JPS59137703A - Fluid feeder - Google Patents

Abstract

(57) [Abstract] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a system for supplying water to a steam generation and distribution system that can be condensed into a replenisher or preparation liquid.

The present invention consists in particular of two phases, namely a gaseous phase (steam) and a liquid phase (condensate), and is particularly intended to be preferably substantially dry and at least to a large extent
with at least a partial recovery portion of the condensate discharged from the system by substantially free, i.e. natural gravity return flow;
At every point between the point at which the return flow is delivered and the point of supply of steam at working pressure, the temperature is at least approximately constant, i.e. approximately constant, i.e. approximately the same at every point in the entire circuit. and at least one evaporative boiler of a system for the generation, distribution and use of condensable steam through a closed circuit, at least a major part of which contains a dual fluid, providing pressure and pressure. The present invention also relates to a method of supplying at least one steam generator with periodically renewed, expandable or utilizable vaporizable liquid. This method, on the one hand, limits the liquid level in each boiler within a range of controlled values defined between two limits: an upper limit or feed water cut-off point and a lower limit or maximum feed water flow limit. on the other hand, in at least one external storage of the feed liquid, provided according to the measured or detected current fluctuations of by providing replenishment to each boiler from at least two replenishment liquid sources, each constituted and used simultaneously or separately, with said recovered condensate being reintroduced directly into the boiler. There is.

In this method, said direct reintroduction of condensate is carried out freely or continuously as the introduction of recovered condensate progresses, and said reintroduction is carried out in accordance with the actual detected physical state of affairs. and this is controlled by said liquid level and/or a finite current amount of condensate collected or present upstream, and said liquid level and/or said amount of condensate Mutual restraint due to tracking.

The discharged condensate is collected and stored at least temporarily in at least one main reservoir forming one of the replenishment liquid sources, after which the replenishment liquid (among its two components) (or a mixture of liquids) is re-introduced into each boiler by means of mechanical propulsion with automatic control, in which case said automatic control may for example It can be either of the floating on-off type, or of the progressive or modulating type, mutually constrained in relation to target liquid level or current volume and tracking.

The invention also applies to carrying out the above method in said apparatus, said apparatus being adapted to carry out said method in said apparatus, said apparatus being capable of carrying out said method via said at least one 9-way conduit with a power-driven pilot bonzo for all hydrostatic heads. a condensate discharge leading to at least one condensate recovery collector connected by at least one condensate direct reintroduction conduit to at least one water supply tank supplying fresh vaporizable liquid to said boiler; and at least one conduit network consisting of a return conduit, at least one main circulation propulsion member for discharging said condensate to said boiler, and an intervening between said collector and said direct reintroduction conduit. inserted and combined with the circulation propulsion member to form a main pumping station. There is at least one primary condensate storage buffer tank. Said circulation propulsion member may be, for example, a dynamically driven bonzo, preferably mounted in series with a downstream check valve, and preferably kept under static pressure by gravity water supply from said buffer tank. A gas submerged fluid injector is suitable.

In accordance with the improvements of the present invention, a structural acid is obtained which is functionally simple, structurally durable, and therefore requires less monitoring and maintenance costs, and which is relatively economical to fabricate and install;
and an improved, effective and highly economical system which ensures a high efficiency of energy, with the result that there is a significant gain in the use of power, fuel and other energy consumed, thereby significantly increasing the amount of waste available for rent. The purpose is to provide the benefits of reliable work processes and operations.

Next, the operation and effects of the present invention will be explained in more detail with reference to the drawings showing embodiments of the present invention.

The embodiment of FIG. 1 includes a vaporizable replenishment liquid (e.g. water) consisting of external fresh liquid coming from the feedwater storage section and/or condensate or condensate coming from the condensate storage tank.
1 shows a method and apparatus for refilling at least one boiler. This includes, as is known per se, before they are introduced into the boiler, after draining said boiler,
A device is provided for generally preheating the hot combustion gases J:f) and said replenishment liquid. The preheating creates an upward flow in the replenishment liquid that enters from below and exits from above.

FIG. 1 shows that the method described above provides a permanent escape of replenishment liquid that is fed from the condensate reservoir, part of which is not diverted, and has a relatively slow, possibly selectively controllable degree of continuous flow. All applications are shown in which a continuous flow of replenishment liquid is recovered in the form of a stream of water. said escape flow consists of already preheated make-up liquid flowing directly back into said condensate storage tank, and a storage portion of external feed liquid (feed water) is discharged directly into said condensate storage tank; The feed liquid is conveyed to the condensate storage tank and mixed into the current volume of storage liquid in a constrained tracking relationship and according to an automatically controlled intermittent flow rate.

Generally, the preheating is carried out in an installation, such as a boiler steam heating system, by at least one economizer in the form of a heat exchanger, through which the combustion gases of the boiler are passed after leaving the installation; Prior to introduction, the economizer operates as a water heating device by recovering the residual heat of the combustion gases or hot combustion products. The apparatus of the invention useful for carrying out the above-described method is primarily characterized in that the temperature and pressure are substantially constant everywhere and the same at all points in the apparatus except for pressure losses due to flow. Applicable to condensable steam generation and distribution systems, such systems equipped with economizers require some precautions.

The main thing is to keep the flow rate of water flowing through the boiler to a minimum, and to reject a certain amount of heat by the economizer, so that the economizer maintains the temperature of the water contained in the boiler and You will be passing relatively cold water through it. The embodiment according to FIG. 1 is of the type defined above, which is connected to a source of fresh water, for example with a float valve, controlled by the water level in the tank 10, and which is normally connected to a source of fresh water. It includes at least one water tank 10 connected by a conduit 69 that communicates with the surrounding atmosphere via a pore 16 or the like. At least one feed water supply conduit or supply conduit 11 starting from the tank 10 includes a power-driven pilot water pump 12 for sucking water with a hydrostatic head from the lower part of the tank 10 through the bottom of the tank. The pump is installed between the downstream separation valve 57 and the upstream separation valve 57', and is installed between the downstream separation valve 57 and the upstream separation valve 57', and passes through the downstream check valve 56, etc. Provides water supply. Here, the separation valve refers to a valve that shuts off the flow of fluid. The boiler 8 produces steam that can be condensed, which is passed through the main supply conduit 9 to a boiler (such as an ambient space heating lavator or heat exchanger) which absorbs heat by condensing the steam. The condensate thus produced is delivered to at least one steam-based device (not shown) which operates by exchanging heat, and the condensate thus produced is transported to at least one steam-based device (not shown) which operates by exchanging heat. At least one condensate recovery device leading to at least one condensate recovery device forming a primarily gravitational return conduit 15 opening into the upper part of one main buffer tank 14 (hereinafter the same). It is discharged via a single return conduit network. Above salary conduit 1
1 opens to the bottom of the buffer tank 14, which forms a common conduit 88 for the supply of the replenishment liquid and advantageously includes a separation valve 90, etc. at least one condensate direct reintroduction pipe 16'
It is connected to boiler 8 by.

Said conduit 16' is mounted in series between an upstream isolation valve 18 and a downstream isolation valve 21 and draws suction from the bottom of the buffer tank 14 under a hydrostatic head and preferably a check valve 20 or the like. It includes at least one power-driven pump 17, which advantageously provides water supply via the pump. In the common pipe line 88, near the date of intake into this boiler, preferably between the upstream separation valve 91 and the downstream separation valve 95, and preferably between the boiler 8 and the valve 46, this pipe is inserted. Road 88
It is convenient to arrange downstream check valves 96 and the like in the pipe line 88, and install one automatic control valve 46fj in series with the pipe line 88. The servo motor of the automatic valve 46 is connected to the remote control circuit 4
7 to a pilot member of a level detector or controller 67 associated with the boiler 8 . In front of the control valve 46, at least one economie f84 is inserted in series with the common conduit 88, and this economie f84 connects its intake and outlet to the common conduit 88. are mounted so as to be connected to an upstream or incoming section and a downstream or outgoing section, respectively.

The individual servo motors of the water pumps 12 are connected by remote control circuits 54b to buffer tanks 14 and associated liquid level detectors or liquid level controllers 5. The common lines 88 are , located in front of the automatic control valve 46 and the separation valve 91, at the branch point 40', the replenishment liquid source opens preferably at the top and is preferably substantially constant and selectively variable. By limiting the free cross-sectional area of the passageway with the openings that allow it to flow, the two replenishment liquid sources mentioned above can be connected via a branch conduit 39 forming an escape route, which includes a member 46 producing a high pressure drop. The branch point 40' is located behind the water outlet of the economie f84, and the branch conduit 69 is connected to one of the
The feed source, which is open at , is constituted by the main buffer tank 14 .

