HU199005B - Apparatus for utilizing the heat content of return water and liquid level control gear for closed condensing vessels - Google Patents

Abstract

The present invention relates to a device for utilizing the condensate heat content, in which a lower bell (10), an upwardly open top bell (12), and an uplink bellows (11) formed by its upright cylindrical container (1) are located in a stationary cylindrical container (1). a. The upper bell (12) has a heat recovery heat exchanger (9). The lower bell (10) can be surrounded by an open shield bell (21). The hot condensate is fed to the lower bell (10), the cooled condensate is discharged from the bottom of the tank (1). An annular gap (13) is provided between the bells (10, 12) and the inner surface of the container (1). If necessary, a separate cooling chamber (33) can be formed in the lower part of the container (1) by means of an open partition plate (31) containing an opening (32), in which a cooling heat exchanger (34) can be placed. The liquid level regulator has two vapor-cushion fluid transfer tanks operatively connected to the condensate recovery tank (1). About this EN 199005 B Scope of the description: 13 pages, 9 pcs -1-

Description

The present invention relates to an apparatus for utilizing the heat content of condensate water, which comprises a reservoir, preferably in the form of a cylindrical cylinder, a conduit for feeding hot condensate water to the reservoir and removing cooled condensate from the reservoir, and a heat exchanger located therein. The invention also relates to a liquid level control device for closed condensate tanks, in particular for the apparatus according to the invention.

In the practice of general snow supply, when using a steam heating medium, steam condensates, i.e. condensates, in other words condensates, which are to be collected and removed from the system, are frequently and in large quantities generated during heat transfer. For both industrial and other condensing systems, it is a challenge to collect and transmit condensate, often from multiple sources, at varying pressures with different pressures. The most common method of collecting condensate is the so-called. open pressure systems and centrifugal pumps for their transport. The widespread distribution of the latter is primarily explained by their relative operational security; their disadvantage, however, is that, especially for small volumes, they represent a relatively high cost in the overall system. Containers used in open systems are generally flat bottomed, rectangular or circular when viewed from above.

One long-known and widely used condensate drainage and transfer system may have multiple open condensate collection tanks connected by a line containing a centrifugal pump. The first, the so-called. conduits for returning condensate flow into the collection tank and a conduit from the bottom of the tank into which a centrifugal pump is installed. The function of the centrifugal pump is to discharge the condensate from the first tank - the collecting tank - into the second so-called. transfer to a central container. This system, like all open systems, is unfavorable from an energy management point of view and entails significant heat losses. Namely, in the first container, condensation water, predominantly above 100 ° C, comes into contact with the open air, boils and steams in an atmospheric environment. The source continues until the condensate has released its hidden snow content and its temperature has dropped to the boiling point temperature of the water at atmospheric pressure or to a temperature of at least close to it. Once the tank is open, the release vapor, the so-called vaporizer, is released. the keg vapor - usually through a duct - is discharged into the open air without recovery, which naturally results in a loss of energy. The temperature of the condensate in the second tank is further reduced.

The spread of open systems is also explained by the fact that condensates of different pressures can be collected in one container without much technical effort, so the device is simple, inexpensive and can be manufactured in series, and the fact that temperatures above 100 ° C cannot occur in an open container. However, open condensate collection tanks also have serious drawbacks such as not being used in closed pressure systems; not capable of effective steaming; because of the low height and the unfavorable shape, the temperature stratification of the container is ineffective, making it difficult to provide a suitable space for the liquid heat extraction; for condensate lifting pumps, only a tank placed above the floor, that is to say high, ensures cavitation-free operation, which can therefore only be achieved by using a container support structure at a significant additional cost.

Pressurized closed systems, which use separate tanks to collect condensates of substantially different pressures, are intended to eliminate the disadvantages or losses of open condensate collection systems. Namely, if condensates of different pressures were connected to a single pressurized container, and if higher pressures were overloaded in volume, lower pressurized condensates would no longer be fed to the container because they would not be able to open a non-return valve. If, on the other hand, a non-return valve was not installed, there would be a risk that the high pressure condensate would be recycled to the lower pressure system. Separation is thus absolutely necessary, but the use of a separate cylindrical closed hopper and pump with embossed ends separately for each pressure stage increases the installation costs so much that, unlike these pumps, for example. the transport fluid at 140-180 ° C and the avoidance of a cavitation hazard (supply) have higher technical requirements. These problems are a major barrier to the widespread use of multi-tank pressurized systems, and are often only applicable to larger equipment.

The risk of cavitation, which increases with the closure and pressure of the tanks, can be reduced by the use of stationary cylindrical tanks, thereby increasing the inflow height of the pumps. This discovery has led to the development of a known closed pressurized condensate collection device having a cylindrical closed container. Condensates of different pressure levels are collected separately from each other in relatively small vessels and transferred to a stationary cylindrical container by vapor pressure. The recovery is done by steam auxiliary energy - steam condensate lift. In the pipelines coming from consumers, double non-return valves ensure the indispensable isolation of each branch and, in the event of failure, absolute safety. Condensates

The flow of HU 199005 Β is controlled by level switches and solenoid valves and these, together with the design of the tank, ensure that condensates with a pressure lower than the pressure in the tank can enter the tank. The apparatus allows for the smooth return of condensates of various pressures to the heat supply system, but the favorable utilization of the heat content of the condensate water is not considered to be solved.

It is an object of the present invention to provide an apparatus which optimizes the utilization of the heat content of condensate water, ensuring maximum heat removal from the condensate water in a structurally simple manner at a low investment cost.

The present invention is based on the discovery that by providing a fast and efficient temperature stratification of the feed liquid in a stationary cylinder container and placing a heat exchanger in the upper highest temperature range of the tank, the heat content of the condensate is maximally efficient. and can be optimally utilized, for example, for domestic hot water production. The present invention is further based on the recognition that the desired rapid temperature stratification - the so-called "high temperature stratification". instead of a free-flow gravity heat exchange, instead of a directed free-flow heat exchange, it is provided by a directed free-flow heat exchanger member having an upwardly opening lower bell in the lower part of the stationary container, an upward opening in the upper part of the container they comprise a riser connecting them, substantially smaller in diameter than its container.

