CS266824B1 - Method of controlling heat supply - Google Patents

Abstract

A method for regulating the supply of heat to a consumer and/or a consumer area with heat consumption in steam, where the energy source supplies heat in hot water and the transfer station is equipped with a steam source, e.g. a steam releaser or a steam generator and a thermocompressor arranged downstream of it. The regulation is carried out qualitatively, i.e. by changing the temperature of the heat transfer medium, and/or quantitatively, i.e. by changing the flow rate of the heat transfer medium supplied to the steam source. This change in temperature and/or flow rate of the heat transfer medium is preferably carried out upstream of the steam source. It can also be carried out on the inlet heat transfer medium, by separating it from the steam that is generated and compressed in the compressor, for example by an exchanger wall.

Description

The invention relates to a method of regulating the supply of heat to consumers and/or a consumer area with heat consumption in steam, where the energy source supplies heat in hot water and the transfer station is equipped with a steam source, e.g. a steam releaser or a steam generator, and a steam compressor arranged downstream of it. The field of application of this method is the operation and economic regulation of a steam compressor, i.e. a compressor, or rather a compressor unit for compressing and simultaneously superheating water vapor. This process, so-called thermocompression, can be used primarily for the purposes of energy, heating and in various industrial technologies in ensuring and rationalizing heat consumption.

The working principle of a thermocompressor is usually significantly different from the known operation of a classic compressor operating in a typical compressor or exhauster mode. This is due to the fact that the considered thermocompressor is significantly influenced by the behavior, i.e. the characteristics of the upstream and downstream elements of the technology, which ensure the production of the sucked-in, usually almost saturated steam and the use of the superheated steam processed in the compressor. There are essentially two exceptions. In the first case, the compressor processes waste, cooled steam from industrial technology, e.g. from large forges or metallurgical operations, which is usually led into large collectors, so its parameters, i.e. pressure and temperature, are essentially constant, the ratios at the discharge are determined by the classic compressor characteristic of the machine. Processing of a variable amount of steam according to the intensity of the technological process, i.e. e.g. differences in operation in the first and second shifts, is then done from the compressor's point of view by regulating the flow rate of the working medium, i.e. steam, by conventional means. In the second case, usually slightly overheated steam from a steam pipeline is processed, through which it is supplied from an energy source to a common need, e.g. heating, industrial technology, etc., at a certain pressure and temperature level, which usually changes during the year, i.e. in the summer-winter period, with winter parameters being higher. A single consumer requiring technological steam with a higher and usually permanently constant pressure and temperature level will then advantageously use a thermocompressor to pressurize the supplied steam to the required parameters. The characteristic of such a compressor will then be exhaust, or the conditions at the machine's discharge will be almost or completely constant, while the conditions at the suction will vary within a certain range. However, these and similar cases are characterized by the fact that the volume, i.e. the vessel, collector, steam pipeline, etc., from which the compressor sucks, is usually quite large and, in addition, steam is not created in this volume, i.e. it does not develop, but is supplied to it and has given parameters.

The main disadvantages of the above facts are that the situation changes completely when the final volume vessel from which the thermocompressor sucks is also an element where steam is produced from its liquid phase, i.e. water or an aqueous or other solution. This is the case of a steam generator, i.e. a steam generator, an expander, i.e. a releaser, but also elements of various technologies, e.g. in the food or chemical industry, such as an evaporator, a brewhouse, etc. Connecting such a device with a compressor and a downstream appliance of processed steam, i.e. the next stage of the technology, steam central heating, production of hot service water, etc., essentially creates a system of a high-potential, i.e. high-temperature heat pump, or cooling device. This means that the input vessel in which the steam is produced and from which it is sucked by the compressor performs the function of an evaporator here, the appliance of the processed steam then behaves as a condenser, even if condensation does not occur. The circuit of this heat pump will usually be open, or possibly closed via other elements of the technological equipment. The essential fact here is that the compressor for compressing steam, connected in the system of the mentioned high-potential heat pump, will not behave at all like a conventional compressor. Moreover, its connection to the circuit can be quite diverse, namely, if it is an aggregate with multiple bodies, i.e. sections. In such a case, in order to reduce the input of mechanical work for driving the compressor, intercooling can be used, similar to air or other machines, which in this case is however solved as suction, i.e. injection of the liquid phase of the working medium, usually water, either directly into the machine body, connecting pipe, or into a separate container between the bodies. This will release another part of the saturated steam at the expense of cooling the already processed, superheated steam. Such intercooling is naturally the most energy-efficient, because no thermal energy is removed from the system and subsequently wasted, e.g. in a cooling tower. An even more advantageous situation will occur where it will be possible to use the so-called cascade connection.