Isolation valves 90 and 9 upstream and downstream of economizer 84
In order to place the economizer 84 in an inoperable state by simultaneously shutting off the boiler 8 and 1, the isolation valve 94 is included and the conduit 16' is closed at point 87'. is connected to the common line 88 at point 96' (between the isolating valve 91 and the control valve 46 of this line) so that the condensate is transferred to the downstream part of the common line behind Economie+1'84. Full reintroduction line 16'
It is advantageous to provide a bypass conduit 92 that connects all the parts.

Advantageously, the branch conduit 39 for drainage is provided with a separation valve 44 .

Next, the percentages of the embodiment shown in FIG. 1 will be given.

The condensate water is directly reintroduced into the boiler 8, mixed with make-up water flowing out from the water tank 10, and then delivered to the flow conduit.

The operation of the power-driven pump 17 for direct condensate reintroduction is continuous, ie permanent.

The periodic operation of the water pump 12 is controlled by the water level in the buffer tank 14 by a water level detector or water level controller 53, said controller 56 starting the pump 12 when the water level drops below a minimum value. , stop the pump when the water level reaches the maximum allowable level.

The liquid level controller 67 regulates the supply of make-up water to the boiler by acting on the single automatic control valve 46.

The economizer 84 is isolated and rendered inoperable by valves 90.91, and the boiler 8 is then directly supplied with re-introduced condensate and make-up water via a short-circuit or by-way conduit 92. will be paid.

According to the possibility of closing the isolation valves 90 and 91 of the economizer 84, the economizer necessarily closes the common pipe 8.
A safety member such as a safety valve 97 mounted on the 8 is provided.

The drainage conduit 39 connected to the discharge side of the economizer 84 allows a permanent minimum flow to be created through the economizer f in the form of drainage terminating in the buffer tank 14. The condensate that has passed through the economizer 84 produces a vaporized portion of the condensate, allowing the liquid flowing through the economizer f to be guided preferably from below to above.

This is because the steam thus produced and which tends to rise has no unfavorable effect, and the heated condensate and the steam which may then be produced do not economize in this way. This is because it is collected from the top of the

The vapors often generated by evaporation of condensate are often lost as they reach the buffer tank 14, are collected therein, and are conveyed from there to the parts of use.

The feed water is not delivered directly to the boiler 8, but is supplied to the buffer tank 14 in order to be mixed with the stored condensate.

Now, the above principle is based on the application of the principle shown in Figure 1 to a multiple boiler system that does not contain an economizer.
:v also applies to embodiments of the type shown in FIGS. 2 to 4. It is known that in installations which involve reintroducing condensate directly into several boilers, the introduction of the reintroduced condensate into the individual boilers must be controlled. It is also necessary to be able to individually control the introduction of make-up water, which takes place each time the water level in each boiler considered reaches a lower limit. The disadvantage to this is that for existing installations it requires the addition of a second control device for the boiler water level, and for new installations it requires the installation of two independent control devices for each boiler. That's true.

The invention makes it possible to eliminate the above-mentioned disadvantages, for example in the case of installations with several boilers forming a set of steam generators, the method according to the invention provides that the above-mentioned permanent escape flow Returned with the feed stream to one of two make-up liquid sources or directly to one main condensate storage tank common to all boilers; said feedwater storage tank discharging directly into said condensate storage tank where said feedwater is fed and mixed by an intermittent flow automatically controlled in a tracking relationship bound to the current liquid volume stored. It is characterized by According to another feature of the invention, the permissible flow into the main reservoir of said water supply is mutually constrained in tracking relationship with a predetermined minimum amount of liquid impounded in said reservoir, so that no residual The stream entering the cold water supply is heated by being diffused into a minimum amount of hot liquid that will heat the stream entering the cold water supply.

The apparatus according to the embodiment of FIGS. 2 and 4 includes a drainage conduit 3
9 (shown in dotted lines in FIG. 4).
), behind the water supply pump 12, the water supply conduit 11
or to the top of a single main buffer tank 14 (as shown by the solid line in FIG. 2 and by the dotted line in FIG. 4), Each joint conduit 16 has an individual automatic control valve 46 for direct reintroduction of
Via a conduit 88.88a containing 46a, it is connected in parallel with several (for example two) boilers 8, 8a 9, and the water supply conduit 11, as in the case of FIG. Opening to the bottom of the buffer tank, the level sensor or controller 56 of the tank is connected by a remote control circuit 54 to the feed water pump 012, which serves as the main pump for the direct reintroduction of this condensate. It is characterized by the fact that

According to another feature of this device, the main pump 17
The suction conduit penetrates the bottom of the main buffer tank 14 and enters said buffer tank approximately vertically at a height corresponding to the minimum amount of liquid to be retained in the buffer tank 14. 1. Thus, according to the above arrangement, directly into the buffer tank 14 located upstream of the condensate reintroduction pump 17,
By drawing back not only the re-introduced condensate water, but also the make-up water exiting the water tank 10, the use of dual controls for each boiler is avoided. in this case,
The operation of the pump 17 must be continuous in order to allow water to be supplied to the boiler according to the respective needs. Therefore, the operation of the feed pump 12, which allows the introduction of fresh make-up water into the buffer tank 14, is limited to a permissible minimum value below which there is no longer any condensate available and there is a risk that there will be no make-up water to send to the boiler. This will be associated with a decrease in the water level in the buffer tank 14. ”2 Into the buffer tank 14, water supply pump 1
A drainage conduit 69 that continuously returns a small portion of the condensate sucked downstream of 7 has no possibility of water supply if the boiler does not require water, especially when the control valve 46.46a is closed at the same time. ie with zero output, eliminating the risk of the pump operating.

FIG. 6 shows that at any time a minimum amount of water of height h remains at the bottom of the tank, and the low water fg,N of the tank.

A special design of the buffer tank 14 is shown in which the buffer tank 14 is arranged in such a way that the liquid level Nll rises (h = N1 - No). This is achieved by placing the suction orifice 16'' above the conduit 16 at least at said liquid level N1, or above said liquid level of the minimum volume of water. , i.e. by being diffused into said minimum volume of hot condensate,
The water is introduced via the water supply conduit 11, thereby completely preventing sudden changes in pressure or hammering due to thermal causes. A liquid level controller or controller 56 (hereinafter the same) starts the water supply pump 12 when the liquid level of condensate in the buffer tank 14 drops to the minimum liquid level N1, and starts the water supply pump 12 when the liquid level of condensate in the buffer tank 14 drops to the minimum liquid level N1. When a high liquid level reaches, for example, intermediate liquid level N2,
It acts to stop the water supply pump 12. Drainage pipe 3
9.39' returns the condensate (delivered by the pump 17 and not introduced to the boiler 8.8a) to the conduit 11 feeding the buffer tank 14, these condensate drains, the feed water It is diffused into water in a buffer tank 14 by a pump or injector 12. This results in
The energy (in particular electrical energy) consumption of the motors of both pumps 12, 17 can be saved.

Figure 4 shows the flow of condensate collected freely, i.e. by gravity flow, and fed to the main reservoir by forced mechanical force.
1 shows a variant application of the method according to the invention of the type using at least one auxiliary reservoir;

This variant is characterized in that the condensate is delivered under a pressure approximately equal to the pressure present in the boiler. The apparatus for carrying out the entire method comprises at least one and preferably several auxiliary pump stations, for example two, each of which connects the condensate gravity drain collection outlet pipe 12.
1.121a' (i = auxiliary buffer tank opened inward, that is, buffer tank 105, 105a (the same applies hereinafter)
and an auxiliary pump 103, 103a kept under static pressure by the buffer tank from which the pump draws suction, and the respective supply conduits 118, 118a of the auxiliary bonf 0 location.
Due to their integration into a common conduit 15 opening into the buffer tank 14, the supply conduits 118, 118a are
It opens to the top of the buffer tank 14. The auxiliary bonzo section delivers condensate under a pressure approximating that present in the boiler to the main buffer tank, and the main pan 7a tank also takes over the make-up water supply that enters from the tank 10. The rear pump 17 sucks these condensates and delivers them to the boiler. In this case, the buffer tank 14
There is a risk of excessive pressure build-up in the Such an increase in pressure mainly occurs when there is no water in the boiler and the drop in the level of condensate in the buffer tank 14 of the boiler equipment is not noticed. Caused by feeding. The risk of such undesirable overpressure is eliminated by the invention by at least one safety valve 97 connected to the top of the main buffer tank 14 or to the supply conduit 15 of the various auxiliary locations.
' can be eliminated by providing . Advantageously, the discharge orifice of the safety valve is connected to the discharge pipe 30, for example to the upper part of the water tank 10. In such a case, with the various pumps momentarily operating at zero or near zero output and maximum water supply head, the pressure within the main buffer tank 14 will be reduced to the tolerance established by the setting of the safety valve 97'. The pressure rises to a value above the limit that can be obtained and therefore the safety valve 97' opens, releasing the excess pressure to the water tank.

