DE1776231A1 - EVAPORATIVE HEAT EXCHANGER - Google Patents

Description

Evaporative heat exchanger

The invention relates to an evaporative heat exchanger with a vertical housing and with air circulation in counterflow to the fluid to be cooled or to be condensed, in particular water, wherein in the housing below a upper fogging device connected to a fluid supply line nozzles for injecting the fluid in uniform distribution over the entire horizontal Housing cross-section, darurter fillers or trickle plates to provide the largest possible contact area between the air flowing up and the air flowing down Fluid and / or at least one fluid containing a second fluid to be cooled or condensed Coiled pipe, and below it in turn one containing the fluid sump, that of the filling bodies or trickle plates A pan that receives fluid or coiled pipes and is connected to a fluid drain line

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are provided, furthermore at least one in the space between the sump surface in the pan on the one hand and the fillers or trickle plates or pipe coils on the other hand is present conveying fan. ., ■

In the present context, evaporative heat exchangers include cooling towers, evaporative condensers, liquid coolers, To understand gas coolers, etc., d. H. all such heat exchangers in which an air circulation, d. H. Forced fc ventilation, is given and evaporative cooling is used. .

Evaporative heat exchangers with the features listed above are known. However, these have the disadvantage that they are either relatively high or relatively expansive, d. H. a relatively large area have, essentially due to the unfavorable fan arrangement. Furthermore, is with the known Devices the relatively large sump volume disadvantageous, 'which increases the operating weight, and also the uneven Distribution of the air blown into the housing over the horizontal Cross section of the same.

In the known pressure-ventilated heat exchangers with ' Evaporative cooling, especially for those with axial fans there is a difficulty in giving direction and speed to the incoming air in the fan duct, so that they go straight from the entry point, through the whole antechamber, d. H. the space between the sump and fillers or trickle plates or pipe coils flows through it. This is associated with the risk that the fillers or trickle plates or pipe coils above and opposite too much air flows into the air inlet, which is directly On the other hand, there is not enough area above the air inlet point. Are used to increase the efficiency of the

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or the fan outlet guide vanes are provided, the achievement of a uniform flow distribution over the Filling elements or trickle plates or pipe coils due to the straightening of the flow direction that has now been brought about entering air is even more difficult. In order to remedy these disadvantages, one has so far the width of each by one The antechamber supplied by the fan is kept low, and is generally limited to approximately the size of the fan diameter. at the known devices, it has also proven difficult to protect the fan against the action of water, and both with air circulation and with an operating mode, ™ where only water is used, which can be the case under certain operating and / or weather conditions.

The object of the invention is to eliminate these disadvantages and to provide an evaporative heat exchanger of the type specified convey which, with high performance and low space requirements, the most even distribution of the upflowing air Lter allows the cross-section of the heat exchanger.

This is achieved according to the invention characterized in that above the mouth of the air outlet pipe of each blower one is located arranged after ä upwardly extending guide plate, which provided with its concave, the or the tube mouths facing over an arc of more than 90 ° extending surface and with lower edge protrudes into the air flow emerging from each mouth and runs with the upper, approximately horizontal edge above each mouth.

For a further embodiment of the invention, the guide plate with the upper, approximately horizontal edge is the mouth of each air outlet pipe of the fan (s) covered.

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According to a preferred embodiment of the invention; a second horizontal guide plate is provided, which is connected to that of the air outlet pipe (s) or the fan interspersed wall opposite housing wall an approximately conical, towards the fillers or trickle plate or Includes coiled tubing widening channel.

Finally, according to a “further feature of the invention, below the filler bodies or trickle plates bgw”, coiled tubes ^ a horizontal, extending approximately horizontally towards the ventilator airflow Guide plate provided.

Other objects and advantages of the invention will become apparent from the context of the detailed description of some of the following Embodiments in connection with the enclosed drawings emerged. In the drawings show:

Figure 1 shows a sectional side view of a single plant unit of an evaporative cooler in Ktthiturßi design, those according to the teachings and points of view . of the first and second aspects of the invention

builds is;

Figure 2 is an end view of two assembly units such as the In Pig. I.

shown in vertical section, with the . both assembly units with the backs facing each other «

are provided and a common collection container is provided

is; \

Figure 3 is a side elevation view of a multiple fan unit like the one shown in Fig. 1, the one here at the end

are juxtaposed;

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Pig. FIG. 4 is a vertical sectional view in one along FIG Line 4-4 of Fig. 3 laid section to show the air blower structure in a considerably larger Scale;

Figure 5 is a view in horizontal section taken along line 5-5 of Figure 2;

6 shows a perspective partial view of a profile section for the antechamber, the deflection angle 1st lick being shown is;

Fig. 7 is an end view, shown in section, of a Wet deck filling unit)

8 shows a perspective view of a single surface component of the type shown in Figure 7;

9 shows a perspective view of the filling support frame of a filling assembly B, with the actual surface components are omitted for the sake of clarity;

10 is a top view of a fully assembled filling unit, over which the water is sprayed for evaporative cooling;

Fig. 11 is a sectional view in one, near one end of a Cooling tower with evaporative cooling in the vertical direction through this laid section j

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Figure 12 is a view in horizontal section taken along line 12-12 of Figure 11;

Figure 13 is a side view of the unit of Figure 11, looking in the direction of view that figure seen from the right;

Flg. 14 is a perspective view of a flow distribution device serving baffle, which as such is part of the invention, and

Figure 15 is a fragmentary view in one taken along line 15-15 13 laid section.

