mixture 7 increases rapidly, and at ambient temperatures below freezing, the undercooling may also be such that the temperature of the condensation space may drop below the freezing point and consequently 5 condensates may freeze. The frozen condensate 5 may block the air extraction path that may cause the condenser tube to fall out of the condensation process, and in the worst case, the frozen condensate 5 may crack the tube.

The arrangement shown in Figure 1 also has the disadvantage that the temperature of the condensate 5 is lower than the theoretical condensation temperature due to the underexposure of the vapor space, and this condensate enters the steam turbine into the circuit, deteriorating the thermal efficiency of the system. Another undesirable effect is that, due to the increased partial pressure of the air and the condensation of the condensate 5, the condensate 5 absorbs a greater amount of oxygen than is allowed, which can cause corrosion and necessitate degassing prior to recirculation.

The countercurrent cooler 15 intends to reduce or eliminate these drawbacks by heating the vapor in the opposite direction to condensate.

The processes described hereinbefore occur when the vapor-air mixture 7 is flowing all the way to the exhaust pipe 8 of the after-cooler 15 in both the main condenser and the after-cooler 15. In the main condenser, this condition is essentially fulfilled. If the capacitor is dimensioned so that the vapor velocity is 50-80 m / s at entry, assuming 95% condensation, the steam velocity at exit will be 2.5-4 m / s, which is enough to allow steam to escape. air 7 blends clearly into the exit point.

However, this is not the case in the after-cooler 15. Assuming that 10% of the condenser tubes are installed in the condenser to condense the remaining 5% steam in the aftercooler 15, i.e. the flow cross-section decreases to 1/10, the speed will be 25-40 m / s when entering the after-cooler 15 in the case of the exhaust pipe 8, however, it is only 0.16-0.25 m / s. In order not to leave too much vapor with the exhaust air and not to use a vacuum pump that is too high, the after-cooler 15 is generally sized so that the volume of the vapor-air mixture 7 at the inlet pipe 8 is only 0.03. -0.04%, and the air content of the extracted mixture 7 is 25-30%, which occurs when the vapor-air mixture 7 is undercut by 4 ... 5 ° C.

It can be seen that the correct design and dimensioning of the after-cooler 15 is an extremely difficult task. For example, if a low air vapor enters the after-cooler 15 at high speed, the disordered swirling flow leads to the exhaust pipe 8 and dilutes the extractable 7 mixture. At this point, the vacuum pump designed to carry the constant volume cannot remove all the air coming into the condenser, so it first accumulates in the aftercooler 15 and later in the main condenser. The increase in air concentration rapidly increases the underflow of the steam room and degrades the heat transfer coefficient, which results in a decrease in the condenser heat output and may cause frost in cold weather. Since only very small amounts of flue pipe 8 are flowing, small amounts of fresh steam can cause the above harmful effects.

Accordingly, a drastic speed reduction between the entry and extraction points should not be allowed for a properly designed after-cooler.

The properly designed condenser and aftercooler must meet another requirement, namely that there must be a line of ribbed pipes in the cooling air flow direction.

This is important because, in the case of more rainstorms, the rainfall on the cooling air inlet side gets much more powerful than other rainstorms, so that the steam flows at both ends of the steam. The upper pipe end is the normal entry point for steam, and the lower end of the pipe flows from the rest of the rainfall through the common condensate collection chamber.

This phenomenon leads to the fact that non-condensing gases cannot escape from the first and, if appropriate, subsequent tubing (s), and stagnant air plugs are formed. The length of these air plugs decreases gradually from the first rainy rain to the next rainstorms that come in contact with the warmer air. In the air-filled zone, the heat dissipation decreases and freezes may occur in cold weather. To eliminate these adverse effects, single-core air-cooled condensers are used. In order to provide sufficient vapor cross-section, a sufficient number of air-side ribs may be provided, and the air-side flow resistance shall be kept to a minimum, in practice flat ribbed tubular cross-sectional tubes.

Description of the Invention

It is an object of the present invention to provide an air cooled condenser having

- low air and vapor flow resistance, (use of flat, high cross-sectional, internal or external pressures);

- ribbed on the air side;

- air side ribs can be optimally adapted to heat transfer and air flow;

- have ribbed tubes that do not produce air plugs, so that air can be safely removed in all operating states;

- the freezing of the pipes can be avoided;

- simple and economical.