On the basis of these findings, the object of the present invention has been solved by means of an apparatus which preferably comprises a stationary cylindrical tank, a conduit for feeding hot condensate into the tank and removing the cooled condensate from the tank and a heat exchanger in the tank. having a downflow regulator member having a lower bell open upwards, a top bell open upwards and a riser connecting these bells to each other, the upper bell of which comprises a heat exchanger for utilizing the heat content of condensed water, or / and an upper bell a conduit for the circulation to the heat exchanger, comprising a circulation pump, from which condensed water is discharged into the water space below the upper bell of the container; the conduit for supplying the hot condensate water is encapsulated in the lower bell and there is a constant width gap between the outside of the bells and the inside of the container. Usually the tank has a liquid space below, a steam space at the top, a condensate drain line from the lower part of the liquid space, preferably from the lowest point of the tank, into which a pump is inserted, optionally a vapor depressurizer containing steam. out, preferably at the highest point of the container. According to another feature of the invention, the container has a fluid level control device which also functions as a level switch for a fluid level sensor. has a lifting pump, which is operatively connected by an electric line and is connected to a cooled condensate drain line.

A preferred embodiment of the apparatus is characterized by having a lower and laterally closed, top-open shielding bell surrounding the lower bell, which is spaced from and spaced from both the container sidewall and the outside of the lower bell. the width of the openings is preferably constant and the upper edge of the shade bell is spaced over the top of the lower bell. In most cases, the reservoir, the lower and upper bell of the riser and the riser, and the shield bell surrounding the lower bell, are cylindrical in shape and concentric with the reservoir.

In a further embodiment, the height of the container is about 3 to 10 times the diameter, preferably about 3000 to 25000 mm; the width of the gap between the lower and upper bell and the shield bell and the container sidewall and the shield bell and the lower bell being about 0.025 to 0.05 times the diameter of the container, preferably about 25 to 125 mm; the height of the lower and upper bells being about 1/6 to 1 / 30th of the height of the container, preferably about 500 to 1000 mm; and that. extending the upper edge of the shade bell above the top of the lower bell up to about twice the height of the latter; the riser has a diameter of about 0.08 to 0.1 times the diameter of the container, preferably about 80 to 250 mm, and has a length of at least three times the height of the lower and upper bell.

If the temperature of the introduced condensate water is so high that it can produce boar steam, the efficiency of the heat utilization can be further increased by having an internal heat exchanger or / and an external heat exchanger for utilizing the heat content of the boar steam.

Another feature of the invention is a cooling space formed at the bottom of the container under the lower bell and separated from the rest of the interior of the container by an open separation plate, preferably a central opening, in which a cooling heat exchanger is disposed or / in the vicinity of the opening of the open separation plate, a conduit for circulating a condensate drainage condensed water to the lower part of the cooling space, preferably to a condensate drainage outlet, is discharged to an external cooling heat exchanger. In this case, it is advantageous if the open separating plate is horizontal or substantially horizontal and has the same diameter as the inside diameter of the stationary cylindrical container.

HU 199005 és and its opening has a diameter of 0.08-0.1 times the diameter of the container, preferably about 80-250 mm.

In a further preferred embodiment of the apparatus according to the invention, a tray for receiving condensate of the heat exchanger e is disposed beneath the heat exchanger in the vapor space, from which at least one, preferably more, of the downpipes protrudes from the downpipe or downpipes. they flow into or out of the buoyancy of the flow control member. In this case, it is expedient for the fall pipe or pipes to fall below the middle region of the riser, preferably around the lower third thereof, or to enter the riser.

Another embodiment of the apparatus is that it has a conduit for supplying boiler auxiliary feed water, which preferably ends up in the steam space of the tank. Preferably, a nozzle for atomizing the water is connected to the end of the replacement feed water supply line in the steam space. It may also be advantageous to connect a line containing a pump from the lower part of the tank to a line for discharging water from the tank to a degassing feed tank by means of a flow control valve, and a gas outlet or fitting with a stop valve; finally, when the supply water to the steam space is connected to one or more heat exchangers in the tank to provide a supply of preheated water to the steam space; or / and a steam line, preferably containing a vapor pressure reducer, enters the vapor space. In the latter case, it is expedient to have a water softener inserted in the supply water supply line and the supply water supply line into the tank from the rest of the interior of the container into the heat exchanger; the outlet line of this heat exchanger being connected to a bypass line which in turn is connected to the heat exchanger inlet pipe in the upper bell of the upflow regulator member in the tank, the heat exchanger outlet line communicating with the feed water directly to the steam space.

In a further embodiment, to prevent preheating of the feed water supplied to the tank, a baffle is directed downwardly, opening in the upper bell of the upflow flow regulator member, having a side wall and a lateral side wall of the tank and , and which, in the upper part of the baffle bell, has steam passages in the steam chamber, preferably extending sideways. In this case, it may be advantageous if the upper part of the deflector bell is conical or pyramidal and the lower edge extends in the region of the lower part of the upper bell.

The fluid level control device of the present invention serves to control the fluid level in condensate recovery vessels and is also useful in the apparatus of the invention. The point is that it has at least two vapor-cushion liquid transfer tanks, one of which has a condensate feed line flowing into the liquid space of the vapor cushion transfer vessel, and out of which the condensate is discharged into the condensate recovery tank and the other is a steam cushion a conduit for drainage of condensate is discharged and a condensate drainage conduit for discharging cooled condensate from the system; working steam lines containing valves into the steam compartment of the vapor cushioning fluid tanks and exits lines or fittings containing the pressure relief and venting valves, while the working steam control valves are connected to the fluid level sensors in the tanks, e.g. integrated liquid level sensors - eg via electrical line - they are operatively connected to a valve installed in the condensate drain line. In a fluid level control device as defined above, a vapor-cushion liquid lift tank on the inlet control side is provided with a pressure relief-vent valve with a time switch, e.g. it is connected to a timer and is operatively connected to the level sensors in the tank, preferably by means of an electric cable. According to another preferred feature of the invention, the vapor-cushion fluid transfer tank pressure relief vent valve on the flow control side is operatively connected to the valve in the cooled condensate discharge line, preferably via an electric line, and is connected to a time switch such as a time switch. It may be expedient for the condensate feed lines to end up in a common condensate manifold, which is connected by a non-return valve conduit to the liquid space of the inlet control-side steam cushioning liquid reservoir and a condensate-free condensation condenser outlet outlet from this vessel.

The invention will now be described in more detail with reference to the accompanying drawings, which include some preferred embodiments of the apparatus.