In FIGS. 1 and 11, a basic unit or individual system is shown, the collecting container in section has the shape of an inverted right triangle, and wherein a single fan or several fans are provided on a common shaft, which are driven by a single drive motor and which are arranged in the sectional view under the hypotenuse of this triangle so that no part needs to protrude significantly laterally beyond the superstructure of the unit in order to de »Motor and to accommodate the individual fan or the plurality of fans, as is the case with those known from the prior art Plants was previously required. This single system; thus represents a basic form of the invention and a construction unit , whereby an increase in capacity is possible as a result, that similar units are placed against each other at the ends. The capacity of such a multi-unit system can be increased even further by arranging similar units "back to back" so that the section of the collecting container no longer has the shape of a right

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right triangle but that of one placed on its tip has isosceles triangle, as shown in Fig. 2, then below the same sides of this Triangle in each case a motor and the fan are arranged.

Should two assembly units be juxtaposed with their backs appropriate modifications to the sump and drain connections are made so that the collecting tanks are connected to one another and a common water outlet can be provided.

Reference is now made in greater detail to the drawings, in particular but to Figures 1, 2 and 3 from their representation it can be seen that the cooling tower with an upper part

10 for cooling the water and a collecting container arranged in the lower part in the form of a V-shaped trough or container

11 is designed to collect the chilled water. The upper part 10 has a rectangular plan and consists of a number of modular frames, which are superimposed in such a way that four vertical Side walls are determined.

The lower part or saramel container part 11 faces one another to each other two perpendicular walls 12 and IJ, the In each case in the same plane with one of two of the side walls of the upper casing part are arranged, while between these walls 12 and I ^ one at an angle of 45 ° inclined, convergent and intersecting with the vertical Wall 14 is provided, which is shared with the walls

12 and I ^ the V-shaped trough 11 is determined. The water to be cooled is supplied via a distributor head 16 and exits through a number of spray nozzles 17 to thereupon as a result of his

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It is very difficult to run down through a cooling area, which contains a wet deck area in the form of a large number of sheet metal components 18, which are held in frames at horizontal and vertical distances from one another, so that the water is presented with a very large contact surface overall. After the water has then flowed through the cooling area in contact with the numerous sheet metal components 18, it drips off into the V-shaped collecting container 11. - ^} Without prejudice to the fact that this wet deck section is shown in connection with the V-shaped collecting container 11, any wet deck as well as any heat exchange surface provided for evaporative cooling can of course be used in connection with the V-shaped collecting container.

The unit shown in FIGS. 1 to 3 inclusive is equipped with centrifugal fans, which is achieved in a manner to be described in more detail below is that between the surface components 18 in countercurrent an air current rises to the water flowing down, which causes an evaporation of water components that are now with are carried upwards by the air flow and exit the system through the mist separators 19 located on the upper part of the unit.

The heat dissipated from the remaining water is of course released into the surrounding atmosphere with the expelled air submitted. As already mentioned, the cold water drips off into the collecting container. Make-up water flows through Valve 20, which is opened by a float 21, so that the evaporated water as well as that for removal wastewater discharged from impurities can be replaced «.

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The cooled water is taken from the collecting tank 11 through a line 22 and conveyed by a pump 2J> via a line 24 at a point of operational use, for example to a heat exchanger, as shown in FIG. 2 at 25 in schematic form. After this operational use, the water has absorbed heat and must be fed back into the cooling system for cooling. A line 26, which leads to the distributor head 16, is provided for this feedback.

Now that the water cycle has been discussed

den is, it should be noted how the V-shape of the '

Collection container 11 to the amount of retained water supply As the volume of the lower part of the triangular or V-shaped cross-section Trough 11 is small, very little water is retained, which has the distinct advantage that the weight load on the supporting base on which the system is built is kept low.

Of course, it is desirable, if at all possible, to place the fan or fans entirely below the inclined To accommodate wall. If, however, due to certain design requirements, a very large ™

Fan is provided, so can to a certain extent a lateral protrusion over the side wall the system may be required.

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The flow distribution of the air in a fan unit consisting of several fans, as shown in FIG is shown, is to be explained in detail below. As can be seen from Figures 2 and 5, there are two Groups of three centrifugal fans each are provided, namely one on the left in the viewing direction of FIG Group of which the fan closest to the viewer is provided with the reference number 28, and one on the right Group of which the fan, which is also closest to the viewer, is denoted by the reference number 29. The blower 29 and the two fans 30 and 31 are keyed to a common drive shaft 32, A pulley 33 is also keyed onto it which is connected by multiple belts 34 to a drive pulley provided on an electric motor 36. Of the Motor 36 is mounted on a support plate 37, which is shown in Guide rails 38 is slidable. A mounting bracket 39 is connected to the support plate 37, through which a threaded rod 40 is passed. This threaded rod is also designed with a U-profile Part 41 passed through, which is the lowest part of a frame structure for the fan and the engine supporting arrangement is. Nuts 42 are provided on the threaded rod 40 by tightening them or loosening the threaded rods 40 of the motor mount assembly moved without difficulty and held in one position in which a suitable belt tension of the belts 34 is ensured.