5-7 illustrate an improved low pressure condensate transfer lock system. In steam installations where the pressure and temperature are practically constant, or at least nearly constant, at all points and are identical in all respects except pressure drop, one or more of the lower The condensate is collected locally or generally by gravity, from where it is taken up again and, for example, mechanically delivered, and then reintroduced directly into at least one steam-generating boiler to supply the plant with water. Guaranteed generation of salary steam. Therefore, this type of equipment
A network of steam and condensate conduits at approximately constant pressure and temperature, excluding fluctuations in flow pressure drop, and one or several auxiliary condensate tubes for direct reintroduction of condensate into the boiler. It consists of departments.

In installations consisting of several pipe networks with different pressures generated by the expansion of steam upstream of these pipe networks, it is necessary to provide as many auxiliary bonzos as there are pipe networks with different pressures. Each auxiliary pump station also includes a buffer tank for gravity collection of condensate and a feed pump kept under static pressure by this buffer tank. The pumps of each of these valley auxiliary pump stations can be used to supply the necessary feed head to the steam boiler, or to the condensate collection buffer of the other auxiliary pump stations, which can serve a higher pressure conduit network. It is possible to deliver condensate directly to the tank, and from the high-pressure conduit network, the aforementioned pump further delivers all the condensate delivered to the associated buffer tank and returns it to, for example, a steam boiler. let

With respect to the lower point of the conduit network at the higher pressure, it is often possible to design an installation at the lower pressure with one lower point which is geometrically superior in height. In this case, there is a problem in discharging condensate from the low pressure network to the high pressure network simply by gravity, without the use of a feed pump or equivalent forced circulation device. On the other hand, 1. It is necessary to avoid free communication between the two groove pipe networks that have different pressures. This is because such free communication causes automatic pressure equalization.

According to the invention, the condensate l
- system power for generating and distributing the steam obtained), providing a method for discharging and recovering the condensate, and providing at least two systems for utilizing the steam (by condensing the steam), respectively, at two different pressures, both high and low. By operating a system workshop, the above problem is technically solved. This type of method involves producing steam supplied to a low pressure system, for example by expanding a portion of the steam supplied to a high pressure system, and producing steam supplied to a low pressure system, preferably substantially dry and at least to a large extent free. i.e. by guiding natural gravitational return flow to recover at least a portion of the condensate discharged from each system;
In this case, said condensate is not collected and stored at least temporarily in individual storage RsO, and at least the condensate stored in the storage of said high-pressure system is connected to said low-pressure system. vaporizable liquid of the boiler by automatically or periodically or intermittently controlling the flow rate of at least the condensate output from the storage, providing mechanically forced and preferably continuous circulation; The water is reintroduced to the boiler according to the request. Such control is achieved by a floating on-off type regulation constrained in a tracking relationship to the current amount of measured or planned condensate present in the reservoir of the low pressure system. [ ), all features automatic or periodic control of the input flow rate of condensate to the storage tank of the low-pressure system, and therefore, the respective control of the input and output flow rates are inversely related to each other. The input flow is interrupted during the progress of the output flow, and the output flow is interrupted during the progress of the input flow. Furthermore, the method includes an input R of condensate entering from a storage tank;
'c isolating the reservoir of the low-pressure system from the system by shutting it down, and then establishing communication between the two systems, l: equalizing the respective pressures in both reservoirs of both systems. It is characterized by the fact that the condensate is discharged by gravity from the storage part of the low-pressure system to the storage part of the high-pressure system.

In order to carry out the above method, the present invention provides a condensate transfer locking device in the entire system, consisting of at least two systems using steam at high and low pressures, respectively, each of the two systems being arranged, for example, in parallel. At least one active steam supply conduit (119 in the high pressure system and 119a in the low pressure system) feeding mounted heat exchange equipment (119 in the high pressure system and 119a in the low pressure system)
7 and 117a) in the low-pressure system and opening to the top of at least one buffer tank located at the lowest point of the system considered from both said devices (buffer tank 14 in the high-pressure system and buffer tank 14 in the low-pressure system). 105
) at least one condensate return conduit (118 in the high pressure system and 118a in the low pressure system) discharging said condensate. At least one of the two buffer tanks described above, particularly the buffer tank 105 of the low pressure system, can be provided with a liquid level control device 107. The active steam supply conduit 117a on the low pressure side opens into the high pressure active steam supply conduit 117, in particular via a steam pressure reducing valve 127 or a similar automatic pressure regulator, while the high pressure buffer tank 14 , conduit 16 for direct reintroduction of condensate.
It is connected to the above boiler via. Said conduit 16 extends from the bottom of said high pressure buffer tank 14 and is connected to a preferably permanently operated forcedly operated pump 17.
Contains. The pump 17 is kept under static pressure by a high-pressure buffer tank 14 and draws suction from within this tank. For example, near the intake of said boiler of conduit 16, in a constrained tracking relationship to the current water level in said boiler;
Automatically controlled, motor-driven valves are installed. Each use-side device 119, 119a has two active steam inflow pipes 120, 120a and a condensate outflow pipe 12, respectively.
1° 121a, two corresponding active steam supply conduits 117, 117a and condensate return conduit 118° 118
a, and each of the above active steam inflow pipes 1
20.120a is advantageously connected to the associated active steam supply conduit 117.degree. 117a via an ascending bend 120"120" or the like. The concave portion of the curved tube is oriented downward to prevent condensate that may be present in the active steam feed conduit 117, 117a from entering the inlet tube 120.degree. 120a.

In the above-mentioned apparatus, the buffer tank 105 at the A pressure is connected to the high pressure buffer tank 14J: 9, and the upper part or top of the high pressure buffer tank 14 is connected to the high pressure condensate condensate conduit 118 (collector). i.e. connected to the buffer tank 14 by a conduit 15),
It is connected to the base of the low pressure buffer tank 105 via the drain conduit 15', but the low pressure condensate condensate conduit 118a
and the drain conduit 15' are each provided with a buffer tank 10.
Two motor-operated stop isolation valves 128, 129 are provided upstream and downstream of 5, respectively, and the servo motors are controlled via remote control circuits 130, 131', respectively.
Liquid level control device 10 mounted on buffer tank 105
7 monitoring elements, and thus the device as a whole is characterized in that it operates cyclically as follows.

If initially no condensate is present in the buffer tank 105 of the ζ low-pressure system, the level control device 107 simultaneously ensures the closure of the downstream isolation valve 129 and the opening of the upstream isolation valve 128. Buffer tank 105 is then at low pressure system pressure and condensate is stored therein by gravity flowing down from conduit 108a. When the buffer tank 105 is full, the liquid level control device 107 operates in the opposite direction. That is, the upstream valve 128 is closed and the downstream valve 129 is opened. When the downstream valve 129 opens 17, the steam filling the upper part of the high pressure condensate condensate conduit 118 and/or the high pressure buffer tank 14 passes through the conduit 15' and the downstream valve 129 to the low pressure buffer tank 105.
It enters from below and thereby increases the pressure therein by a value of 1, which is the high pressure of the high pressure system. Thereafter, when the pressures reach equilibrium, the condensate flows by gravity from the buffer tank 105 into the high pressure system, ie, into the buffer tank 14 which forms the low point of the high pressure system. During said time period, the condensate water of the low pressure system continues to arrive via conduit 118a and to the upstream isolation valve 128.
is accumulated in front of the Therefore, the above needs to be taken into account when designing the low pressure system, particularly the condensate return conduit 118a. When the buffer tank 105 of the low pressure system becomes empty, the liquid level control device 107 repeats the two series of operations to perform the filling and draining circulation operations. This arrangement has the advantage of allowing condensate to be discharged from the low pressure system to the high pressure system, thus allowing the saving of at least one pump and various accessories.

The conduits 15 and 15' are placed in permanent communication with each other through the intervening buffer tank 14 and possibly also through the direct connecting conduit 162 shown in dotted lines in FIG. The buffer tank 105 is advantageously cylindrical and can be placed either horizontally as shown in FIG. 5 or horizontally as shown in FIG. It can be arranged vertically as shown in FIG.

According to another feature of the invention, the upstream end of the drain conduit 15/ extends into the tank 105 and has an orifice 1 at its base.
By means of a substantially vertical conduit 15'a in which 66 is provided,
It extends in the upper part 1 of the low pressure buffer tank 105.

The line 15'a is connected to the buffer tank 1 when the operation cycle is reversed, that is, when the isolation valve 129 is opened.
471), the lower orifice 106 allows condensate in the buffer tank 105 to enter the drain conduit 15'.