1 is a schematic vertical sectional view of a base type of the apparatus of the invention;

Fig. 2 is a view similar to Fig. 1 but so-called. an example of an internal heat exchanger is shown;

Figure 3 shows an exterior heat exchanger embodiment of the apparatus;

Figure 4 illustrates a device having a double internal heat exchanger where it is possible to utilize occasional steam in a closed space above the liquid level of the container;

Figure 5 is a view similar to Figure 4 but having a dual external heat exchanger;

Figure 6 illustrates an exemplary embodiment having an inner receptacle divided by an open separation plate and internal heat exchangers;

Figure 7 is a view similar to Figure 6, but with an external heat exchanger;

Figure 8 shows a further embodiment of the apparatus on a larger scale and including arrows indicating flow conditions;

Figure 9 is a further embodiment similar to that of Figure 1;

Fig. 10 is a schematic vertical sectional view of another embodiment which also allows the supply of boiler feed water and heating of the unit with its own heat;

Fig. 11 shows a device similar to Fig. 10, except that the replacement feed water is heated from an internal and, if necessary, external source;

the apparatus of FIG. 12 is similar to that of FIGS. 10 and 11, however, the preheating of the backup feed water is eliminated;

Figure 13 illustrates a fluid level control device for use with the apparatus of the present invention.

As shown in Figure 1, the apparatus has a stationary cylindrical container 1 which is closed at the top and bottom by an embossed lid or bottom. During operation, the container has a v surface (v = kj> k ₂ ) 2 liquid space, above which a vapor space 3 is formed, which is highlighted by vertical shading. The reservoir 1 has a float flow regulator 4, all of which has a downwardly opening lower bell 10, an upwardly opening upper bell 12 and a central riser 11 coaxial with the cylindrical container 1. The bells 10, 12, which are also cylindrical in shape, are spaced about the same distance from the inner surface of the side wall of the container 1, i.e., between the bells and the container, there is an annular gap 13 at the top and bottom. The apparatus also includes a fluid level control device 5 having fluid level sensors kj, k ₂ , which of course function as level switches, and a transfer pump 15 connected to a conduit drainage conduit 16 from the bottom of the container, e.g. in operation with the fluid level sensors. A vapor line 6 exits the vapor space 3 into which a vapor pressure reducer 7 is inserted. The safety valve 8 is also connected to the steam chamber 3. In the upper bell 12, a heat recovery heat exchanger 9 is provided for extracting heat from the tank 1 in another system, with an inlet conduit for the medium to be heated, usually water, and an outlet conduit for supplying domestic hot water (not shown) , 9b. Condensate feed line 17 terminates in lower bell 10, to which condensate collection conduits 18,19 and 20 of various pressure levels and / or temperatures are connected outside the container 1; each comprising a non-return valve 18a, 19a and 20, respectively.

The height H of the container 1 of the apparatus is generally about three to ten times the diameter of D ₂ ; the latter has a specific value of between 1000 and 2500 mm and consequently the container height H is between 3000 and 25000 mm. Its width is 0.025 - 0.05 times the size of D ₂ , so it can range from 25 to 125 mm, and its value - the bell diameter - is Di - D? - 2a, which means that generally D ₂ = 950 - 2250 mm. The bell height m is 1 / 6-1 / 30th of the tank height H, generally 500-1000 mm, while the length of the riser pipe 11 is at least three times the value of m, practically 1500 - 15000 mm and its diameter d 0.08 to 0.1 times the diameter of the D ₂ region, generally 80 to 250 mm.

The apparatus of Fig. 1 operates as follows: Condensate collecting conduits 18-20 through conduits 18-20, for example from the steam heating system of a boiler house, have different temperatures, but in all cases are expected to exceed 100 ° C, through conduit 17 into lower bell 10 They are. The high temperature condensate in the tank 1 cannot mix with the liquid mass outside the space bordered by the lower bell 10 and flows in the riser 11 to the heat exchanger 9 in the upper bell 12 (arrow b) while the cooled lower water flows therefrom. The buoyancy flow regulator 4 thus produces an optimum degree of stratification in the fluid space of the container 1 due to gravity buoyancy based on the difference in gravity for heat recovery: the heat exchanger 9 always contacts the highest temperature condensate in the system 12; the condensate drain tube 16 exits, collecting the lowest temperature water which is returned to the boiler house (not shown) by the transfer pump 15. The low-temperature water supplied to the heat exchanger 9 via the inlet conduit 9a is then discharged through the outgoing conduit 9b as domestic hot water heated by condensation heat. The apparatus of Fig. 1 thus separates the return condensate by providing the highest parameters for heat exchange and the lowest temperature, thus the most favorable, for the return; the internal circulation in the container is illustrated by the arrows b, f mentioned above.

The condensate transfer pump 15, controlled by the fluid level control device 5, maintains a constant level within the specified switching levels k ₂ , while the protective vapor cushion formed in the steam space 3 by means of the vapor pressure reducer 7 ensures that the tank 1 does not degass. The high cylindrical container 1, even for the transport of high-temperature condensate, can provide the pump 15 with a favorable flow, thus providing a reliable protection against damaging cavitation on the pumps.

HU 199005 Β

Note that in each of the following figures, the flow direction of the fluids is indicated by arrows drawn on the conductors.

The exemplary embodiment shown in Figure 2, somewhat simplified, with the exclusion of certain structural elements, such as the water level regulator, is substantially the same as that of Figure 1, therefore, the structural elements already described are denoted by the reference numerals already used. Compared to the apparatus of Fig. 1, the use of a lower upwardly opening shade bell 21 which surrounds the lower bell 10 is a difference. The annular gap 13a between the shield bell 21 and the wall of the container 1, and the annular gap between the shield bell and the lower bell 13 are also designated 13b. Ei, these _two values are constants, i.e., the cylindrical shield bell 21 concentric with the container 1, 10 and 12 with bell and the lift tube 11 is situated. The slots 13a, 13b may have the same width as the slots 13 shown in FIG. The upper edge of the shielding bell 21 extends g above the top (cover) of the lower bell 10. Note, however, that in Figure 2 and in the other figures, the upper wall (top) of the bottom bell from which the all-ramp extends, and the bottom (bottom) of the upper bell 12, where the all-in raft extends, are shown as horizontal plates, but it goes without saying that these walls can be of any shape, such as curved (convex or concave). Thus, when talking about the shield bell 21 extending over the top of the lower bell 10, this is understood to mean the point at which the riser extends out of the cover of the lower bell.

With the use of the shield bell 21, it is possible to reliably prevent drainage of condensate through conduit 16 only from the cold zone of the fluid compartment 2 (arrows f), since the inner bellows 10 is closed from below by the bell 21 and prevents hot and cold mixing in the tank space below the bottom 10 bells. Part of the cooled water flows according to the arrows f _t into the lower bell 10 and mixes with the hot condensate supplied.