An arrangement that is completely the same as that just described is also for the fan 28 and the two behind it Fan provided. In this case the engine is with the Reference number 44, the belt tensioning structure with reference number 45,

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the pulley is provided with the reference number 46 and the common drive shaft with the reference number 47.

All centrifugal fans, for example also fans 28 and 29, suck in the air in the axial direction and expel it in the radial direction. The individual fans are spaced apart, and shaft bearings are provided at each of the two ends of a group of fans. For the construction, the in m

Figure 3 is a typical arrangement in which a front main bearing 48 is provided on the shaft 32, to the left of the fan 29 in the viewing direction, as well as a further main bearing 50 on the end of the shaft 32 remote from the pulley 33. Due to the fact that If a shaft with a larger diameter is provided between the bearings 48 and 50, only these two bearings arranged on the outside are required, but not an additional bearing between the fans carried by a single shaft. The main bearings 48 and 50 are supported by rigid frame members such as members 51 and 52 which extend between U-shaped floor members 41 and the wall 14. The substantially three \ eckförmig formed side portions of each blower being provided with the reference numerals 53, 54 and 55th They are arranged parallel to one another at intervals and extend in a vertical direction from the bottom of the system to the inclined wall 14 of the collecting part. The walls 53, 54 and 55 are shown in FIG. 3, and the front surface of a corresponding wall 56 naturally appears in the left-hand part of FIG Space below the inclined walls 14 and 15 of the collecting units are housed.

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On the outlet side, each fan, for example the fan 28 and the fan 29 ″, is connected to a flow guide channel which is passed through the wall 15 or 14 of the collecting part and ends in a turn that extends in an almost vertical plane, but slightly in one of the Inclination of the respective wall 14 or 15 perforated by the channel extends beveled in the opposite direction. The flow channel connected to the fan 29 also includes a part 58 which is arranged entirely within the collecting container . A corresponding duct part 59 projecting into the collecting container is provided on the fan J50, and one such on the fan 311. Part 6o. In the illustration of FIG. 5, similar parts 61 and 62 are shown for the two fans, which are not provided with reference numbers, are arranged behind the fan 28 in the viewing direction of FIG. 2 and are adjacent in FIG . These duct parts all have the same construction and are usually designed with a rectangular cross section , so that only the duct part for the fan 29 needs to be described in more detail.

In FIG. 4, the fan 29 is shown on a larger scale and with the omission of the side wall 53 in order to show the construction of the flow channel from the tapping side 63 to the mouth opening 64 of the inner channel part 58. The circumscribed by Strömungsleitteile total area is determined by the in the representation of Figure 4 for better clarity detached wall 53, which in a Abstand'parallel to that of * · minor wall 54, arranged between the walls 53 and 54 and extending from the Tapping end 63 from spirally extending, through the side wall ΪΗ of the collecting

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The curved wall 65 passed through the container and only ends at 66, a flange part 68 and the channel part 58. It should be noted that both ends of the spiral-shaped wall 65, i.e. the tapping end at 63 and also the end 66, engage in the channel 58, which is attached with its flanges 68 to the inner surface of the wall 14 of the V-shaped collecting container 11. The flow path of the air determined by the walls 53, 54 and 65 as well as by the additional duct part 58 and the flange part 68 is formed with a constantly increasing cross-sectional area in the direction of flow, so that between the tapping end 6j> and the mouth opening 64 of the duct arrangement a considerable The extent to which flow pressure is converted into static pressure. The fan 29 rotates counterclockwise in the viewing direction of FIG.

This is the case with the symmetrically structured unit with the rear sides facing each other In the figures 2, 4 and 5 shown collecting container or collecting part 11 in the middle by a partition

69, which extends down between the walls 12 and \ J> from the upper end of the collecting part to a point slightly below the water level in the collecting container. Below the lower end of the partition wall 69, a plate 70 provided to prevent air from being released is arranged, which extends in the horizontal direction somewhat above the outlet pipe 22 over the bottom of the collecting container. The plate

70 also serves to ensure that water is drawn evenly to enable from the collecting container 11, since it is narrowed towards one end of the mandrel in such a way that the incoming water at the end remote from the outlet

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a wider passage opening is available. Immediately above the plate 70 preventing the entrainment of air can be arranged a sieve which is carried by suitable supports.

When looking at Figures 1, 2 and 5 it becomes apparent that the air flowing out of the mouth openings of the channels 57 up to and including 62 is first directed into a somewhat narrowed space, which is directed downwards through the water level, in front of the mouth opening of the channel through the partition 69 and is bounded behind the flow channel by the inclined wall 14 and 15, respectively. Even if the static pressure rises to a certain extent before the air flows out of the individual duct parts 57 to 62, the flow velocity of the air flowing out of the orifices of these ducts is still too high for that alone an effective and uniform flow distribution of the air over the entire cross-sectional area of the filling area lying above the V-shaped collecting container part 11 could be achieved. In the embodiment of the invention shown in FIGS. 1 to 4 inclusive, various precautions are taken which are suitable for contributing to the uniformity of the flow distribution of the air over the total cross section of the filling. One of these precautions can be seen in the fact that the part of the collecting container chamber located above the blower outlet opening is designed with a cross-sectional area that increases in size in the direction of flow of the air rising from the mouth opening of the blower duct. This in turn is of course due to the fact that the vertical wall or central partition