Figures 8-20 show the core of the inventive principle for producing the necessary mechanical shock distortion or acceleration for the forced discharge of condensate or condensate to be directly reintroduced into the boiler. In a steam plant where pressure and temperature are virtually constant everywhere and substantially the same at all points (excluding pressure losses), condensate generally reaches a low point by gravity, from where it flows into steam. It must be placed under higher pressure as it is reintroduced directly into the generating boiler. This pressure difference that arises between the system of condensate gravity flow lines (in which the pressure is substantially equal to the pressure in the boiler and the pressure loss in the steam phase circuit is small) and the inlet to the boiler is, on the one hand, equal to the sum of the liquid phase pressure losses between the low point of the system of water gravity return flow lines and the inlet of the boiler, on the other hand the net geometric height over which condensation must be forced, i.e. equal to the difference between the water level at the lowest point and the water level in the boiler). Therefore, in order to force condensate from the low pressure system into the high pressure system and from there to push this condensate together with the condensate of the high pressure system, the upper pressure must be equal to or equal to the geometric height of the rise of the pitch retaining tube. It is necessary to overcome the pressure difference (which can be increased by the geometric height difference) between two systems with different pressures.

This pressure difference is typically provided mechanically, for example by a rotating device, such as a rotary pump. For a number of technical and economic reasons it is desirable to avoid the use of mechanical forced pumps to reintroduce condensate directly into the steam generating boiler. Among the above reasons, the following may be mentioned:

To reduce business investment.

To reduce maintenance costs (wear of moving parts under severe temperature and pressure conditions).

Elimination of the risk of cavitation of the pump (which tends to occur at very high wear and reduces the hydraulic properties considerably) or the net positive static head caused by the upward flow of the pump, i.e. the high suction required in the buffer pump. To eliminate the need for.

For the elimination of the need for cooling of rotating bearings and seals.

To eliminate most of the risks of shutdown or the need to prepare backup or emergency equipment in the event of a breakage.

To eliminate the need to install accessories such as separation member filters to the operating pump and backup pump.

In order to solve all this technical problem, the invention proposes to condense in a closed circuit where the pressure and temperature are substantially constant everywhere and are virtually identical at all points excluding pressure loss. Condensate discharge stream in a system that generates, distributes and utilizes all of the steam, either for direct reintroduction into the steam generating boiler or for forced discharge into the system at high pressure.
or providing a method for forced discharge of condensate through a geometrical rise, such as a pitch-holding pipe rise, in a highly intermittent manner, in which at least a portion of the condensate discharged by guidance; is recovered, preferably in dry form, at least most of it generally by gravity flow;
Returning to at least one closed vessel for at least temporary collection and accumulation forming a main buffer tank or the like, generally located at a low point. This method is performed in a manner known per se; waits for the buffer tank to be filled with liquid at a certain maximum level; disconnects all non-at least indirect fluid communication with at least the upstream part of the system; By isolating the head space of the buffer tank containing the gas phase from the outside, or completely stopping any upstream ingress and preventing any downstream return of condensate into the buffer tank; and free surfaces of the contained liquid. by adding sufficient additional vapor pressure to make the total effective gas pressure substantially equal to the sum of the required net geometric height and the downstream flow pressure losses to be overcome.

According to another feature of the method, the automatic control is repeated periodically in a manner known per se in a linked follow-up relationship to the amount of condensate present in the vessel forming the buffer tank. A controlled cycling operation is provided.

The apparatus according to FIGS. 8-20 for carrying out the method described above consists of at least one main buffer tank 14.105. This buffer tank 14, 105 has at least one maximum and one minimum level controller 53.107'r and an inclined condensate return conduit 15 opening into the boiler.
, 125. The main buffer tank is generally located at a low point to form a pumping substation for direct reintroduction into the boiler, or at a geometric rise at position 1 to a break or local low point or pitch holding pipe rise. Forms a transit lift pumping substation. The upstream part 15 or 101' and the downstream part 16 or 116' of this conduit connect to the upper and lower parts, respectively, of the main buffer tank 14, while check valves etc. 20.2
0' is interposed in the downstream conduit section 16 or 106'. This device is characterized by a means for completely additionally or locally introducing steam into the upper space of the main buffer tank 14. The means consist of a pilot or switch element connected by a remote control circuit 54, 54'', 124 to a monitoring element of the level controller 53, 107, while the check valve 20' is operated in a manner known per se. The upstream conduit sections 15, 101° 101' are installed in series.

- According to an aspect, the method includes heating at least a portion of the liquid phase present in the buffer tank by external heating to raise the temperature of the liquid phase and evaporating the portion of the liquid to pressure and thus generate a thermodynamic pumping effect that generates a cyclic shock. This theoretical principle can be understood by considering a closed vessel, such as buffer tank 14 in Figure 8, filled with condensate (e.g. liquid water) at a certain temperature and previously discharged non-condensable products. be done. The upper part of this vessel, which is not filled with liquid phase, contains vapor at a pressure corresponding to the temperature of the liquid with respect to the saturated vapor tension curve for the vapor of the fluid in question (in this case water). If this liquid water is heated by some means 140 and at the same time the container 14 is always closed, each juncture corresponds exactly to a new pressure always located on the saturated steam tension curve. Therefore, in order to increase the pressure of the condensate and at the same time raise the temperature of the condensate, it is necessary to install a buffer located at a generally low point in the condensate gravity return line system, or at a local low point in the rise of the condensate return pipe. It is sufficient to heat the condensate contained in the tank 14.

Starting from a certain pressure rise value, it is thus possible to reintroduce the condensate directly into the steam boiler or to pass the condensate through the pipe riser. In this way, the desired efficiency or useful pressure increase is obtained simply by heating the contained condensate from an initial temperature to a final temperature and bringing it from an initial pressure to a final pressure. At the beginning of this heating cycle, the volume located below the condensate is filled with saturated steam at a pressure corresponding to the temperature defined on the saturated steam tension curve. Due to the increase in temperature, evaporation also occurs, the significance of which is determined by the difference between the total heat or enthalpy contained in the respective initial and final volumes of vapor entering the tank 14. A constant and complex mutual heat exchange therefore takes place in both directions between the steam and condensate in contact with each other. In practice, the actual heating power supplied to such a thermodynamic pump is that required to raise the temperature of the liquid phase or water of the fluid used in the cell from an initial temperature to a final temperature. In this way, when the upper condensate level N3 reaches the tank of the thermodynamic pump,
The space formed between this upper liquid level N3 and the top N4 of the tank has saturated steam at the same pressure and the same temperature as the condensate, and hence is called the initial pressure. In order for these condensates to be subsequently discharged by the thermodynamic bonder, at the end of the discharge cycle the initial volume of condensate is replaced by saturated steam at a pressure called the final pressure. Therefore, in order to be able to discharge condensate, it is necessary to supply a heating power that satisfies the following:

On the one hand, to raise the temperature of the condensate from its initial value to its final value, thus providing sensible heat; on the other hand, to evaporate the required weight of water and to bring the steam thus produced up to the final pressure. be able to fill the volume of the condensate evaporated at and the part of the volume of the initial steam which decreased with an increase in its pressure and therefore with an increase in its density by the initial steam.

From the summation of the two preceding items, it is necessary to derive the difference between the potential heat of vaporization at the respective initial and final pressures of the weight of the vapor initially present. Most of the thermal power supplied by the power source serves to increase the temperature of the liquid water, and since this power is supplied to the fluid (water) itself, it is contained integrally in the condensate at the inlet to the boiler. It can be seen that it is completely recovered in the boiler and is thus derived from the power supplied by the boiler and thus from the consumption of heating fuel in the furnace of the boiler. If the heating power thus supplied to the condensate is accordingly from an electrical source, the unit price at its thermodynamic pump is the same as that supplied to the boiler, where relatively low-cost fuel is consumed in the furnace. substantially higher than the unit price of heating power. On the one hand, the heating power consumption in this thermodynamic pump is relatively higher than the power consumption in a mechanical pump providing the same characteristics.

From this it follows that the thermodynamic pumping device according to the invention is suitable for small overpressures and low flow rates, which are difficult to obtain by ordinary pumps, as well as for cases where the net positive suction head required by ordinary pumps is prohibitive. If high,
It will essentially be equalized.

According to the embodiment shown in FIGS. 8 to 18, said heating means provide at least one heating in the transmission and heat exchange connection with at least a portion of the nominal volume of condensate contained in the main buffer tank 14 or 105. resistor 140
or constituted by equivalent heat supply means. Switching of this heating resistor is controlled by the remote control circuit 54 or 124 of the liquid level controller 56 or 107. In Figures 15 to 18 of the 8th and 9th work, the float of the liquid level controller 56''! or 107 is connected to the upper liquid level N3 while the condensate in the buffer tank 14 or 105 is rising.
Once the liquid level controller reaches the remote control circuit 54
or 124 switches on the heating resistor 140, which then heats the condensate and brings its pressure to the value Pi (which is essentially the pressure in the boiler).
to the value P2 required to reintroduce the condensate directly into the boiler. During this forced transport, the level of condensate becomes low in the buffer tank, and when it reaches the lower level N1, the level controller 53 automatically switches off the heating resistor 140.