The embodiment of Fig. 3 differs from that of Fig. 2 in that an external heat exchanger 22 is provided for utilizing the heat content of the maximum temperature of the water stratified in the upper bell 12. The conduit 22a extending from the upper bell 12, which includes a circulation pump 23, extends into the space of the heat exchanger 22 from which the outlet conduit 22b is inserted into the liquid space 2 of the container 1 between the lower bell 10 and the upper bell 12. On the other side of the heat exchanger, conduit 24a is used for introducing the medium to be heated, usually water, and conduit 24b for discharging heated domestic hot water.

The apparatus of FIG. 4 differs from that of FIG. 2 in that a vapor recovery heat exchanger 25 is also provided in the steam space 3 of the container 1, the inlet and outlet lines of which are designated 25a. As has already been mentioned with reference to Fig. 1, the parameters of the condensate discharged through the condensate collecting ducts 18, 19 and 20 to the condensate feed line 17 are generally variable, so that the steam space 3 is filled with boiling steam as condensates above 100 ° C. Thus, not only the heat exchanger 9 but also the heat exchanger 25 provides the domestic hot water heated by condensed heat with the apparatus of Figure 4.

The apparatus of Fig. 5 is also suitable for utilizing both condensate arriving via condensate feed line 17 and the cavity steam collected in the steam space 3; external heat exchangers 22, 26 are used here. The heat exchanger 22 a

3 is connected to the tank 1, while the convection steam line 27 exits the steam space 3 through one of the space 26 of the heat exchanger and the line 28 containing the condensate drainage vessel 29 discharged therefrom into the condensate supply line 17, 20 wires entry point and

I tank between sections. A non-return valve 28a is provided in the conduit 28 between the branch junction of the conduit 217 and the condensate collecting vessel 29. In the other space of the heat exchanger 26, the outgoing line 24b of the heat exchanger 22 terminates and from there the line 30 exits. In this case too, the condenser operates at a temperature above 100 ° C from the bottom bell 10 under the

In a riser II (riser) they flow into the inside of the upper bell 12, from where they are circulated by the circulation pump 23 to the heat exchanger 22, from where the cooled water is returned to the liquid space 2 of the tank. The heated water in the heat exchanger 22 flows to the heat exchanger 26 where it is further heated by the steam leaving the steam space 3 and finally the domestic hot water is discharged through the conduit 30 to the consumer (not shown). The cooled steam is condensed in the heat exchanger 26 and returned to the tank 1 via the condensate collecting vessel 29 and the conduit 17.

Note that Figs. The upper bell may have an external heat exchanger, an internal heat exchanger in the steam space, or vice versa.

If the temperature of the condensate discharged through the conduit 16 is to be below the usual 70-90 ° C, the apparatus of FIG. 6 may be used, which differs from that of FIG. 4 in that a cooling space 33 is provided in which is separated from the remainder of the liquid space 2 of the container 1 by an open baffle plate 31 having a central opening 32. A cooling heat exchanger 34 is incorporated in the cooling space 33, the refrigerant supply inlet line 34a and the heated refrigerant outlet outlet line being designated 34b.

The open baffle plate 31 prevents so-called fluid masses between the individual compartments at different temperatures. free stream 61

At the same time, it allows the higher temperature water in the liquid compartment 2 above the open separation plate 31 to cool the lower temperature stream through the heat exchanger 34. Reverse water movement is not possible because of the downward flow caused by the pump 15 and the specific gravity difference due to the temperature difference between the water bodies.

Operation of the equipment of Figure 6 a

4 differs from that of Fig. 4 in that the heat exchanger 34 cools the condensate exiting the tank 1 through the conduit 16 to the desired temperature in the cooling chamber 33. The heated water discharged through conduit 34b can be utilized in other systems as domestic hot water.

In the apparatus of Fig. 7, the task of post-cooling the outgoing condensate water was solved by means of an external heat exchanger 35 having a conduit 37 leaving the tank 1 from the upper part of its cooling space 33 formed by an open separation plate 31 while the inlet conduit 38 of the heat exchanger refrigerant 35 extends to the bottom of the refrigerator compartment 33, preferably directly above the outlet of the conduit 16. Otherwise, Figure 7 is a solution similar to the embodiment of Figure 5, therefore, the structural elements already described therein are denoted by the reference numerals already used. The coolant, usually cold water, is supplied to the heat exchanger 35 via the conduit 36 on the outside, while the warmed water is supplied to the heat exchanger 22 via conduit 24a. The apparatus of Fig. 7, except for the condensate cooling, operates in the same manner as that of Fig. 5, and the cooling is effected such that the hot condensate entering the refrigerator 33 through the orifice 32, or part thereof, it conveys through the heat exchanger to the outlet of the outlet conduit 16. The mixed condensed condensate has reduced the temperature of the liquid entering the conduit 16 to the desired level, e.g. when using cold water at 15 'C as the refrigerant, the temperature of the condensate can be cooled to below 30 to 40' C depending on the mass flow rate of the refrigerant.

In all of the examples described above, the imaginary horizontal plane laid through the point B of the hot condensate can be considered as the separation plane of the flows in the tank 1; a gravitational hot ramp while the sub-plane is considered as a cold exit. The heat recovery heat exchangers are called vertical heat exchangers. are considered to be essential stages of heat energy transport. Heat exchangers, as described above, can simultaneously utilize both the heat of the condensate and the liquid heat of the condensate within the same container.

Fig. 8 differs from Fig. 6 only in that there is no useful heat exchanger for the keg steam content, but in the larger scale the flow conditions are more clearly visible. Due to the incorporation of the shielding bell 21, as already mentioned, the condensate drainage through conduit 16 can effectively leave condensate already cooled by heat exchangers 9 and 34 from the container 1, in particular to the part of height 1 bounded by the conceptual planes s _2. outside the shade bell 21.

However, the condensable water discharged through the conduit 17, when taken through the conduit 16, is congested within the shield bell 21 (including, of course, the inner bellows 10 of the lower bell member 10) and continues in the ridge 11, gravity upstream; at the same time, a certain amount of water is mixed from the portion of the liquid space 2 above the shielding bell 21 in accordance _with arrows f _t . However, the shielding bell, despite the fact that the liquid phases at different temperatures are in the same space, i.e. the interior of the container 1, greatly facilitates their separation. Incorporation of shield bell 21 results in condensate fed through conduit 17 not readily discharged through aperture 32 of open separator plate 31 in the direction of outlet conduit 16, but forcing the liquid from bottom bell 10 to flow, but at least most of it. In other words, the shielding bell 21 is reassuring to ensure that the condensate to be recycled is gravitationally upward and the coolant cooled by the heat exchanger 9 to flow unhindered to the bottom of the container without short-circuiting.