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wall 69 interacts with the inclined wall] Λ to delimit an area which, in a vertical section, has the shape of a right-angled triangle placed on its apex, so that the air flowing up from the bottom of the collecting container necessarily reaches an area of steadily increasing cross-section got to. This brings about an increase in the static pressure to a certain extent, which is added to that already caused in the outlet channels. μ

If reference is now made to FIG. 5, it can be seen that the horizontal distance between each two channel parts, that is between the channel parts 57, 61 and 62 on the left side of the system and between the channel parts 58, 59 and 60 on the right side thereof, is dimensioned so that the space between the channel parts is the same the width of these parts themselves or greater. To calculate the required distance, a about 3 * 70 meter long system the following rule of thumb as proven expedient:

the distance between two fans should be equal to the f

Length of the collecting container part minus the sum of the width dimensions of the fans arranged in this part divided by the number of fans present in that part.

According to this formula, there are still considerable gaps between the flow channels, and it has been shown that that this contributes significantly to the achievement of a high efficiency of the plant.

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The distance between the fans at the ends of a group and the respectively adjacent end wall is not less than half the width of an air duct. The arrows in FIG. 5 indicate in * like a part the outflowing air, after hitting <$ ie Partition 69 deflected somewhat out of its direction, now in the spaces between the fan ducts to the upper part of the collecting container rises.

^ The air escaping from Auslassströmungshauben the blast air impinges on the provided in opposition to the opening of the flow hood vertical wall, and a 'portion of this air is deflected directly upwardly in the direction of the wet deck part. The remaining air portions are deflected from their direction by 180 ° and flow into the spaces between the fans, while they simultaneously spread upwards through the V-shaped collecting container part. The distances between the fans must therefore be chosen so that just the right amount of air can penetrate into these spaces and fill them. It was found that the fan width, the distance distribution along the drive shaft and the length-width ratio in the dimensions of the V-shaped one were used to achieve optimal cooling performance. Collection container are decisive. For example, in the case of Feiner certain systems, whose collecting container part was 3 * 66 meters long, three fans with a diameter of 559 millimeters each and a width of 533 millimeters were provided, the distance between two fans each being 686 millimeters and between the fans arranged at the end and the neighboring Eftdwan-

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There is a gap of 533 millimeters between the collecting container Width remained. A deviation from the above-described optimal spacing arrangement of the fans can be a uneven flow distribution of the air result, which increases the cooling capacity of the system is affected. When the air finally reaches the upper end of the V-shaped collecting container part, so is their flow velocity has been reduced with a simultaneous increase in the static pressure. So is the air although it is largely evenly distributed when it reaches the upper end of the V-shaped collecting container part, it does a further refinement can be made in the flow distribution Achieve air before it reaches the wet deck when antechamber sections 170 and 71 are provided will. These antechambers are used to compensate for slight differences in the flow velocity of the upper one Air flowing out at the end of the V-shaped collecting container part.

Above the collecting container part 11 and below the lowermost layer of the filling there can therefore be an antechamber section or several such prechamber sections can be provided, which are frames, each for represent a structural unit serving for flow distribution. The lower of these building units, which the Reference numeral 170 is shown in Figure 1, from which it can be seen that the unit consists of a rectangular frame consists, which is determined by U-profiles, which are so arranged are that their flanges extend outwardly, the side members having the reference numerals 73 and 74 are. On the inner surface of the link 73 is an L-shaped profile formed angle member attached, which is a deflection angle flange 77. The horizontal part of this deflection angle flange 77 usually extends about 50 to 75 millimeters in length in the horizontal plane

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Direction of the fan duct. If, on the other hand, systems are placed against one another with their rear sides, as shown in FIG is, the structural unit 170 is formed with a central member 75 on which deflection angle flanges 77 are provided are each extending in the direction of the fan assembly concerned. The frame unit 71 is In all respects it is constructed very similarly to the frame unit 170, except that here the deflection angle flange 77 is omitted.

The two frames will cover the upper part of the V-shaped trough 11 and a large space with a rectangular floor plan under the wet deck made available, which serves the purpose of enabling a more even distribution of the air flowing into the filling., The Flow distribution of the air is also achieved through the deflection angle flange 77 improved considerably. Thus, the V-shape of the trough 11, carry the arrangement of the one Frame 170 and 71 defining the space and the deflection angle flange 77 as a whole and each individually for contribute significantly to the efficiency of the system, enable an even flow of air and increase the cooling capacity considerably.

The measuring deck is denoted generally by the reference number 18 in FIGS. 1 and 2 and in greater detail shown in FIGS. 7 to 10 inclusive.

Although in the representation of Figures 1 and 2 a with

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Blown air working (pressurized) cooling tower reproduced any other centrifugal fan or impeller fan arrangement may also be provided, likes this in individual cases in terms of blow ventilation (pressure ventilation) or induced draft ventilation (suction ventilation) work. Merely for the sake of simplicity of representation, only one specific way is used here received the fan assembly.