The invention therefore relates to an air-cooled condenser having a condensate vapor dispenser.

HU 220 430 has a Β1 splitting chamber, a condensate collecting chamber, and ribbed tubing with parallel ribs connected to the distribution chamber and condensate collecting chamber. The condenser according to the invention has two ribbed tubes formed from two parallel, substantially flat side walls and the end closures connecting the side walls, longitudinal partitions connected to the side walls dividing the inner space of the ribbed tubes in the longitudinal direction, and the fluid flow between adjacent channels in the partitions. breakthroughs are provided.

In a preferred embodiment of the invention, at least a portion of the ribbed tubing with the closures formed in the channels and through the breakthroughs in the partitions adjacent the closure elements is divided into the main condenser leading from the distribution chamber to the condensate collecting chamber and from the condensate collection chamber to the exhaust pipe leading to the distribution chamber.

This embodiment allows each condenser tube of the condenser to be of the same type, i.e. it is not necessary to design and manufacture a separate capacitor and aftercooler as well as a connecting tube. Thanks to this embodiment, air coolers are not formed as a result of temperature changes in the cooling air or the unevenness of steam distribution. The after-cooler has a metallic connection with the main condenser, from which it is always sufficient to transfer heat to the high-air sections around the exhaust pipe so that they do not freeze.

The closures formed in the channels are preferably arranged at an increasing distance from the distribution chamber inwardly from one of the outermost channels, the breakthroughs adjacent to the closures are arranged in the adjacent channel of the fluid, and the exhaust pipe is located between the closure of the outer conduit and the condensate collection chamber near the closure. is connected.

The closures and the breakthroughs adjacent thereto are preferably arranged in the channels to prevent the formation of air plugs. Advantageously, about half of the channels are provided with closure elements extending inwardly from the outer channel. In this way, a continuous constriction of the medium is available.

The closures and the breakthroughs adjacent thereto are preferably provided to allow the gravitational passage of the condensed medium into the adjacent channel.

The condenser according to the invention preferably includes further breakthroughs in the bulkheads between the main condenser channels and / or in the partition walls between the after-cooler channels.

In another preferred embodiment of the capacitor, each partition includes a plurality of breakthroughs, which breakthroughs are preferably provided at equal distances in the partition. In this way, the formation of air plugs in the channels with higher cooling can be prevented, as the medium can flow through the breakthroughs into the channels in which the condensation space pressure decreases due to faster condensation of the medium.

A brief description of the drawings

Preferred embodiments of the invention will now be described with reference to the drawings, in which it is

Figure 1 is a schematic cross-sectional view of a known air-cooled condenser, a

Figure 2 is a schematic cross-sectional drawing of a known air-cooled condenser consisting of a main condenser and a post-cooler;

Figures 3 and 4 are a cross-sectional and longitudinal cross-sectional view of a flat inner partition wall with a partition wall according to the invention;

5-7. Figures 1 to 6 are cross-sectional drawings of various embodiments of flat ribbed tubes with internal partitions;

8-10. Figures 4a and 6b are cross-sectional views of various embodiments of the air side ribs;

Figure 11 is a longitudinal cross-sectional view of a preferred embodiment of a condenser tube according to the invention, provided with condenser tube internal partitions, internal channels, and breakthroughs in the partitions;

Figure 12. FIG. 1 is a cross-sectional view of the preferred embodiment of FIG

13 and 14 are cross-sectional drawings of two preferred embodiments of breakthroughs in the partitions, a

Figure 15 is a longitudinal cross-sectional view of a condenser tube according to another preferred embodiment of the present invention divided into a condenser pipe main capacitor and a post-cooler;

Figure 16 is a longitudinal cross-sectional view of a condenser tube according to a further preferred embodiment of the invention, a

Fig. 17 is a schematic diagram of an air-cooled condenser according to the invention, in which the post-cooler and post-cooler ribbed tubes are alternately arranged, and

Figure 18 is a schematic diagram of another preferred embodiment of an air cooled condenser.