The embodiment shown in Figure 9 differs from that of Figure 4 in that a tray 40 is placed under the heat exchanger 25 in the vapor space 3, above the liquid level y, from which two droplets 41, 42 extend. These drop pipes 41, 42 extend into this riser around the lower third of the riser 11 of the riser 4. This design results in a better utilization of the heat content of the hot condensate water generated during the operation of the heat exchanger 25 and the best possible flow conditions within the tank 1. Namely, if the condensate of the heat exchanger 25 falls directly on the liquid surface v in the vapor space 3, its contact with the heat exchanger 9 is not maximal, that is it participates in the gravitational flow in the tank 1 without utilizing part of its heat and effectively raising its temperature. Flow towards bottom of 1 tank.

9, the flow of condensate from the heat exchanger 25 is controlled to provide optimum utilization of its heat content. In fact, the condensate trapped in the tray 40 is provided by the drop pipes 41, 42 into the riser 11, i.e. the heat exchanger 9 in the upper bell Ϊ2 with respect to the upstream direction indicated by the arrow b.

-7EN 199005 B is placed in accordance with the arrows i and this condenser is mixed with the upwardly flowing high-condensate water at the K point to the heat exchanger 9. Thus, the condenser of the heat exchanger 25 participates in the heat cycle as well as in the heat exchange so that its heat content is maximally utilized.

In principle, a fall pipe is enough to produce the intended effect. Preferably, the fall pipe (s) extends into this riser in the region of less than half the height h of the all riser.

Use of tray 40 and drop pipes 41, 42 a

6 and all embodiments where a heat-exchanging heat exchanger is located in the vapor space of the container. Incidentally, reference numerals and symbols used previously in Figure 9 are applied mutatis mutandis.

The apparatus according to the invention, or the closed condensation tank, can be used either in a boiler cycle or in a boiler plant located further away from the boiler house. When installing the unit in a boiler room cycle, in addition to receiving the returning condensates, you must be able to receive boiler auxiliary feedwater as well, because in this case you must receive boiler auxiliary feedwater, because in this case it is not only a condensate tank but a can also function. However, when introducing auxiliary feedwater, care must be taken that the gravity flow characteristic of the smooth operation of the tank is not disturbed by the auxiliary feedwater being introduced. Replacement feed water can be fed into the tank either without preheating or preheating. Due to the closed system, the replacement feed water is preheated after removal of most of the dissolved O ₂ , CO _{2 in} a so-called after the pre-degassing stage, it is advisable to introduce it into the closed condensate tank, since the high-O ₂ , CO ₂ -contained feed water would contaminate the entire amount of condensate. Pre-degassing at the top of the tank, feed! place domain. To overcome this, the device according to the invention can be designed in various variants.

The apparatus of FIG. 10, which is similar in structure to the exemplary embodiment described hereinabove and is therefore denoted by the reference numerals already used, supplies the auxiliary feed water through line 47 and passes through the water softener 48 and line 34a. to the heat exchanger 34. As the temperature of the condensate water in the refrigeration chamber 33 exceeds the temperature of the feed water supplied, the latter is already preheated to the heat exchanger 34 and then continues in the heat exchanger 9, where the feed water flows through the conduits 34b, 34c and 9a. The supply of preheated supplementary feed water to the steam space 3, which also functions as a dewatering space, is effected through conduits 9b and 49 as well as via the nozzle head 43. In the event that the heat supplied from the heat exchangers 34 and 9 would not be sufficient for preheating, fresh steam may be fed to the steam space 3 via a steam line containing the vapor pressure reducer 7, whereby approx. The 0.23 bar pressurized steam cushion can be used to reheat the water entering the nozzle head 43. Thus, by providing the physical condition of this introduced feedwater for pre-degassing, increasing the surface of the water at a suitable steam temperature and pressure, and ensuring that the dissolved but precipitated O ₂ , CO ₂ is removed from the tank, A conduit 44 or conduit is provided - the replacement feed water may be mixed in a degassed form with the condensates in the container. The preheated and de-degassed replacement feed water falling into the tray 40 mixes downwardly through the downpipes 41,42 and meets j at the point K and merges with the conduit 17 flowing upwardly through the riser 11 of the riser 4. Water fed into the steam space 3 is provided with a downward and inwardly sloping baffle plate 51 for guiding the tray 40. From the tank 1, the cooled condensates pass through line 16 and pump 15 through the flow control valve 45 into line 46 and from there into a degassing feed tank (not shown).

It follows from the above that the heat content of the condensates fed through line 17 was used to preheat the fresh (cold) feedwater and the heat needed for preheating was replaced by fresh steam supplied through line 6. Obviously, it is also possible to have a state of operation in which the proper vapor pressure in the steam space 3 can be achieved without additional steam introduction, only by the amount of heat obtained from the heat exchangers 34 and 9. It is also obvious that the tray 40 and the drain pipes 41, 42 are not necessarily required to preheat the replacement feed water, but these structures (parts increase the efficiency of preheating).

The embodiment of Figure 11 differs from that of Figure 10 in that only fresh steam fed through line 6 is used to preheat fresh (cold) feedwater supplied through line 49 and heat exchangers 34 and 9 from tank 1 are used. and through the 9b in another heat take-off cycle,

8, such as heating, domestic hot water preheating and the like. In the vapor space 3, as in the embodiment of Fig. 10, an inward and downwardly sloping trap conical plate is secured which directs the liquid from the side wall to the tray 40. THE

In addition, the reference numerals of FIG. 10 are used mutatis mutandis in FIG.

In practice, there may also be cases where the cold supplemental feed water introduced into the tank 1 is not required to be preheated for some reason, for example because the tank has too much excess heat. To solve this problem, e.g. The apparatus of Fig. 12 is suitable, having the same basic structure as the solution of Fig. 2, therefore, the structural elements already explained therein are designated by the reference numerals already used-8HU 199005 Β. In this case, the nozzle 43 will not meet the heat exchanger 9 due to the presence of a deflector bell 50, which is inverted downwardly through the orifice of water sprayed into the steam space 3, due to the presence of a deflection bell 50. There is, of course, a gap between the outside of the deflector bell 50 and the inner surface of the container 1. There are openings 50a in the upper part of the deflector bell 50, through which the vapor can pass from the liquid surface v to the vapor space 3 (arrows 1 o). Supply feed water 10 flows downwardly between the inner wall of the container and the outer surface of the deflector bell 50 in accordance with arrow p and mixes in the liquid space 2 with hot condensate there. The flow control valve 45, which is incorporated in the conduit 46 leading to the degassing feed tank (not shown) 15, is operatively connected to the fluid level control structure 5 via an electrical conduit 52. During operation of the apparatus of Fig. 12, adequate preheating for de-gassing 20 may be effected by vaporization (arrows o) from the liquid level mirror v of the container 1. If surplus heat is always available safely, there is no need to introduce fresh steam, but if it is doubtful, it is expedient to use a fresh steam supply for steam supply to the vapor space above the liquid mirror, i.e. steam 3, provided with a steam line 6. 30

If water (auxiliary feed water) is introduced into the tank 1 of any of the embodiments of the apparatus according to the invention according to Figs. However, when preheating is used, the heat content of the water in the tank increases, which may not always be the goal. If the tank has too much overheating capacity, it would be advisable to reduce it and heat the supplied feed water without preheating only with the 4Q heat content of the tank or reduce the heat content of the tank.