An air flow is generated by the fan 29, which is driven by an electric motor 36 . This air flow is evenly distributed over the surface of the lowermost filling section 79. The water from which the heat is to be removed is supplied from above via a distributor head 16 and distributed over the filling inserts by spray nozzles 17 in the form of a fine, uniform mist. If it were possible to give this mist resistance in a cooling tower, a very high efficiency could be achieved in a small space, since in this case a very large surface of the water particles would be exposed unprotected. Man tries to grasp this in a mist-filled tower, but unfortunately I can not be avoided that the water droplets run together very soon und_stets large werdendgJTropf en emerge. This makes use of the fact that a high degree of efficiency can be achieved with the fine mist directly below the spray nozzles, and as soon as the droplets cluster on them, namely in an area 10 to 15 centimeters below, they hit the first

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Layer of infill components l8 on> the at this point are provided. The water droplets then fall on the filling parts, whereby in the uppermost filling section 8o the parts a thin film of water of uniform thickness is formed. This filling section contains a large number of sheet metal components 18, the horizontal ones and vertical distances from each other supported in the frame are, so that the water droplets are very large overall Surface is presented. After the water has run down over the surface of a filling part 18 and has given off a certain amount of heat in the process "it drips at the lower edge 89 in the form of small drops of approximately of the same quality in which it is also immediately is below the spray nozzles. So these small droplets offer a great deal to the air flowing upwards large attack surface, so that a powerful heat transfer zone is created. Start the If small drops clump together again, they hit another, more intermediate layer of filling parts. After the water then over the the number of filling units required to achieve the desired cooling effect has been trickled down, drips it finally into the V-shaped collecting container 11.

Above the combination of the blower, sump, and antechamber sections are three superimposed wet dee building units 79, 80 and 8l arranged. The frames 79 and 80 are as modular Units formed that are interchangeable with one another. Accordingly, only the frame 79 will be described in more detail This description is then of course also equally applicable to the frame 80.

The frame 79 is 10 in FIGS. 1, 2, f, 9, tttid

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posed. As can be seen from FIG. 10, the frame 79 consists of four U-profile members 83, 84, 85 and 86.

The sheet metal filling parts 18 can easily be installed and held in a frame such as this frame 79. It can be seen from FIG. 8 that each of the components 18 is formed with an upper and a lower straight edge part 88 and 89, respectively, and with a curved part 90 in between. Spacers 91 are formed on the edge parts 88 μ and 89 by means of a stamping and folding process. Spacers or tabs 92 of the same effective height, which extend from the concave side of the curved part 90, are also punched out of this, the particular cross-sectional design of these tabs being due to the fact that the extent of their outer edges is adapted to the curvature of the metal part must from which they are formed. The spacers 91 and 92 make any other arrangement for maintaining predetermined distances in the support frame 79 superfluous. As can be seen from FIGS. 7 and 10, the sheet metal filling parts 18 are installed in such a way that they extend parallel to the U-profile members f 85 and 86. The outermost filling part 18 engages under a holding flange such as flange 93 and is thereby held in place, while the remaining filling parts are installed side by side, with the presence of the tabs 91 and 92 ensuring that they are arranged at the intended intervals . Halfway between the U-profile 85 and the U-profile 86, two adjacent filling parts are arranged in such a way that their concave parts 90 face one another (see FIG. 1). With

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In other words, this means that the PUllungsteile on each of the U-profiles 85 or 86 provided in parallel to these with the convex side of their arched Parts 90 rest against the U-profile in question.

The mounting flanges designed in the form of Z-profile parts 93 serve a dual purpose. On the one hand, lead they those parts of the water that run down on the inner surfaces of the walls of the wet deck structure, in the air flow back so that the desired distribution is achieved. Second, however, they serve to support the U-profile beam Adjacent panels in the intended position ■ hold in the sedn convex part away from the center of the arrangement and turned outwards. Through this Precautions are taken to ensure a uniform flow rate of the air over the entire surface of the wet deck superstructure unit ensured away.

The structure of the arrangement just described allows to assemble a construction unit such as the frame 79 in a simple and economical manner. It it should be noted that the arrangement of the U-profile members 83 and 84 is such that their flanges extend inward. For assembling such a construction unit the procedure is such that the FUllungstei-Ie l8 first pushes into a U-shaped frame structure open on one side, which is supported by one of the for the Long sides provided U-profile beams 85 or 86 and formed by the two end-side U-profile beams 83 and 84 will. The filling parts l8 here rest on the inwardly protruding flanges of the end-side U-profile girders 83 and 84. After half of the total number of filling parts has been inserted, you build the rest of these

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Divide in reverse order to create the aforementioned grouping. Then is the entire set of Filling parts installed, so hold-down rails 97 and 98 are attached to the end walls 83 and 84, with the flanges of these rails on the upper marginal edges the individual filling parts come to rest so that they are held in their position and the Assembly unit can be transported as a whole and handled as a unit before assembly.

As can be seen when looking at Figure 10, the Filling parts 18 are not all identical to one another, but are usually a staggered arrangement the spacers 91 and 92 on adjacent filling parts 18 provided in order to prevent the spacers from entering the punched-out area of the neighboring Engage the filling part.

In the structure of the filling or wet cover surfaces known from the prior art, metal sheets were provided which are in Direction of the air flow and extended over the total height of the wet deck section. In contrast in relation to the arrangement according to the invention, there were between the individual filling layers in a vertical extension no spaces provided. The towering wet deck panels the known arrangement required not only large amounts of construction material, but Hessen also in so far as to be desired, as their operational efficiency in no way corresponds to the amount of material used was proportional as the water merged or converged to "streams" near the lower ends of the sheets.