CS 266 824 Bl with two or three evaporation temperatures, which also has its analogue in refrigeration technology. The advantage of this connection is primarily a significant reduction in the power consumption of the compressor drive, because the thermal potential from the source, that is, from the supplied hot water, is released and processed gradually, which is thermodynamically more advantageous.

parameters, t].

^{where G} prot Aí where i _D

However, even a simple, single-body compressor without intercooling will, as mentioned, behave differently than a classic machine operating in a typical compressor mode. The essence of this fact is that the real goal of the thermocompressor from the point of view of the operator's needs is not to ensure the suction, compression and delivery of a certain volume of the working medium, in this case water vapor, but to deliver a certain amount of heat, processed to the required thermodynamic .ak and temperature. This amount of heat is given by the relationship = ^G prof ^Δί <

is the delivered mass of steam at the compressor discharge, is the difference in enthalpies, i.e.

Ái = i _D - i _in (2) is the enthalpy of the supplied steam is the enthalpy of the returning steam or condensate, i.e. the enthalpy of the outgoing working medium, which has transferred its energy.

However, the compressor works on the basis of its basic relationship, i.e. the characteristic, given by the relation of the pressure in the discharge, or compression, to the volume of the medium sucked in. However, this means that when the operating point of the compressor changes, e.g. by the intervention of the damper in the machine discharge, or by changing the load of the downstream steam consumer along the characteristic, the compressor's absorption capacity will change. The compressor is therefore able to suck in a different amount, i.e. the volume of the medium, i.e. steam, than the inlet evaporator delivers. If the aim of this principle is not to maintain the compressor's operation permanently at a single operating design point, the evaporator must adapt to this change, i.e. it must release the same amount, i.e. the volume of the medium, which corresponds to the compressor's absorption capacity. With a constant process in the evaporator, i.e. a constant amount of heat supplied, or heat transfer medium with given parameters, there will be a change in the parameters, i.e. pressure, temperature and density of the generated steam, such that its quantity, i.e. volume, corresponds to the compressor's absorption capacity. In practice, this means that when the suction volume decreases, the pressure and therefore the temperature of the saturated steam will increase. The suction mass will also decrease, but less than the volume, because it is given by the relationship ^G s ^{+ Q} s' ^p s ⁽³⁾ where G _s ^Q s

- Ps is the suction weight, is the suction volume and is the vapor density, and the vapor density will increase with increasing pressure and vice versa. The result will be that the actual characteristic of the thermocompressor will only pass through the design point of the typical compressor characteristic, but it will be much steeper. This applies to the simple case of a single-shell compressor; the analogous characteristic of a multi-shell compressor with intercooling, i.e. suction, will be even steeper. A much more pronounced steepness will also occur in the characteristic of a multi-shell compressor in a cascade connection.

From the above it is clear that for the design and construction of a thermocompressor it is not enough to know only the parameters at the design point, but it is also necessary to specify the characteristic of the inlet evaporator, i.e. the dependence of the steam pressure in the suction on the volume of steam in the suction, or the steam pressure in the suction on the mass sucked into the compressor suction. From this it also follows that for two identical cases of design states, but different courses of the steepness of this input characteristic, it may be necessary to design two different machines.

CS 266 824 Bl

These facts provide basic knowledge for thermocompressor control. Analysis of the use of thermocompressors, especially in district heating, results in requirements for an exceptionally wide range of control of the heat supplied in steam, i.e. also the mass of steam supplied. It is usually necessary to take into account the range

G _p = (20 Ť 120) %.G _{p náv} ⁽⁴⁾ where GPG < p nav is the mass of steam sucked by the compressor and is the design mass of steam sucked by the compressor, while the pressure of the supplied steam is required to be almost constant or to increase somewhat with increasing quantity. A similar situation occurs in industrial technologies, where the required control ranges are not so large, but as a rule it is required to maintain a constant steam pressure in the entire regulated range of supplied quantities. It is impossible to ensure such ranges of continuous and loss-free control in a single unit using conventional means of control, e.g. by changing the flow part of a radial turbocompressor by turning the distributor or diffuser blades, therefore it is assumed that several devices are connected in parallel and the basic, i.e. rough control is ensured by the number of working machines. However, when continuous control of the mass of supplied steam is required, this still means ensuring control of approx.

G _s (50 4 110) %.G _{S náv} (5) where G is the intake mass and ^s G , is the design intake mass.

with the name ^J

This case corresponds to the worst-case mode from a control perspective, when two units reduce their output so that one can be shut down and only one will continue to operate, while the remaining unit will operate at full output, or vice versa.

However, with few exceptions, classic methods of regulating a turbocharger or turbocompressor assembly completely preclude the achievement of such control ranges. For regulation, throttling in the turbocompressor intake, regulation by changing the drive speed, or regulation by changing the flow section is usually used.