When introducing fresh auxiliary feedwater, it is essential to provide the conditions under which the auxiliary feedwater 45 can be discharged as quickly as possible prior to mixing the dissolved O ₂ , CO _{2 with} the condensate in the tank, thereby rendering the auxiliary feedwater drained. Depending on the temperature of the return condensates 50, they still have usable enthalpy, and for what purpose they can be used, options 10-12 can be selected. is the most favorable of the options shown in Figs.

A fresh primary steam injection is required only to ensure optimal a2 degassing under all conditions.

Thus, on the one hand, the apparatus according to the invention can be operated economically and the degassing feed tank can also be relieved. 60

There are basically two ways to optimally utilize the heat content of the condensate stored in the apparatus of the invention: namely, to preheat fresh cold replacement water (e.g., Fig. 10) * or to supply it to an external consumer, e.g. 65 for domestic hot water or for heating. The enthalpy surplus is, for example, a two-step liquid heat recovery; steamed with spit; and a combination of these methods can be utilized or recovered.

Ensuring the smooth flow of flows in closed condensate tanks is an essential requirement. To this end, condensates should preferably be introduced into the tank as smoothly as possible, and be careful to keep the water level and to remove excess condensate as evenly as possible. The control used to fill the tank is called the flow control, and the control used to empty is called the flow control.

The operation of the device according to the invention is more efficient the more independent it is from external disturbances. The condensate collection center - in the unit - often receives condensates from multiple heat centers at irregular intervals, with varying pressures and temperatures, in a shockless, uncontrolled manner, which can disrupt the operation of the unit.

The capacity of the smallest pumps for condensate transport is also usually several times higher than that required, and this may cause problems due to the larger quantities transported in one unit of time. Therefore, in many cases, the inlet and outlet control of the device of the present invention as a function of the fluid level in the tank may be better solved by the water level control device shown in Figure 13 rather than by the pump control of Figure 1. The operation of this structure is based on the use of working steam and steam cushion and the volume displacement principle, and is made of liquid-lifting vessels made of fluid-free vessels operating at high condensation temperatures even at high condensation temperatures. the flow-in-flow level control system can be used to stabilize the plant positively. With the help of the water level control device of Fig. 13, a near continuous flow and flow can be achieved and the use of high-value pumps or fittings is eliminated.

The container 1 shown in FIG. 13 is substantially the same as the embodiment of FIG. 2: In its water space 2 located below its steam space 3, there is a buoyancy flow regulator 4 formed by an upper bell 12, a lower bell 10, and The lower bell 10 is surrounded by a shield bell 21 and the upper bell 12 has a heat exchanger 9. Conduit 17 is provided for the introduction of condensation into the lower bell 10.

The water level regulating structure is an essential part of the vapor-cushion fluid transfer tanks 61, 62. The working steam line 59 is enclosed in the reservoir 62 and the working steam line 60 branched into the reservoir 16, into the steam space 62a, 61a of these reservoirs. Prior to insertion, the working steam line 60 is fitted with 63 valves and the working steam line 590 with valve 76, which are preferably solenoid valves.

HU 199005 Β

From the steam chamber 61a of the reservoir 61, a line 64 or a nozzle 64 comprising a valve 65; and from the steam chamber 62a of the tank 62, the conduit 77 or valve nozzle 77 extends into the section. These conduits 64, 67 and their associated valves are used to depressurize the tanks 61, 62. for ventilation. Again, the valves 65, 78 are preferably solenoid valves.

Conduits for condensation from various locations are designated by reference numerals 18 through 20, as shown in Figure 1; these lines include check valves 18a-20a. The conduits 18-20 to 67 condensate collectors - e.g. condensate collecting pipe - from which the conduit 68 containing the non-return valve 69 exits and flows into the lower part of the vapor-cushioned fluid reservoir 61, i.e. the liquid space 61b, from which the condensate-feeding conduit 17 is discharged into the container 1 . From the foregoing, it will be appreciated that the collected condensates are fed into the container 1 via the vapor cushion liquid transfer container 61 which is part of the fluid level control system. From the condensate collector 67, an outlet line 70 exits which closures 71, e.g. contains a valve. Through line 70, excess condensate from condensate collector 67 is e.g. channel (not shown).

A conduit 16 discharging from the bottom of the container 1 for discharging cooled condensate, preferably containing a closure 53, such as a valve, immediately below the outlet, terminates in the lower part of the vapor cushioning vessel 62, i.e. the fluid space 62b. Before the insertion point, a non-return valve 54 is installed in the conduit 16. From the liquid space 62b of the reservoir 62, a conduit 57 is provided for discharging the cooled condensates out of the system, into which a valve 58 (e.g. a solenoid valve) is inserted, preferably immediately after the outlet. A drain line 55 also exits the bottom of the container 62, which closes the closure assembly 57, e.g. contains a valve. Likewise, the container 61 is provided with a discharge line 82 which is provided with a shut-off valve 83. Through the drain lines 55 and 82, it can be drained into a drain (not shown) which is unnecessary (eg operating).

Liquid level sensors 81 and 84 are incorporated in the upper part of the container ₁ to detect the liquid level kj and k ₂ that may be formed in the container. Liquid level sensors 74 and 75 are associated with fluid levels kj and k _{6 in} the vapor cushioning tank 61, respectively, for liquid levels ₃ and K, or liquid level sensors 72.73.

A k _b k ₂ ; a kj, Kt. and the liquid volumes defined by the liquid level differences ks and k ₆ are conveniently the same.