Ideally, the water flowing down over a flat sheet should cover the entire surface on both sides

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away in a thin. Keep the film evenly distributed. The envisaged formation of the wet cover surface ensures a much better retention of this uniform film due to the fact that the height of each filling part is only small. In a preferred embodiment, a height of 102 to 127 millimeters is provided for each of the wet deck filling parts. A space that remains free vertically between the individual wet deck superstructure units or an intermediate chamber of approximately the same height as a filling part (although this height can vary between half and one and a half times the height of the filling part ) serves as a redistribution zone in which the down flowing water is distributed uniformly over the surfaces of the next lower filling unit, where it forms a thin film again, the le whose Füllungstei 18 covers.

It has been shown that various critical factors have to be taken into account in the design of the filling parts 18. Since the place sharing between the adjacent filling rising air always only in one direction perpendicular to the direction of spacing between adjacent filling parts passage in this airflow turbulence can be caused by the fact that Wellun be provided gen which are similarities at each of the filling portions Lich. If the concavo-convex curved part 90, which represents this corrugation, is formed with too great a curvature , the film of water flowing down cannot follow the curvature. On the other hand, however, the greatest possible curvature is desired in order to bring about as intensive a contact as possible between the air and the water and to ensure that it is washed through as thoroughly as possible

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to ensure the air on the water surface, whereupon the air flow with a simultaneous slight increase the static pressure should be evenly slowed down a little before the air at the upper edge of the filling parts flows off. A main radius of curvature of 15.88 to 22.22 mm has proven to be useful for this, secondary radii of 12.70 to 19.05 mm are provided at those points where the curved part in the edge parts 88 and 89 of a filling component with a height of 108 to 114 mm are transferred.

It has been found that the best distance between adjacent panels is about 12.70 up to 22.22 mm is selected. If the arrangement is closer together, there will be stagnation phenomena, with the water denying the Gaps between neighboring components bridged; a wider distance has also proven to be less suitable proven. It is desirable to arrange the filling parts at such a distance from one another that in a certain amount A reciprocal nesting is carried out circumference, that is, the convex side of the curved part 90 should be into the through the concave area of an adjacent filling component extend into the described cavity. So if you wanted the edge parts 88 and 89 of any filling component 18 are connected to one another by a straight line, so the adjacent component would be with the convex one Range its bulge 90 to a point above this Reach straight away, the distance from this up to about JO percent of the distance of the horizontal distance of two adjacent panels.

As an example of the dimensions of a preferred embodiment let it be noted that in a specific case

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a filling component l8 a finished height of 111.12 mm, a main radius of curvature of the arched part of 19 * 8 ^ and had minor radii of curvature of 16.67 mm, the total length of the bulged portion being 60.0 mm, while the straight edge parts adjoining this each had a length of 21.6 mm. The spacers 91 had a length of 15.9 mm, and this corresponded to the distance between adjacent filling components.

The frame 81 is not like the frames 79 and 80, but is about twice as high. The reason for this is that not only a filling layer is to be accommodated in the frame 81, but also the distributor head 16 and the various pipelines 27 * extending from it are on the inside of the frame 8l flanges and hold-down devices are provided, which are provided with the reference numerals 95 and 96, as shown in FIG Figure 9 is shown. The filling parts 18 are pushed into the upper frame unit 8l in the same way as in the frame units 79 and 80, the only essential difference being that they have a lower proportion of the total space enclosed by the frame claim.

These wet deck superstructures can then be used in a reciprocal manner Coverage position above a suitable collecting container are screwed together, with either a blow ventilation (pressure ventilation) or induced draft ventilation (suction ventilation) can be provided and so many structural units Find use as required to achieve the desired cooling effect. .

Figures 11 to 15 inclusive serve for explanation

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of the third aspect of the invention, namely that aspect, the novel provisions for achieving a uniform Flow distribution of the air exiting a pressure fan on the outlet side in the entire space into the inlet end a wet deck connecting antechamber concerns.

Although this third aspect of the invention is combined with the first and second aspects explained above in the illustration of FIG to lay the determination value, that the invention can be found on cooling towers also apply where the collection has a different training and dec structure of the wet deck is different.

In Figures 11 to 15, a cooling tower is shown in which Axial fans are provided for pressure ventilation, which embodies the third aspect of the invention in this cooling tower is. The same reference numerals are used in FIGS. 11 to 15 to denote corresponding and similar parts used as in the previous figures.

The lower or header section 11 of the cooling tower shown in figure 11 has in the sectional view of Figure 11, a trapezoidal shape and is bounded by three vertical walls 12, 1J> and 69 and by an inclined or sloping wall 14 'and a bottom wall 21st The walls 12, IJ and 69 are approximately in the vertical alignment of the corresponding walls of the modular units 71, 79, 80 and 81 arranged above them (see

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Figure 12). Because of the inclined arrangement of the wall 14 *, the bottom of the collecting container area 11 has a smaller surface area than would be ascertained for any horizontal planes above it. In the inclined wall 14 ^! Two fan ducts 122 and 123 with a circular cross-section are installed at a distance from one another, in each of which a hub 124 or 125 is provided in a central position, from which seven radial guide vanes 126 extend. The cross-sectional shape of the radial guide vanes 126 is shown in FIG. Shaft bearings 127 for supporting a fan shaft 128 are arranged inside the hub 124, on the right side of the hub 124 in the viewing direction of FIG 130, which is connected by a belt 34 to a double pulley 132 provided on an electric motor 36 arranged between the channel and the channel 123. Bearings 138 for the shaft 136 are provided within the hub 125. The impeller 137 is keyed onto the shaft 136. The impellers 129 and 137 are thus both driven by the motor 36, due to the arrangement of the belts and pulleys with the same direction of rotation and the same speed. The air flows into the channels 122 and 123 through orifices 139 and 14o, respectively, which are used to reduce the turbulence in an outer, annular area of the channel and to increase the volume accordingly.