According to other general features of the above-described method shown in Figures 9-11 and 15, i6 and 19, the quantum buffer tank 14 forcibly conveys condensate from the main buffer tank 14 to the pumping. Provision is provided for temporarily collecting and storing condensate in at least one upstream auxiliary buffer tank 105'. According to other general features of the above-described method illustrated in FIGS. 9-11 and 16-20, at the end of the forced transfer cycle the main buffer tank 14t or 10
5, means are provided for releasing the vapor pressure, preferably automatically, known per se. This release continues until the vapor pressure in the buffer tank is again substantially equal to the condensate pressure upstream of the main buffer tank. According to still further features of the aforesaid method, the aforesaid pitch retention between the respective upper gas phase compartment spaces of the respective main and auxiliary buffer tanks or as shown in FIGS. 9-11 and 16-20. said pressure by providing a temporary and controlled direct communication between the headspace of said main buffer tank in the pigeonhouse of the arrangement and an upstream inlet stream of condensate - or preferably an upstream feed stream of live steam. be equal.

The arrangement for applying the said features of this method is shown in FIG. Interposed before the check valve 20' and possibly after an additional upstream check valve 20#. The upper part of the main buffer tank 14 has at least one vapor release conduit 14
1, the auxiliary buffer tank 105' opens into the interior.
or to the top of the trench motor shut-off valve 142
to the upstream portion 15 of the condensate take-off conduit, preferably in front of the check valve 20'' (as indicated by the dashed line 141'). The capacity of the auxiliary buffer tank 105' is determined by the maximum liquid level N3 and the minimum liquid level N1 of the float or sensing means of the liquid level controller 56 in the main buffer tank 14, respectively. Advantageously, it is substantially equal to the volume v2 of condensate defined between the corresponding highest and lowest positions, said positions being respectively connected to resistors 140, r,!ll switches of the heating means configured Insert or cut.

The operation of the apparatus of FIG. 9 is as follows. Is the main buffer tank 14 initially substantially empty?1. or heating means 14
0. It contains a minimum volume v1 of condensate sufficient to submerge the sensing means, e.g. ), the heating means 140 is not switched on and the valve 142 is open. A communication is thus formed between the upper vapor phase space (capacity V3) of the main buffer tank 14 and the upper space of the auxiliary buffer tank 105' for temporary storage of condensate,
In this way the respective pressures in these two tanks are equal and the pressure in the main buffer tank 14 (equal to the pressure in the condensate gravity flow system), thus the check valve 20' is opened. Eventually, the condensate temporarily accumulated and held in the auxiliary buffer tank 105' enters the main buffer tank 14 by gravity through the check valve 20' and maintains it at a constant liquid level N3. When the detection member of the liquid level controller 53 rises to its highest position corresponding to the highest liquid level shown in FIG. operates until the required delivery pressure P2 empties at least a portion of the main buffer tank 14, and then the cycle described above is repeated in this manner cyclically and indefinitely.

FIG. 10 shows the application of the method described above to at least two pumping substations installed in parallel. The method in this case involves keeping the substations in step with each other for the purpose of substantially continuously filling the boiler with liquid that is evaporated by the independent operation of the substation while filling the other substation with condensate. The turbulent operation is characterized by an automatic time delay linked in a tracking relationship to the amount of condensate contained in the individual main buffer tank of the pumping substation. FIG. 10 shows an arrangement for carrying out this method in a system in which each pumping substation is identical to that shown in FIG. The elements of the second substation are designated with the same reference numerals as the first, but with the index a. The condensate feed pipes 16.16a are combined at the junction 144 to form one common pipe for reintroducing the condensate into the boiler and into one auxiliary buffer tank 105' of the pumping substation. The leading condensate gravity flow return conduit 15 supplies via branch 15a to the auxiliary buffer tank 105'a of the other pumping station. A feature of this arrangement is that each main buffer tank 14,
The monitoring elements of the liquid level controllers 53, 53a of a are connected by individual remote control circuits 145, 145a to time delay adjustment relays, which actuate both heat pumps to alternately convey condensate. Due to the mechanical pumping substations, condensate can be continuously reintroduced directly into the boiler, and one of said substations transports condensate by emptying its main buffer tank, and the other substation transports condensate by emptying its main buffer tank. Fill the buffer tank and vice versa.

FIG. 11 shows another modification of the method of the invention.

According to this method, a safe conveyance can be achieved in which the excess condensate present in the main buffer tank 14 is conveyed to the supply tank or to a low pressure system (not shown), and this safe conveyance is automatically controlled. In particular, if a steam boiler is not required or the need is low in the liquid to be evaporated, it is preferred to interlock it in a tracking relationship with the maximum permissible liquid level in the main buffer tank. This variant is characterized by the safe transfer of steam in the case of overpressure in the main buffer tank (because the condensate is not discharged and the temperature in the main buffer tank increases), which is automatically controlled to the highest permissible pressure. and occurs in a following relationship with the excess condensate conveying line or into the upstream inlet flow of condensate.

In the arrangement shown in FIG. 11 for carrying out this method, at least one of the systems can be provided with an upper liquid level controller 56' in each main buffer tank 14, and the main buffer tank 14 is at least 1
It has a lower part connected by a main condensate discharge conduit 58 to the supply tank outlet or to the low pressure system mentioned above. Said discharge conduit 58 advantageously has a non-return valve 45 and a motor-activated check valve 60, the servo motor of which is connected by a remote control circuit 66 to a monitoring element of said upper liquid level controller 56'. be done. This condensate discharge conduit 58 connects to the condensate discharge conduit 16 at a junction 59 . A feature of this arrangement is that the upper part of the main buffer tank 14 is connected to the condensate discharge conduit 58 (
downstream of the valve 60 (at a point 147) or condensate is connected to the upstream portion of the conduit 15 (upstream of the check valve 20' (at a junction 148); and These two connection possibilities for conduit 149 are shown in dashed lines in FIG. 11. The condensate gravity return conduit 15 can be connected directly, as shown in solid lines in FIG. As shown in , the force is indirectly guided to the main buffer tank 14 via the auxiliary buffer tank 105' in front of which the non-return valve 20'' exists. A bleed conduit 25 is provided.
5 comprises an automatic bleeder 27 preceded by a stop valve 26, and a bleed conduit 28 with a manual drain cock 29 is connected in parallel to the conduit 25 in a manner known per se.

Furthermore, the main buffer tank 14 has a decant pot 1 at its bottom.
It has 51. This decant bot 151 has stop valve 1.
It has an outlet 142 with 53.

The operation of the device described above is carried out as follows. When the main buffer tank 14 is filled with condensate at a constant level which starts the operation of the level controller 53, the level controller 5
6 sets the heating means 140 into operation so that condensate is discharged from the main buffer tank 14 via the pipe 16 as a result of thermodynamic effects. If the need to resupply the boiler or high-pressure system with the condensate thus discharged is less than the flow rate of condensate discharge as a result of said thermodynamic effects, the condensate in the main buffer tank 14 is discharged by the upper liquid level controller. 53
' can continue to rise at level 1 by actuating valve 60 (generally closed during normal operation), and excess condensate is thus drained via drain conduit 58. Any possible steam overpressure in the headspace of the buffer tank 14 is discharged via the safety valve 150 and the discharge conduit 149.

FIG. 12 shows the application of the above principle to two tube systems. This piping system comprises at least two distinct line systems, respectively for live steam inlet (117) and condensate discharge (118), between which there is a steam use or utilization equipment diverter or steam consumption station; For example, heat exchangers 119 are connected in parallel or in a derivative manner. Each of those stations is connected to a common main steam inlet conduit 117 and a common main downhill condensate return conduit 118 via a steam inlet conduit 120 and a condensate return conduit 121, respectively. At least one pitch holding tube rise with a main buffer tank 105' is provided.

The main buffer tank 105 has two systems or conduits 117, 11
8 has at least one vapor phase direct connection conduit 122 between the descending branch 1 of said tube rise 126.
01 and the live steam inlet conduit 117 are interconnected.