The fluid level control device of Figure 13 operates as follows:

when the condensate flowing through the conduit 68 into the tank 61 reaches the upper liquid level kj, the fluid level sensor, which of course also functions as a level switch, opens the valve 63 of the working steam, and the working steam flowing into the tank holds the water from the lower Kt. It is pushed through a path 17 into the tank 1. When the liquid level Kt is reached, the liquid level sensor 73 (and level switch) closes the work valve 63 and simultaneously opens the pressure relief and vent valve 65 in the line 64, which can be set with a time switch, for example, for a period of time, e.g. . After the valve 65 closes, there is no back pressure in the reservoir 61, so that the reservoir is able to receive (suck in) condensation through the conduit 68 and the processes described above may be repeated.

When the volume of liquid corresponding to the difference between the liquid levels k3 and Kt flows from the tank 61 into the condensate recovery tank 1 through the conduit 61, the excess liquid flow through the conduit 16 immediately causes the liquid to flow through the condensate k ₆ ; the valves 76, 78 and 58 are now closed. When the rising fluid in reservoir 62 reaches liquid level K5, the liquid level sensor switch 75 opens the steam valve 76 and simultaneously valve 58 so that the steam coming from the working steam line 59 pushes out the liquid 62 from the reservoir 62. previously sucked in. " When the sinking liquid mirror reaches fluid level ₆ , the fluid level sensor switch 75 closes valves 76 and 58 and opens valve 78 in venting and depressurizing line 77. The latter has a timer that allows you to set a time for a specific time, eg. Valve 78 can be kept open for 5 seconds.

Due to the above-described operation of the two tanks 61, 62, the condensate recovery tank 1 can maintain a nearly constant fluid level.

The operation of the vapor cushioning fluid transfer tank 62 is also controlled by the fluid level sensors 81, 84 in the condensate recovery tank 1. For the smooth operation of the container 1, the fluid level therein is shown in Figure 13 and k ₂ between the liquid levels indicated by reference letters. When the rising liquid mirror reaches the liquid level kj, the fluid transport process described above in tank 62 is started because the liquid level sensor switch 81 opens valve 76 and working steam can flow from the line 59 to the liquid level kj. However, when the sinking liquid mirror in tank 1 reaches level k ₂ , the fluid level sensor switch 84 closes valves 58 and 76 so that tank 62 can be filled with liquid. When the fluid level in the reservoir 62 reaches the level, the fluid level control switch 74 opens the valves 76 and 58, and via the line 59, working steam enters the reservoir 62 and the above-described processes are repeated.

The control system detailed above - the container 1 is a substantially constant fluid10

With a level of -101 - eliminates the risk of developing a stable container 1

Condensation arrives at the system to control eavitation flows.

An advantage of the present invention is that it allows, with maximum structural efficiency, the recovery of the heat content of condensed water and its rational use in, for example, domestic hot water production, and cooling of the condensation water to a temperature of 30-40 ° C or less. The stationary cylindrical container offers an optimum solution, both statically and functionally and dynamically. Condensers of various temperature and / or pressure levels can be fed into the unit via a common conduit, without the need for separate tanks, chambers, or complex valve systems to receive these condensates, as in the presently known condensate collection systems. Thus, the heat content of the condensate water can be optimally utilized by the present invention. The fluid level control device of the present invention makes it possible to maintain a substantially constant liquid level in the condensate recovery tank and to maintain the smooth gravity flow conditions in the tank.

The invention is, of course, not limited to the embodiments detailed above, but may be practiced in many ways within the scope of the claims.

Claims (24)