ö '

Blowing efficiency up to about 9Ö flanged to the outside are. The air then emerges from the mouth openings 14l and 142 of channels 122 and 123, respectively, and flows out then continue in the manner indicated in FIG. 11 by the arrows.

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The inclined wall 14 ^f , together with the walls 12 and 1J5, also defines a space S (see FIG. 11). This space extends below the space delimited by the upper part, its outer walls, apart from small offsets, being in vertical alignment with those of part 10. As can be seen from FIGS. 11 and 13 ^{, the parts of the channels 122 and 12} lying outside the wall 14 f} as well as all parts located within these channels, insofar as they are arranged on the outside of the wall 14 ', are accommodated in the space S. The space S also accommodates the motor J> 6 , so that in the end no part of the blower device protrudes outward beyond a plane through the edge delimitation of the cooling tower on the right-hand side in the viewing direction of FIG.

The water to be cooled is fed in via a distributor head 16 and flows below it already further above Reference in the manner described in Figures 1 to 10 through the cooling area 10 downwards.

The flow distribution of the air over the cross-sectional area of the modular units 79, 8o and 8l is essential for solving the problem of cooling large amounts of water in a rational manner. For this purpose, a guide plate 148 is provided, the shape of which can best be seen from FIG. 14, while its arrangement is most evident from FIG. This guide plate is carried by the end walls 12 and 11> of the collecting container part 11 by means of suitable mountings (not shown), while a tether or connecting piece 149 is provided on a central part of its length, which is part of the wall 14 *

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is guided above the motor 36. The baffle 148 reverses the air exiting from the channels 122 and 123 in a curved manner Area whose curvature extends over an arc of more than 90 °. This area has on average almost the cross-sectional shape of a shell wall. The lower edge 150 of the baffle 148 extends into the upper one Part of the airflow, bundled in a generally cylindrical shape, exiting channels 122 and 123. The upper edge 151 of the guide plate 148 is located above the P uppermost parts of the channels 122 and 123 and is even somewhat to the right in the viewing direction of FIG of the mouth openings 141 and 142 of these channels, at the outer curve of the guide plate 148 is near the lower edge 150 a small deflection flange 152 with an L-profile is provided.

A further guide plate 153 is arranged on the left side of the guide plate 148 in the viewing direction of FIG. This Guide plate 153 extends essentially transversely through the entire antechamber from the wall 12 to the wall The baffle 153 is a flat plate which is arranged at an angle to the vertical and fc which, together with the wall 69, defines a space of generally triangular cross-sectional shape, at the bottom of which At the end a narrow slot 153a remains free for the entry of air, while at the upper end a wider exit slot 153b is cut out for the air.

It should be noted here that the arched inner or concave surface of the baffle 148 is a direction reversal of the opposite flow (in the viewing direction 11 therefore causes air flowing away from right to left, so that it now moves from left to right in the illustration of FIG.

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moves away when it flows away from the baffle between its upper edge and the upper outer surfaces of the channels 122 and 123. The purpose of this reversal of the flow direction is to supply the wet cover surface 10 in the part above the channels 122 and 123 with a sufficient amount of air. In addition, the air also tries to follow the outer surface of the guide plate 148, which also contributes to an increased uniformity of the flow distribution. Λ In this context, attention should be drawn to the arrows A in FIG. Also of importance is the fact that the upper part (148 ¹ ) of the guide plate 148 prevents larger amounts of water dripping from the filling part on the inner or concave surface of the guide plate due to the curvature of the guide plate over an arc of more than 90 degrees can get. The air emerging from the channels 122 and 123 thus flows along the guide plate 148 and thereby suffers the complete reversal of its flow direction, while the upper part 148 'of the guide plate at the same time keeps the concave guide surface dry. By keeping the inner or concave surface of the baffle 148 dry it is achieved that I.

no water from the lower part of the inner surface of the baffle can seep into the fan ducts. The baffle flange 152 is also used to protect against water Device which prevents the water flowing off on the outside 3 of the guide plate 148 from entering the fan ducts. The L-profile of the deflecting flange 152 causes the water film from the outer surface of the baffle 148 tears off and the water drips down more or less vertically into an area, which is already well beyond the mouth of the flow channel. The deflector flange 152

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is arranged on the outer surface of the baffle 148 so that its lower edge does not get into the Air flow extends in and so does not hinder the outflow of air on the outer surface.