Embodiments of the Invention Figures 3 and 4 show cross-sectional and longitudinal views of a ribbed tube 17 according to the invention, which is flat and consists of a pair of substantially flat side walls and curved edge closures, i.e. horse racing. Inside the ribbed tube 17 are partition walls 18 which separate internal longitudinal channels 19 from each other. Air ribs 4 are disposed on the outer flat sides of the ribbed tube 17. The ribs 4 are provided with slots perpendicular to the air flow direction, so that no thick boundary layer can be formed around the heat transfer tube 17 around the ribbed tube 17.

5-7. 1 to 3 show some embodiments of the tubular portion of the ribbed tube 17. In the embodiment of Fig. 5, the tubular part consists of two halves and the partitions 18 are separate pieces. Separate pieces by welding, soldering or gluing or mechanical ter4

HU 220 430 Β1 can be connected to an anchor for fastening,

In the embodiment of Figure 6, the two-part pipe section and the partition walls 18 can be joined together, and the two halves can be joined together by welding or soldering.

Fig. 7 shows an extrusion tube section, where the tube part and the partitions 18 are one piece, whereby the tube portion can be produced by a single operation.

8-10. 1 to 3 show some embodiments of the ribs 4 of the ribbed tubes 17. In Figure 8, the crowns 4 of the ribs 4 are punctured and sealed, bonded, or bonded, tightly attached to the ribbed tube 17.

In Fig. 9, the ribs 4 may be formed by cutting out the material of the tube such that the knives 21 move in the direction of the arrows 22 and, after forming a pair of 4 ribs, move to the left with a rib division and then form a pair of four ribs.

Figure 10 shows a rib 4 made of corrugated sheet, which is for example sealed to the tube.

In addition to the additional role described below, the inner partitions 18 have the advantage that the large surface planar walls of the ribbed tube 17 are supported against both external and internal pressures, so there is no need for the ribs to contribute to the load-bearing capacity of the pipe walls. Therefore, in the way of forming the ribs 4 and attaching to the sidewall, there is no tightness in the strength of the ribbed tubes 17, but they can be made with an optimum shape for heat transfer. Such ribs 4 are generally not suitable for absorbing the pressure of the pipe wall from internal or external pressure, but are excellent in terms of heat transfer.

All. Figure 1 shows an air-cooled condenser according to the invention, comprising a distribution chamber 23, a condensate collecting chamber 24 arranged at a lower level thereon, and a ribbed tube 17, parallel to each other, connected in parallel with each other on the air side, parallel to each other. Only one ribbed tube 17 is shown in the cross-sectional drawing. Since the ribbed tubes 17 are connected in parallel, it is sufficient to describe the construction of a single ribbed tube 17.

From the distribution chamber 23, which in this embodiment is a steam distribution pipeline, a small amount of air vapor is introduced into the ribbed tube 17. The ribbed tube 17 has five partitions 18 which divide the ribbed tube 17 into six internal longitudinal channels 19. The air side ribs 4 are disposed on the outer plane wall of the ribbed tubes 17.

In channels 19, steam and condensate 5 flow down into the condensate collection chamber 24. From here, the condensate is led through conduit 6 by a condensate pump. In the partitions 18 there are 27 breakthroughs with even spaces. These connect the channels 19 of the ribbed tube 17 so that the steam can flow from any of the channels 19 to any of the channels 19. If, in this embodiment, the air flowing in the direction of the arrows 3 condenses the steam flowing through the channels 19 at the entrance side, as in the channels 19 farther from the entrance of the air, the steam can flow in the direction of the arrows 2 through the breakthroughs 27 and thus in the channels 19 on the entry side the formation of air plugs can be prevented. Figure 12 below. Fig. 17 is a cross-sectional view of the ribbed tube 17 shown in Fig. 1A on plane A-A.

The breakthroughs 27 can be formed in different ways. Figures 13 and 14 show two exemplary breakthroughs 27. Fig. 13 shows a circular or rectangular opening in the partition 18, and in Fig. 14 the breakthrough 27 is configured to cut three sides of a rectangular portion in the partition 18 and a fourth non-cut side of the rectangular portion. bent along. The bent part 18A facilitates steam dispersal, and no waste is produced when the breakthrough is formed.