An apparatus for utilizing the heat content of condensate water, comprising a container, preferably a cylindrical form, a conduit for supplying hot condensate to the container and removing cooled condensate from the container, and a heat exchanger disposed in the container (1). an upstream flow regulator member (4) having an open lower bell (10), an upwardly open upper bell (12) and a riser (11) connecting each of these bells (10, 12), the upper bell (12) of which has condensation water a heat exchanger (9) for utilizing its heat content, or / and a conduit (22a) containing a circulation pump (23a) from the upper bell (12) to an external heat exchanger (22) from which the condensed water is cooled. ) into the fluid space (2) below the upper bell (12) 2b) protruding out; a conduit (17) for supplying condensed water, preferably hot, containing the heat to be recessed to the lower bell (10); and a gap (13) of preferably constant width (a) between the outer surface of the bells (10,12) and the inner surface of the container (1). (Els. 6/11/1984) Apparatus according to Claim 1, characterized in that the container (1) has a lower liquid space (2), the lower part of which, preferably from the lowest point of the container (1), discharges a condensate drainage conduit into which in the case - a lifting pump (15) is installed; and from the upper steam space (3) of the container (1), a steam line (6), optionally containing a vapor pressure relief device (7), protrudes, preferably from the highest point of the container (1). (Ele. 11.11.1984) Apparatus according to claim 1 or 2, characterized in that the container (1) has a liquid level control device (5) which is provided with liquid level sensors ( _klt k ₂ ) and by means thereof, for example, by means of an electric line (14). has an operable connection pump (15) incorporated in the cooled condensate drain line (16). (Els. 6/11/1984) Apparatus according to any one of claims 1 to 3, characterized in that it has a lower and laterally closed, open upper shielding bell (21) surrounding the lower bell (10), which is both from the side wall of the container (1) and the lower bell (10). ) is spaced apart (e _b e ₂ ) from the outside thereof, forming a gap (13a, 13b) therewith, the width (e _b e ₂ ) of the gaps (13a, 13b) being preferably constant and the upper edge of the shielding bell (21) spaced (g) above the top of the lower bell (10). (Els. 6/11/1984) 5. Apparatus according to any one of claims 1 to 3, characterized in that the container (1), the lower and upper bell (10, 12) of the runner flow member (4) and the riser (11) and the shield bell (10) surrounding the lower bell (10). 21) are in the form of a stationary hcngcr and are concentric with the container (l). (Els. 6/11/1984) Apparatus according to claim 5, characterized in that the height (H) of the container (1) is about 3 to 10 times the diameter (D ₂ ), preferably about 3000 to 25000 mm; width of the gap (13, 13a, 13b) between the lower and upper bell (10, 12) and the shield bell (21) and the container side (l) and the gap (13, 13a, 13b) between the shield bell (21) and the first bell (10) the e _2, e _{2) of} the diameter (D ₂₎ of the container (1) about 0.025 to 0.05 times, preferably about 25 to 125 mm; the height (m) of the lower and upper bell (10, 12) being about 1/6 to 1 / 30th of the height of the container (1), preferably about 500 to 1000 mm; and the projection (g) of the upper edge of the screening bell (21) above the top of the lower bell (10) is up to about twice the height of the latter (m); the diameter (d) of the riser (11) is about 0.080 to 0.1 times the diameter (D ₂ ) of the container (1), preferably about 80 to 250 mm, and its length (h) is the lower and upper bell (10, 12); ) at least three times its height () m). (Els. 6/11/1984) 7. Apparatus according to any one of claims 1 to 4, characterized in that it has an internal heat exchanger (25) or / and an external heat exchanger (26) for utilizing the heat content of the boiling liquor located in the steam space (3) of the container (1). (Els. 6/11/1984) 8. Apparatus according to any one of the preceding claims, characterized in that it is formed at the bottom of the container (1), below the lower bell (10), and -111 HU 199005 van has a cooling space (33) separated from the remainder of the interior of the container (1) by an open separation plate (31), preferably having a central opening (32), in which a heat exchanger (34) is disposed, or preferably, a conduit (37) for circulating a condensate water to the lower part of the cooling space (33), which is provided in the vicinity of the opening (32) of the open separating plate (31) to an external cooling heat exchanger (35). preferably, a conduit (38) for discharging the condensate drain (16) to the outlet. (Els. 6/11/1984) Apparatus according to claim 8, characterized in that the open separating plate (31) is horizontal or substantially horizontal, has a diameter equal to the inside diameter (D ₂ ) of the stationary cylindrical container (1) and a diameter (dj of the plate) ₂ ) 0.08 to 0.1 times, preferably about 80 to 250 mm. Apparatus according to any one of claims 7 to 9, characterized in that a tray (40) for receiving condensate from the heat exchanger (25) is disposed beneath the heat exchanger (25) in the vapor space (25), above the liquid level (v). Preferably, a plurality of downpipes (41,42) protrude from the downpipe (11) into the uppipe (11) of the upflow flow regulator member (4). (Els. 2/24/1988) Apparatus according to claim 10, characterized in that the fall pipe (s) (41, 42) extends below the middle region of the riser (11), preferably around its lower third, into the riser (11). (Els. 24.12.1988.) 12. Apparatus according to any one of claims 1 to 3, characterized in that it has a conduit (49) for supplying boiler feed water, which preferably flows into the steam space of the tank (1). (Els. 2/24/1988) Apparatus according to claim 12, characterized in that a nozzle (43) suitable for feeding water atomisers is connected to the end of the auxiliary feed water supply line located in its steam compartment (3). (Els. 2/24/1988) Apparatus according to claim 12 or 13, characterized in that the conduit (16) exiting the lower part of the reservoir (1), comprising a lifting pump (15), is provided with a flow control valve (45) into the degassing feed tank. is connected to a drain line (46). (Els. 2/24/1988) 15. A 12-14. Apparatus according to any one of claims 1 to 3, characterized in that a gas outlet (44) or a nozzle containing a closing device (44a) emerges from the steam compartment (3). (Els. 2/24/1988) 16. A 12-15. Apparatus according to any one of claims 1 to 5, characterized in that the supply water (49) for supplying the auxiliary feed water to the steam space (3) is connected to one or more heat exchangers (34; 9) in the tank (1), or / and a steam conduit (6) which enters the vapor space (3), preferably comprising a vapor pressure reducer (7). (Els. 2/24/1988) Apparatus according to Claim 16, characterized in that a water softener (48) is provided in the conduit (47) for supplying the auxiliary water to the tank (1). (Els. 2/24/1988) Apparatus according to claim 16 or 17, characterized in that the supply line (47) for the supply water to the tank (1) is separated by a separating plate (47) open in the lower part of the tank (1) from the remainder of the interior of the tank (1). 31) it enters a heat exchanger (34) located in an isolated space; the outlet line (34b) of said heat exchanger (34) being connected to a jumper line (34c) which in turn connects to the inlet line (9a) of the heat exchanger (9) in the upper bell (12) of the ramp member (4) in the tank (1), the outlet conduit (9b) of the heat exchanger (9) being connected to the conduit feeding the replacement feed water directly to the steam space (3). (Els. 2/24/1988) 19. A 12-14. Apparatus according to any one of claims 1 to 3, characterized in that the baffle (50) is turned downwardly with the opening of the upper bell (12) of the buoyancy flow regulator member (4) in order to eliminate preheating of the feed water fed to the tank (1). fitting having a circumferential slot between the side wall and the side wall of the container (1) and the side wall of the upper bell (12), and having a deflection bellows (50a) in the upper portion of the bell in the steam space (3). (Els. 2/24/1988) Apparatus according to claim 19, characterized in that the upper part of the deflection bell (50) is conical or pyramidal and the lower edge extends in the region of the lower part of the upper bell (12). (Els. Aug 24, 1988) 21. Liquid level control device for condensate heat recovery vessels, in particular 1, Apparatus according to any one of claims 2 or 4 to 20, characterized in that there are at least two steam cushion transfer tanks (61, 62), one of which is provided with a condensate feed line (68) into the liquid space (61b) of the container; from there, the conduit drains into the condensate recovery tank (1), and the other steam cushion transfer vessel (62) flows into the liquid space (62b) of the condensate recovery tank (1) to drain the cooled condensate (16), and a conduit (57) for removing cooled condensate from the system; the working steam lines (59, 60) containing valves (63, 76) extending into the vapor space (shells, 62a) of the fluid transfer tanks (61, 62) and the lines (64, 77) comprising a pressure relief vent (65, 78); or stubs exit, the work steam control valves (63, 76) having fluid level (k3, k4; k5 k6) sensors (72, 73; 74, 75) built into the tanks (61, 62), for example on electrical lines (85, 86). ) - they are operationally connected and that liquid level (off, k2) sensors (81, 84) are integrated in the upper part of the condensate recovery tank (1) -121 HU 199005 Β - for example, via an electric wire (14) - operatively connected to a valve (58) provided in the condensate drain line (57). (Els. 2/24/1988) A device according to claim 21, characterized in that the pressure relief vent valve (65) of the fluid transfer tank (61) at the steam control side is connected to a time switch, such as a time switch, and - preferably via an electric line (85). is also operatively connected to the level sensors (72, 73) associated with the container (61). (Els. 2/24/1988) Device according to Claim 21 or 22, characterized in that the pressure relief vent valve (78) of the vapor cushion liquid transfer tank (62) on the flow control side comprises a valve (58) integrated in the cooled condensate discharge line (57). via a wire (80) in an operative connection and also connected to a timer such as a timer. (Els. 2/24/1988) Device according to any one of claims 21 to 23, characterized in that the condensate supply lines (18-20) end up in a common condensate collector (67) which is connected by a conduit (68) containing a non-return valve (69) to the flow control side vapor cushioning tank. With a fluid space (61), a conduit exiting from said reservoir (61), also containing a non-return valve (66), is directed to the lower bell (12) of the condensate recovery tank (1). (Els. 2/24/1988)