The buffer tank 105 is located at the lower point of the tube rise 123, its descending vertical branch 101 opens into the vapor phase space or upper part of the buffer tank via a check valve 20', and its descending vertical branch 106 opens into the vapor phase space or upper part of the buffer tank. 105 and within which the lower open free end of branch 106 opens substantially proximate the bottom of the buffer tank, and the rising branch 106 is connected to check valve 126.
has. Furthermore, the buffer tank is equipped with the aforementioned heating means 1402.
For example, it includes a heating resistor, and this heating means 140 is connected to the liquid level controller 107 via a remote control circuit 124. Difference ha in liquid level between the respective upper points of the descending vertical branch pipe 101 and the ascending vertical branch pipe 106 of the pipe rise 126
defines the geometric height of the condensate rise for passing condensate from the downstream section to the upstream section of the condensate return conduit 118, while the lower end of the upstream section of this condensate return conduit 118 and the downstream section The liquid level difference hb between the upper end and the upper end defines the value of the pitch holding tube rise of this condensate gravity flow tube, and the liquid level controller 107 determines the minimum liquid level of condensate that is always maintained in the Eri buffer tank 105. Rising branch pipe 1 with surface and pipe rise arrangement 126
06 upper point (slanted stop connection portion 10 of conduit 118
The difference H in the liquid level between exactly equal.

This arrangement is characterized by said vapor exhaust conduit 141 connecting the upper part or vapor phase space of the buffer tank 105 to the vapor phase direct connection conduit 122 and containing a motor-operated isolation valve 142, the servo motor of said valve 142 being remotely controlled. It is connected to a monitor part of the liquid level controller 107 by a circuit 146 (51). This steam exhaust conduit 141, shown in dotted lines in FIG. 12, is optional.

Figure 16 shows the same application of the same principle to a single tube system. This single pipe system consists of at least one single common inclined conduit 125 for inlet of live steam and return of condensate to gravity. Use or consumption devices 119' for this conduit 125 are subsequently provided for steam inlet pipes and condensate outlet pipes 120' and 121, respectively.
” (connected via r, the common line 125 includes a pinch retaining tube rise arrangement 1 with the same elements of the same shape as in the previous drawings)
26' is provided. Steam phase upper derivative loop conduit 1
16' bypasses this tube rise arrangement 123'ffi and connects the upper point of its descending vertical branch 101' to the (rise-1 of the tube rise arrangement: or the step of the inclined conduit 102' connecting the downstream branch). towards the upstream end of the downstream section of the common conduit 125 (between the connection point of the steam inlet pipe of the first downstream usage device 109') and to a point located downstream of the pipe rise arrangement. This arrangement connects the top of the buffer tank 105 to the loop conduit 116' and includes a motor-operated stop valve 142'c which is remotely controlled by the level controller 107 via circuit (52) 143. characterized by

As previously discussed, the power dissipated in the thermodynamic pumping action (i.e., the calorifica provided by heating means 1402, e.g., heating resistors, etc.) is controlled by conventional mechanical pumping to provide the required flow rate and pressure performance. The power consumption is considerably higher than that consumed by forced pumps. According to the invention, an important proportion (e.g. 60
%, 1. The total cost of energy required for the pressure increase to be obtained to force the condensate out of the buffer tank is reduced, and the thermodynamic pumping effect to achieve the operating cycle is It takes less time. To this end, in order to implement this idea, the method according to the invention starts rapid heating as soon as the condensate in said vessel forming the main buffer tank reaches a certain intermediate filling level below said maximum liquid level. characterized by According to another feature of the method of the invention, this is achieved by physically separating the volume to be evaporated from the condensate to be discharged, in particular the strictly necessary volume, and by separating and the buffer tank vessel itself. Is it heated inside? This is achieved by exclusively heating the volume of condensate to be evaporated which is transferred into an auxiliary vessel outside the tank and heated therein, the vapor thus produced preferably containing the liquid to be discharged. A minimum amount of condensate, which is conveyed directly to the space above the free surface plane of the condensate and is to be heated, is retained in the buffer tank. This method can also be implemented using any one of the arrangements of FIGS. 14-18, respectively. 1st each
Each of the arrangements shown in Figures 4 to 18 consists of an isolation valve 149' installed towards the downstream end of the condensate gravity return conduit 15, said conduit 15 leading into the main buffer tank 14, in particular the auxiliary buffer tank 105''. e installation 1. opens between it and said tank 14. According to one feature of this arrangement, an isolation valve 149"k is installed upstream of said check valve 20' in series with said corresponding check valve 20'. installed, the motor is activated, and the servomotor is connected via remote control circuit 150 to a monitoring component of level controller 56 of buffer tank 14. As shown in FIGS. 14 and 18, there is an additional intermediate level controller 151 in the buffer tank 14.
(i=it is advantageous to install, and according to other features of this arrangement, the respective monitoring parts of the middle level controller 151' and the highest and lowest level controllers 56, in a common pilot relay remote control circuits 153', 54 and 15 respectively via media of 152';
4' to the switch or start-stop member of the heating means 140 (both level controllers are connected to the pilot relay 152 and the latter to the heating means 140, respectively).

In the embodiment shown in FIG. 14, the aforementioned physical separation of condensate is accomplished by a partial internal partition wall 155 provided within the main buffer tank 14. This partition wall 155 extends upwardly from the bottom of this buffer tank to a finite height corresponding to the maximum (55) high liquid level N3 and thus divides the buffer tank 14 into two unequal areas, which The zones communicate with each other in the upper part of the buffer tank, ie in the vapor phase space.

This partition wall is an additional intermediate liquid level controller 151'
at least one interconnected through-orifice 15 located substantially at an intermediate liquid level N2 defined by the relative position of
6, whereas the heating means 140 are arranged at the bottom of the smaller zone, the volume of which corresponds to the required minimum amount of liquid to be evaporated. Therefore partial partition wall 1
The six small through orifices 156 located in the second part of the heating means 140 provide a full supply of liquid water (condensate) to this smaller area, whereas the upper part of this smaller area Steam can pass freely upwards in the space and can be introduced above the plane of the free surface of the condensate to be discharged, which fills the larger area (to the right of partition wall 155 in FIG. 14). In the embodiment according to FIG. 14, the heating means 140 have to heat the entire volume of water contained in the smaller area (56) located on the left side of the wall 155. Now, this volume is usually large, depending on the exact amount of liquid that is converted to steam in order to release the condensate under high pressure. To further reduce this volume of water to be evaporated, the 15th
According to other features of this arrangement, shown in FIG. The respective lower and upper parts thereof (thus forming separate steam generators) communicate with the respective lower and upper parts of the main buffer tank 14 , and at least the lower part of the enclosure 157 is located substantially at the level of the lower part of the buffer tank 14 or below that level.

According to the embodiment shown in FIGS. 15-17, the steam generator 140
, 157 is an elongated, e.g. cylindrical, hollow casing or enclosure located within the main buffer tank 14, particularly near its bottom, forming said enclosure 157 and placed horizontally as shown in FIG. for example at least one lower communicating orifice 158 opening towards the free end of this casing and a vertical open communicating conduit 159 extending at 1 from the top of the casing 157 into the upper vapor phase space of the buffer tank 14. The volume of the enclosure 157 is relatively small, and water can enter through the orifice 158 in its lower part, while the steam generated within the enclosure 157 can be passed through the tube. It rises through conduit 159 and escapes through an upper end orifice 160 located near the top of the buffer tank and opening into the vapor phase space of the buffer tank. Cylindrical heating element enclosure 157
For example, as seen in FIG. 15, it penetrates laterally into the buffer tank 14 through the lateral wall at the end of the buffer tank 14.

In the embodiment of FIGS. 16 and 17, internal heating element 14
The cylindrical heating element enclosure 157 with 0 is vertically positioned and can be passed upwardly over the bottom of the lower part of the buffer tank 14 as in FIG. 16 or downwardly across the top of the buffer tank 14 as in FIG. By passing, it penetrates (in a fluid-tight manner) into the buffer tank 14. In a modification of the embodiment of FIGS. 16 and 17, the introduction of liquid into the heating element is via one or several orifices 158' (16 ), or through the open lower end 161 of the heater enclosure 157 (Figure 17), the lower part of which is submerged or immersed in the condensate, while the effluent stream of steam produced in the heater enclosure 157 is 1-! Passes through the upper wall of the enclosure 157 and enters the vapor phase space of the buffer tank 14! ,
or through several orifices 160''e.

In the embodiment according to FIG. 18, the heating means forming the individual straddle autonomous steam generators (consisting of the enclosure 157 and the heating element 140) are placed outside the main buffer tank 14;
The lower and upper parts, respectively, of the enclosure 157 are connected to the corresponding lower and upper parts, respectively, of the buffer tank 14 via conduits 162, 166, respectively. In this embodiment, the heating means are located at a lower level than the buffer tank 14, and a conduit 162 exiting from the lower part of the enclosure 157 penetrates the bottom of the buffer tank 14 in a fluid-shaped manner, inside of which (59) the intermediate The conduit 166 extends vertically at a height substantially corresponding to the aforementioned intermediate liquid level N2 defined by the relative portion of the liquid level controller 151' of the enclosure 1.
57 is connected to the top of buffer tank 14.