Figure 15 shows another preferred embodiment of a capacitor according to the invention. In this embodiment, the ribbed tube 17 is divided into the main condenser 11 and the aftercooler 15 by means of the closure elements 26 in the channels 19. The closures 26 are disposed in the first, second and third channels. The closure members 26 are positioned so that the longest of the ends of the first channel 19 is shorter, the second is shorter, and the third is the shortest section. In order to allow the condensate 5 to escape from the channels 19 sealed by the closure 26 and to allow the steam to flow through, there are breakthroughs 28 and 28A directly on the partition walls 18 adjacent the closure elements 26 and below. Thus, for the steam flowing in the direction of the arrows 2, a gradually decreasing cross-section is provided towards the condensate collecting chamber 24 and then towards the suction line 8, which ensures that the vapor velocity of the exhaust pipe 8 is sufficient.

In the partition walls 18 between the main capacitor 11 of the ribbed tube 17 and the conduits 19 of the aftercooler 15, there are also several breakthroughs 27 for connecting the channels 19 so that no air plug can be formed on the air inlet side.

The steam-air mixture from the condensate collection chamber 24 is introduced into the after-cooler 15. The after-cooler 15 also has a narrowing cross-section. The principle of the only rainfall here is provided by the breakthroughs 27 in the after-cooler. The suction line 8 is located at the highest point of the after-cooler portion of the outermost channel 19, which passes the residual vapor-air mixture through the collecting tube to the vacuum pump. In the aftercooler 15, the vapor-air mixture is upward, the condensate 5 is downward, i.e., countercurrent.

In the case where the condenser is in a warm climate with no risk of frost, the breakthroughs 27 may be omitted. This embodiment is illustrated in Figure 16. In this embodiment, the closure elements 26 should preferably be positioned so as to reach the upper limit of the above-mentioned stagnant stoppers. In this case, breakthroughs 28 and 28A on both sides of the closure 26 are also required.

The after-cooler 15 of the condenser according to the invention can also be placed on the side opposite the air inlet,

EN 220 430 Β1 its cooling is already done by warm air. This solution avoids freezing the after-cooler 15 in cold climates. A similar advantageous embodiment can also be provided by the fact that the cooling air fan can be changed in the direction of rotation, so that the aftercooler 15 can be positioned opposite the air inlet. With this solution, a device operating under optimal conditions in both hot and cold weather is created.

A17. Fig. 1 is a schematic diagram of an air-cooled condenser 30 according to the invention, in which the ribbed tubes 31 with the after-cooler 15 and the non-refrigerated tubular tubes 15 are alternately arranged. The ribbed tubes 31 and 32 may be installed at any rate depending on the flow rate required in the aftercoolers, the heat exchanger surface of the aftercoolers, or other parameters.

In some cases, capacitors operating especially in cold climates may need to have a higher cooling effect on the section of the ribbed surface where the aftercooler is located than on the main condenser section alone. This requirement can be met by passing through a higher specific air volume than the main condenser section on the aftercooler section. This embodiment is illustrated in FIG. 18, where a fan 33 travels air to a condenser 30 connected to a common steam distribution tube 29. The air flows in the direction of 36 arrows. On the air inlet, there are independently operated louvers 34 and 35. The shutter 34 covers only the main condenser part 11 and the damper 35 comprises the part comprising the after-cooler 15. By varying the position of the shutters 34 and 35, it is possible to independently change the amount of air flowing through the main capacitor 11 and the aftercooler 15.

The advantages of the integrated main condenser / aftercooler described above are:

- All condenser pipes of the condenser can be of the same type, no separate capacitor and aftercooler and piping connecting them are to be designed and manufactured.

- The speed and pressure of the flowing vapor in the steam distribution chamber varies. As a result, the distribution of steam in the condenser pipes connected to the steam distribution chamber is uneven, which deteriorates the flow and thermal properties of the condenser and, in a critical situation, can cause frost. In the present invention, where each ribbed tube has its own after-cooler and exhaust pipe, this inequality is substantially lower than that of the capacitors of the known design.

- Due to the structural design, each ribbed tube is equipped with its own after-cooler and exhaust pipe, neither air temperature changes nor air roughness can be caused by the change of temperature of the cooling air.

- The after-cooler has a metallic connection with the main condenser, from which it is always sufficient to transfer heat to the high-air sections around the suction line so that they do not freeze.