Facilities of the type described here can meet the requirements can be adapted to very different operating conditions in terms of heat dissipation. It is also a Operation in different weather conditions

fc envisaged. Under certain conditions there is a Operation possible in which the fan fans remain switched off for longer periods of time. This can be the Be the case when the outside temperature is low or if no large amounts of heat need to be dissipated and if both come together. Another mode of operation would be that of a cyclical working actuation of the fan blower, in which these are put into operation, if the water temperature in the collecting tank rises above a predetermined value in order to be switched off again, as soon as a desired low water temperature is reached. If the fan is out of operation, it is in particular mass against that from part 10 dripping down

'Water sensitive. However, it is precisely at this point that a further advantage provided by the invention becomes apparent. When the fan blowers are at a standstill, the bend at the upper end portion 151 of the baffle 148 serves an important purpose. If it were not present, portions of the water falling on the upper part 148 'of the guide plate 148 would seek to encircle the end 151 and then flow off on the inside or concave surface of the guide plate and thus get into the fan ducts. The bent portion 151 causes but now that the ser What _r at its end in a straight direction and therefore drips

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falls on the outside of the cylindrical fan 122 and the cylindrical fan 123. On the canals 122 and 123 are provided at 154 marginal lips, the able to hold back the water to such an extent that it flows off the cylindrical walls along the circumferential direction and does not drip off at the edge of the cylinder, possibly in the flow channel in question to get. It should be noted that the channels 122 and 123 are arranged with a slight slope, which in FIG the viewing direction of FIG. 11 drops from right to left. This also ensures that the water that may possibly penetrate into the flow channel in the form of spray mist drains off by itself.

The cooling tower provided by the invention is capable of operating at different average flow rates suitable for the air flowing through the filling part 10. For example, it could be determined that at flow speeds of around 150 meters per minute or less, the baffle alone is enough 148 is quite sufficient to bring about a good flow distribution over the entire filling part 10. at On the other hand, there are high flow velocities, for example those of around 180 meters per minute the tendency that a small part of the air with a kind of channel effect along the surface of the wall 69 seeks to rise in order to then flow through the corresponding part of the area 10 so quickly that even water is entrained and in a local area which is immediately to the right in the viewing direction of FIG lies next to a plane encompassing the wall 69,

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exits through the fog absorbers. This is now prevented by the baffle 155, which balances the flow the air helps to bring about. This baffle is used in the between the slot 153a and the slot 15Jb the rising air causes a scattering effect. Through this is the longitudinally flowing ent on the wall 69. air slowed down, and consequently can even with high average Flow velocities in the filling part 10 still have a good flow distribution over its overall cross-section be achieved.

It is clear that the inclination of the wall 14 'has the effect, among other things, of keeping the water reserve retained in the system low. It also allows the fan motor 36 and the fan to be arranged essentially within a space which is circumscribed by the vertical projection of the rectangular plan of the wet deck section 10 of the system. In addition, the steadily increasing size of the longitudinal sectional area of the antechamber in the direction from the water level to the first add-on unit 71 also has the effect to a certain extent of an increase in the static pressure in the vertical port movement direction of the air.

Figure 13 is a front view showing a System with several fans, one possibility being shown, several fans by a single drive motor to drive, which is arranged in the space below the inclined wall 14 '.

It should be emphasized that such a system with evaporative cooling can be expanded to a desired capacity simply by having similar

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Units either end to one another, so that the arrangement shown in FIG. 12 is extended, or that similar units with the rear sides juxtaposed in such a way that in the graphic reproduction, for example, a mirror image Representation of the arrangement of FIG. 11 would appear immediately to the left of this. In the case of large systems, a Combination of rear and in the lateral direction at the ends opposing units provided be.

In the appended claims the designations are "Blower" and "fan" are used as generic terms and refer to any devices that are too are capable of moving air.

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Claims (4)

Pat en tan sprue he Evaporative heat exchanger with vertical housing and with air circulation in countercurrent to the fluid to be cooled or condensed, in particular water, with nozzles connected to a fluid supply line in the housing below an upper defogging device for injecting the fluid in uniform distribution over the entire horizontal housing cross-section, including fillers or trickle plates for Mediation of the largest possible contact area between the upflowing air and the downflowing fluid and / or at least one coil containing a second fluid to be cooled or condensed, and below it a fluid sump containing the fluid sump, the fluid flowing down from the filling bodies or trickle plates or coils receiving pan connected to a fluid discharge line are provided, furthermore at least one in the space between the sump surface e in the pan on the one hand and the filling bodies or trickle plates or pipe coils on the other hand there is a conveying fan, characterized in that above the mouth (141 or 142) of the air outlet pipe (122 or 123) each fan (124 to 1J57) has a upwardly extending guide plate (148) is arranged, which with its concave, over an arc of more than 90 ° extending surface of the pipe mouth or mouths (141 ; 142) faces and protrudes with the lower card (150) into the air flow emerging from each opening and with the upper, approximately horizontal edge (151) extends above each opening. 309871/0368 Case 18F / Tr.A. If- 2. Heat exchanger according to claim 1, characterized in that the guide plate (148) with the upper, approximately horizontal Edge (151) the mouth (141; 142) of each air outlet pipe (122; 123) of the fan or fans covered. 3. Heat exchanger according to claim 1 or 2, characterized in that that a second horizontal guide plate (155) is provided which interspersed with that of the air outlet pipe (s) (122; 123) of the fan (s) Wall (14 ') opposite housing wall (69) an approximately conical, towards the fillers or trickle plates (l8) or pipe coils towards widening channel (153a, b) includes. 4. Heat exchanger according to claim 1, 2 or 3> characterized in that underneath the fillers or trickle plates (18) or coiled tubes for uniform air admission the same is provided with a horizontal guide plate (77) extending approximately horizontally against the blower air flow is.