In the embodiment shown in FIGS. 14 and 18, the auxiliary buffer tank 105 of the isolation valve 149' has a remote control circuit 150.
', pilot relay 1 with intermediate liquid level controller 151 and associated remote control circuit 153'ffi
The presence of 52' is optional. The operation of these devices is
It is as follows. During filling of the main buffer tank 14, when the condensate therein reaches the upper liquid level N3 (for example, in FIG. Controller 56 is valve 14
2 and 149''e open and the heating means 140 activated.

Due to the heating of the condensate, the pressure in the vapor phase space above the plane of the condensate in the main buffer tank 14 increases, and when a final pressure is reached therein, the condensate passes through the pipe 16 leaving the bottom of the buffer tank 14.
and the self (60) is dynamically pushed out through the check valve 20. In the case of FIG. 18, the condensate in the buffer tank 14 is at the intermediate liquid level N2 at the orifice at the upper end of the conduit 162.
It should be noted that upon reaching and rising above the heating element enclosure 157 is automatically filled by the conduit 162. During discharge, when the liquid level drops to the lower limit liquid level N1-4 in the buffer tank 14, the liquid level controller 53 opens the valve 142 (to reduce the pressure in the buffer tank 14 by discharging steam through the conduit 141). The valve 149"!r is then opened and the discharge stops after the pressures are equalized. The condensate in the upstream system is transferred to the auxiliary buffer tank 105'. The check valve 20' is then temporarily stored in the
(released when the pressure becomes equal)'(il
- re-enter the buffer tank and fill this buffer tank 14 until the liquid level inside reaches the upper liquid level N3,
A new cycle or operation is thus started.

The sequence of operations described above occurs when only one level controller 56 is present in the main buffer tank 14, and the upper limit position N and the lower limit position N1 of its detection member or float are
determine the beginning of the period of condensate heating and discharge, respectively.

According to another aspect, an additional intermediate level controller 151' to the main buffer tank 14 and a pilot relay 15
2"e, the heating means 140 is started as soon as the rising level of the condensate reaches the intermediate level N2, so that the tempo of the periodic cycle, i.e., the repeated intermittent operation, is controlled so that the main buffer tank 14 This can be accelerated by starting the heating of the condensate to be evaporated before it fills the surface N31.

Figures 19 and 20 show another method of creating condensate discharge pressure in the main buffer tank 14 as a variation of the method described above. This method requires that the external tank be under pressure higher than the pressure in the auxiliary buffer tank 105', which may be caused by pressure breaks existing in the system upstream of the gravity return of condensate or by temporarily stored condensate. It is characterized in that it is introduced into the upper vapor phase space of the main buffer tank 14 at the live steam inlet. To carry out this method, the top of the main buffer tank 14 is connected to at least one live steam inlet conduit 162 to a suitable live steam generation or supply source. The pressure of the saturated steam located above the plane of the free surface of the condensate in the closed vessel constituted by the partially filled main buffer tank 14 is thus reduced below the pressure initially present in this vessel. If the pressure is increased by introducing live steam at high pressure, then via a pipe 16 which penetrates into the buffer tank, descending with a trench to a point located close to the bottom of the lower side of the buffer tank for this pressure increase; The condensate can be pushed out from the lower part of the buffer tank 14. In this case, heat is necessarily transferred from the high pressure steam introduced into the buffer tank 14 to the relatively low pressure steam and condensate initially contained within this buffer tank. The live steam inlet conduit 162 includes an isolation valve 166', etc., which is preferably actuated by a motor and connected via a remote control circuit 164 to a level controller installed in the main buffer tank 14. It has a servo motor connected to the troller 56. Valve 166' can also be a manually operated closure, a solenoid controlled valve, a pressurized auxiliary fluid actuated valve or (63) a similar closure provided for high pressure steam access. In addition, the device includes the other accessories already mentioned above, namely one or several conduits 15 through which relatively low-pressure condensate is introduced by gravity; closing elements on each condensate inlet pipe, e.g. Return valve 20' or manually or automatically, remotely or non-remotely controlled closing member (e.g., solenoid valve, motor operated valve, auxiliary pressurized fluid controlled valve, etc.) ; a closing member on the condensate re-introduction pipe 16', for example a check valve 20 or one of the other types mentioned above; An auxiliary buffer tank 105' located upstream of the closing valve 20' at the inlet to the main condensate buffer tank 14 is optional and absorbs incoming condensate while the closing valve 20' is closed. It is intended to be included temporarily. Instead of having a single level controller 56, the main buffer tank 14 can also have several condensate level controllers that control the opening and closing of various closures. The vapor phase connection conduit 141 provided between the confined space located on the horizontal plane of the condensate in the main buffer tank 14 and the condensate gravity return conduit 15 upstream of the closing valve 20' (64) is connected to the conduit 15. The purpose of this connecting conduit is to allow the condensate contained in the main buffer tank 14 to flow under the pressure of the condensate contained in the main buffer tank The aim is to ensure a full direct pressure drop in the main buffer tank 14 at the end of the discharge of the gas, but this connecting conduit can also open to other systems where the pressure is sufficiently low, if appropriate. The closing member constituted by the stop valve 142 above (release by steam discharge) allows steam to be discharged only after the end of the condensate discharge period, and it is for example It can be of the type you use to install it.

Nowadays, said arrangement also includes other usual accessories such as isolation valves for disconnecting various connections, devices for bypassing various closing members, discharge or drain cocks and pipes, manual and Equipped with automatic bleed means.

FIG. 20 shows a modification of the embodiment of FIG. 19, and this (65)
. , where valves 142 and 166' on conduits 141 and 162, respectively, are replaced by a single three-way valve 16 that performs the same function as those 142, 166'.
5 has been replaced.

The operation of this arrangement is as follows. Initially, main buffer tank 14 contains no condensate, valve 142 is open and valve 166 is open.
′ is assumed to be closed. The condensate proceeding by gravity via the condensate take-off conduit or from the auxiliary buffer tank 105' enters the main buffer tank 14 at the one-way closing valve 20''eR, in this case constituted by an inverted valve, and is thus Filling of the buffer tank 14 is started.Buffer tank 1
When the condensate in 4 reaches the upper liquid level N3, the liquid level controller 53 closes the valve 163' on the live steam conduit 162.
is opened and valve 142 is closed at the same time, allowing high pressure live steam to enter the head space of the buffer tank. As soon as the pressure in the buffer tank 14 is high enough, it closes the check valve 20' and stops the gravity flow of condensate. This check valve 20' may be replaced by a shutoff valve remotely controlled by a level controller 56, if appropriate.

As the pressure continues to increase within the confined vapor phase space of the main buffer (66) tank 14, this overcomes the counter pressure present within the condensate discharge system 16, resulting in a The contained condensate is discharged via check valve 20 and pipe 16. The check valve 20 can be replaced with a stop date that is remotely controlled by the controller 53 into an open or closed position. During the condensate release period, the main buffer tank 14 is empty and the condensate level inside it reaches the lower limit or minimum level N1.
When reaching 1. Liquid level controller 56 is valve 1
6 filter and at the same time close the valve 142 on the pressure equalization conduit 141.
The introduction of live steam is cut off by opening the main buffer tank 14, so that the pressure in the main buffer tank 14 is reduced to the upstream condensate intake system 15.
105'. Once this pressure balance is achieved, the check valve 20' is opened so that the condensate proceeding from this upstream condensate gravity return system is free to flow once again into the main buffer tank 14. The maximum liquid level N3 can be filled, and a new operation cycle is thus started.

(67) Compressed gas-powered fluid (compressed air or steam) pumps of the so-called float type are already known in the prior art, and these pumps are generally used as condensate lifting devices, but also as condensate reintroduction devices. It is not used as such. In this known device, the liquid condensate to be discharged is introduced by gravity into the pump body through a non-return valve, gradually raising a float until the float directly closes the relief valve and the inlet valve, For example, open the live steam valve at the same time,
Steam is thus allowed to flow into the upper part of the pump body at a higher pressure than the desired discharge head, on the one hand this pressure holds the relief valve closed, and on the other hand it forces the liquid condensate through the check valve. to propel the condensate, and finally lock the condensate inlet check valve in the closed position. Next, the pump body becomes empty, 71) the comb float descends, the relief valve opens automatically, and the live steam population valve closes at the same time, so the pressure inside the pump decreases and the condensate introduction check valve closes. The condensate thus reenters the pump while the condensate back valve remains closed (68) and a new cycle begins. The steam pump designed in accordance with the invention and illustrated in FIG. 19 has the following advantages over the known pumps just described.