- With the proper design of the exhaust pipe, using a small amount of throttle, it is possible for the collecting tube to remove the vapor-air mixture from each of the ribbed tubes incorporated in the condenser, thereby allowing each ribbed tube to operate with the same, good cooling.

It will be appreciated by those skilled in the art that the above embodiments are considered to be exemplary only and various variations and variations may be made within the scope of the invention as defined by the claims.

Claims (17)

PATENT CLAIMS An air-cooled condenser having a vapor medium distribution condenser, a condensate collection chamber, and a parallelepiped, parallel-walled, side-flanked, ribbed tube, having ribbed pipes (17) formed by connecting end seals, longitudinal partitions (18) dividing their inner space into longitudinally parallel channels (19) dividing their interior space into side walls, and adjacent channels (18) in the partitions (18) 19) are provided with breakthroughs (27, 28, 28A) to allow fluid flow. Capacitor according to Claim 1, characterized in that at least a portion of the ribbed tubes (17) are provided with closures (26) formed in the channels (19) and openings (28, 28A) in the partitions (18) adjacent to the closures (26). ) dividing the medium from the distribution chamber (23) to the main condenser (11) leading to the condensate collection chamber (24) and to the aftercooler (15) leading from the condensate collection chamber (24) to the exhaust pipe (8). A capacitor according to claim 2, characterized in that the closure elements (26) formed in the channels (19) are arranged in a progressively increasing distance from one of the peripheral channels (19) to the distribution chamber (23), formed adjacent the closures (26). the openings (28, 28A) being formed to divert the medium into an adjacent channel (19), and the exhaust pipe (8) for the section of the extreme channel (19) between its own closure (26) and the condensate collection chamber (24) near the closure (26) is connected. The capacitor according to claim 3, characterized in that the closures (26) and the breakthroughs (28A) formed adjacent thereto are arranged in the channels (19) to create a narrowing flow cross section without congestion zones. A capacitor according to claim 3, characterized in that upstream of the outermost channel (19) the closure (26) is formed in up to 2/3 of the channels (19). A capacitor according to claim 3, characterized in that the closures (26) and adjacent breakthroughs (28) are formed to allow gravity passage of the condensed medium into the adjacent channel (19). HU 220 430 BI 7. A capacitor according to any one of claims 1 to 5, characterized in that further openings (27) are formed in the partitions (18) between the channels (19) of the main capacitor (11). 8. A capacitor according to any one of claims 1 to 3, characterized in that further openings (27) are formed in the partitions (18) between the channels (19) of the aftercooler (15). 9. A capacitor according to any one of the preceding claims, characterized in that the aftercooler (15) is located upstream of the main condenser (11) in the direction of air flow cooling the ribbed pipes (17). 10. 2-6. A capacitor according to any one of the preceding claims, characterized in that the aftercooler (15) is located downstream of the main condenser (11) in the direction of air flow cooling the ribbed pipes (17). 11. A capacitor according to any one of the preceding claims, characterized in that it has a cooling air flow device which is capable of reversing the flow direction of the cooling air. 12. A capacitor according to any one of the preceding claims, characterized in that the cooling air flow and / or regulating device allows independent control of the amount of air flowing through the ribbed surface comprising the aftercooler (15) and the ribbed surface comprising only the main condenser (11). A capacitor according to claim 1, characterized in that each partition (18) comprises a plurality of breakthroughs (27), the breakthroughs (27) being preferably spaced apart in the partition (18). 14. A capacitor according to any one of claims 1 to 13 and 13, characterized in that the partitions (18) are arranged perpendicular to the side walls and / or integrally formed with the side walls or connected thereto by mechanical load transfer, for example by welding, soldering or gluing. 15. A capacitor according to any one of claims 1 to 13 and 13, characterized in that the openings (27, 28, 28A) are formed as openings in the partitions (18) or in the form of bending of part of the partition (18). 16. A capacitor according to any one of claims 1 to 13 and 13, characterized in that the end closures of the ribbed tubes (17) are arcuate. 17. A capacitor according to any one of claims 1 to 4, characterized in that a portion of the ribbed tubes (17) is provided with a post-cooler (15) formed by the closures (26) and the other portion is provided only through openings (27) in the partitions (18). formed.