- Since the condensate flow line upstream of the known pump is periodically connected to the external atmosphere, this pump can only be applied to condensate whose temperature is below 95°C. In contrast, the steam pump according to the invention can be used when the condensate temperature is above 100°C, is designed for steam at substantially constant pressure and temperature within the valley system, and is designed for steam at substantially constant pressure and temperature within the valley system, resulting in phase separation, That is, no steam condensation occurs. After all, the known pump can only be operated because the condensate source system is provided with condensate bleeder or drain means. If the live steam reaches the known pump via the condensate inlet passage, the internal float of the pump will not respond and will therefore remain in its lower position, so that the vent orifice present in the upper position will remain open. be. Any steam that can enter the pump via the condensate inlet pipe then escapes through this orifice (69).
, it will hurt. In contrast, the steam pump according to FIG. 19 operates perfectly even when the condensate gravity line contains steam and condensate simultaneously. The entire arrangement is integrated in a completely closed circuit, so no steam can escape.

In one known steam pump, all live steam used to convey condensate under pressure is lost as it freely escapes into the air after completing the required work.

In contrast, in the pump according to the invention, all of the power live steam used for conveying condensate is recovered. Furthermore, in the known pump, the condensate upstream of the pump is necessarily in communication with the open air, so that all the raw steam passing through the bleeder as well as the hot condensate are freed from self-evaporation due to its release into the open air. It is unavoidable that all vapors produced are vented to the atmosphere. In contrast, in the steam pump according to the invention, the pump is installed in a closed circuit plant, so that there is no communication with the atmosphere and no loss of live steam can occur.

(70) - Known steam pumps are applicable only to low pressure plants where the upstream condensate is at the same pressure and temperature as the surrounding atmosphere. In contrast, the novel steam pump according to the invention can be used at any range of pressures (as long as powered live steam at a sufficiently high pressure is available). Furthermore, the maximum condensate discharge head of the known pump is limited to a water column height of approximately 15 m. In contrast, the novel pump of the present invention can be provided with any discharge head compatible with the available powered live steam pressures.

In one known steam pump, the opening and closing of the various successive passageway orifices is mechanically linked to the position of an internal float of the pump. In contrast, the novel pump according to the present invention
It consists of a number of independent components (level controllers, remote control components, etc.) that can be programmed in different ways according to the nature of the problem to be solved.

If the total pressure of the condensate in the main buffer tank 14 has to be discharged to a location higher than the pressure of the powered live steam used for pumping, then according to the method of the present invention and in accordance with feature (71) above, the condensate can be discharged onto the main buffer tank. in combination with the introduction of powered live steam and the aforementioned evaporative heating of at least a portion of the condensate, so as to bring the total vapor pressure thus created in the main buffer tank at least somewhat equal to the required discharge pressure. It is advantageous to do so. In this case, the nuclear main buffer tank is connected at its lower part, for example by a discharge conduit, to a steam generation boiler or to a system of lines at a pressure higher than the pressure of the power live steam, and for this purpose the method is An arrangement in which a variant can be carried out includes said evaporative heating means 140 according to one of FIGS. 8 to 18 and a live steam inlet pipe 162 (according to FIG. 19 or 20) connecting the main buffer tank 14 to a live steam supply source. , thus forming a combined pumping substation.

Such a combined arrangement is advantageously used, for example, in the following cases: Thus, for example, a condensate of less than 2 bar is brought to a location with a pressure of 15 parr and, if the live steam is 14 bar, is used by being pumped (72) with a driving live steam of 14 parr; Live steam is obtained by thermodynamic pumping effect by heating the condensate, i.e. by heating electrically, resulting in a pressure deficit of 1 bar to obtain the required final discharge pressure of 15 bar.

The various aforementioned configurations or components may of course be combined and cooperate with other closed circuit steam systems or networks to reintroduce condensate directly into the boiler. The working fluid is at a substantially or at least approximately constant temperature and pressure everywhere, and is generally excluded from any vapor or condensate bleeders, drains, or similar phase separation devices in the system or network (flow pressure losses and accidental The same is true in all respects (without considering cooling).

Of course, the invention is not limited to the embodiments described above, which are merely illustrative. The technology of the invention is limited only by the scope of the claims.

[Brief explanation of drawings]

FIG. 1 is a circuit diagram including an economizer showing a first embodiment of the present invention, in which a pump sub-section supplies vaporized make-up liquid to a boiler (73) supplied from a supply tank.
. Figure 2 is a modification of the circuit in Figure 1, in which the economizer is not used and two boilers are placed in parallel; Figure 6 is a diagram showing the supply system for the 4 is an enlarged sectional view of only the main buffer tank shown in the figure, showing various characteristic levels described later. FIG. 4 is another specific example of the circuit shown in FIG. Figure 5 shows the transfer for condensate originating from the low-pressure network in the main Ponzo sub-section of the high-pressure network using an auxiliary buffer tank in the low-pressure network connected to the high-pressure network. 6 is an enlarged cutaway view of the interconnected main buffer tank and auxiliary buffer tank system; FIG. 7 is a cutaway view of only the auxiliary buffer tank showing a modified example; FIG. 9 is a longitudinal sectional view of the main condensate collection buffer tank with means for internally heating the condensate, showing the subsections of the thermodynamic pump; FIG. 9 is similar to FIG. 8; However, a thermodynamic pump sub-section is located after the auxiliary pan 7a tank for temporary accumulation of condensate, and discharges pressure (74) from the main pan 7a tank into the auxiliary buffer tank, Figure 10. Figure 11 is a diagram similar to Figure 9, respectively, showing two systems placed parallel to each other and a similar condensate return network; Figure 11 is similar to Figure 9, but with excess condensate discharge means and overpressure discharge. A small enlarged view showing the main buffer tank with means, FIG. 12 shows a rupture of the bi-pipe network of the condensable steam-using device, including a common condensate return conduit with a pitch maintenance pipe riser equipped with a thermodynamic pump. FIG. 13 is a diagram similar to FIG. 12 but showing the installation of a thermodynamic bonder in a single pipe network; FIG. 14 is a modification of the previously described device which heats only the liquid to be vaporized; Figure 15 is a slightly enlarged cutaway view of the main buffer tank showing another example of the principle shown in Figure 14, showing partial partitions of the main buffer tank, with one directly connected to the liquid phase and the other to the gas phase. Figure 16 is a diagram similar to Figure 15 using a connected submersible internal horizontal tubular auxiliary steam generator, with a vertical tubular part partially submerged and resting through the bottom. FIG. 17 is a diagram similar to FIG. 16 showing another specific example of a steam generator, in which the steam generator is partially submerged in water (75) and is placed through the top of the main buffer tank. The diagram showing the apparatus, FIG. 18, is a modification of the principle shown in FIGS. 14 to 17, and is independent from the outside for supplying forced steam to the main buffer tank and extracting the required amount of liquid to be vaporized from the steam. Figure 19 is a cutaway view of the main condensate accumulation buffer tank with an external forced pump steam introduction system, and Figure 20 is a diagram showing the live steam intake valve and pressure shown in the previous figure. FIG. 3 is a partial view of the main buffer tank in which the release valve is replaced by a three-way valve. Explanation of symbols 8... Boiler 10... 4. Supply tank 14... Main buffer tank 37... Liquid level detection control device patent applicant Vinyl Euchene Legamée
Sankiyokamo's attorney Patent attorney Kyoji Yuasa U1 (1 other person) (76) 3ri pL -271η9-11 Procedural amendment Showa year//month/day 1, case indication Showa, ((year patent application no. 161 soup No. 2, Name of the invention 6t いみJ仝唄(S 6, Relationship to the case of the person making the amendment Patent applicant's address - (Name (0nee1shi・1-shi"k-fu)・
-4, Agent 5, Specification writer who typed the subject of amendment 6, Contents of amendment ℃晧 Corebori procedure amendment (method) % formula % 1, Display of case No. 4, 1929 Application No. i71. /g evening number n L i 4
Relationship to the case of the person making the amendment to Kui Fubok 6. Applicant Address AJ Fan V-0 Ale, 1 - Seane Luker 4, Agent

Claims (1)

[Claims] from a condensate discharge and return line to at least one steam-using condenser, at least one steam-generating boiler, and at least one condensate storage main buffer tank connected to each boiler by at least one direct reintroduction line system; at least one supply tank for a new vaporizable liquid supply connected by at least one supply conduit to a buffer tank; and a guided power-driven supply pump and a new vaporization system. a closed system comprising: said supply conduit having automatic control means for the supply of available liquid; and said control means being in slave relation to the existing amount of available condensate water in the buffer tank. A steam generation and distribution device comprising at least one re-introduction piping system.
two main driven continuously operating force pumps maintained under static pressure by a van-a-tank such that the force pumps together with a buffer tank form the main pumping substation, and at least one automatic control valve reintroduced in series. The servo motor is mounted on the piping system and its servo motor is connected to the remote control circuit to the liquid level control device of the boiler, and the permanent leakage conduit is connected to the re-introduction piping system between the main pump and the automatic control valve. A closed system steam generation and distribution apparatus characterized in that the system communicates with a main buffer tank and a leakage conduit opens after the supply pump into one of the supply conduits and one of the top of the main pan tank.