However, there are few possibilities in this regard for a thermocompressor, i.e. a compressor for compressing steam. Regulation by throttling in the suction is possible in principle. Moreover, the throttling phenomenon is characterized as an isoenthalpic process, i.e. the saturated steam sucked in will pass through throttling to a state of lower pressure and temperature, but overall to a state of slightly superheated steam. However, this is only a theory, considering only the states before and after the throttling element. The actual course of throttling is different and can lead, and this is essential, to a local excess of the saturation limit, i.e. even to the formation of a liquid phase. However, this liquid phase does not evaporate immediately during the further throttling process. A heterogeneous mixture of slightly superheated steam and water droplets of a significantly smaller volume is formed. The result may be, especially if the compressor operates with a smaller amount in the suction, i.e. near the pumping limit, that the machine quickly reaches the operating point up to the pumping limit, which leads to the intervention of the anti-pumping protection and the inability of further steady operation of the machine. In addition, there will be a significant loss of thermal energy in the entire system due to throttling, which is fundamentally undesirable. The erosion effect of water droplets on the elements of the flow part of the compressor cannot be ignored. Regulation by changing the drive speed is in principle possible. A change, e.g. a reduction in speed at a constant input technology mode, however, will also cause the already indicated change, e.g. an increase in suction pressure, so the actual decrease in the sucked-in steam mass will be small. The thermal output and power input of the compressor will therefore decrease slightly, but the power of the drive unit will decrease very significantly with a decrease in speed, e.g. in the case of a steam or gas turbine. The resulting control characteristic will therefore be both very steep, which is undesirable, and also very narrow and limited. In reality, however, it must be taken into account that a constant-speed electric motor must be considered for driving the thermocompressor. Use of a steam turbine to drive compression equipment

CS 266 824 Bl steam will be used only exceptionally in some technological applications or in existing heating plants, and it will probably be the same with a combustion turbine drive. Regulation of a steam turbocompressor by changing the flow section is in principle the most effective. However, as already mentioned, changing the compressor absorption, even by interfering with the flow section, causes a change in the conditions in the upstream evaporator, i.e. also in the compressor suction. The result will again be that a significant change in absorption, i.e. the compressor suction volume by adjusting the distributor or diffuser row of blades in a radial turbocompressor, or by changing the setting of the stator blades of an axial turbocompressor, will cause a corresponding change in pressure in the upstream apparatus, e.g. the evaporator. The result will be that the change in the suction mass will be only very small, i.e. the total change in the supplied heat will also be small.

The main disadvantages of known solutions are that the regulation of the thermocompressor by classical means will be only slightly effective and it will definitely not be possible to achieve the expected, in this case very large, regulation ranges of the machine. The reason is that there is a very close connection between the work of the compressor itself and what happens in the upstream and downstream technology, from the point of view of the purpose of the thermocompressor, it is therefore the case that there is a certain heat flow in the entire system, i.e. a certain amount of heat is transferred from one element to another via heat transfer substances for a given period of time. The function of the thermocompressor here is that this heat in the form of sucked saturated steam of given parameters is received, processed and transferred to another element of the system, while the processing of the said heat consists in increasing the thermodynamic potential, i.e. enthalpy and partially increasing the value of the amount of heat, all at the expense of the mechanical work input. Assuming that the amount of heat removed from the upstream element of the system is almost constant and the preceding technological process operates with constant inputs, it is not possible for the intervention of another element, i.e. regulation of the thermocompressor, to significantly influence the passage of this heat flow through the compressor. It follows that regulation of the heat supplied by the compressor to other elements of the technology will be possible only to a very small extent under these conditions.

The invention aims to essentially eliminate the above-mentioned shortcomings and ensure economical regulation of the steam compressor.

The essence of the control method according to the invention is that the control is carried out qualitatively, that is, by changing the temperature of the heat transfer medium, and/or quantitatively, that is, by changing the flow rate of the heat transfer medium supplied to the steam source, whereby this change in temperature and/or flow rate of the heat transfer medium is preferably carried out upstream of the steam source. It can also be carried out on the inlet heat transfer medium, separated from the steam generated and compressed in the compressor, e.g. by an exchanger wall. The control in the above-mentioned manner can be carried out either completely or at least to a decisive extent.

The main advantages of the solution according to the invention are that changing the amount of heat passing through the entire system will enable very good, extensive and economically advantageous regulation.

The invention is explained in more detail below with reference to exemplary embodiments in conjunction with the drawings.

Fig. 1 shows the control characteristics of the thermocompressor, Fig. 2 shows the diagram of the heating circuit when the thermal output is changed by qualitative control of hot water in the source, Fig. 3 shows the diagram of the heating circuit when the thermal output is changed by quantitative control of hot water in the source, Fig. 4 shows the diagram of the heating circuit when the thermal output is changed by combined, i.e. both qualitative and quantitative control of hot water in the source, and Fig. 5 shows the diagram of the heating circuit when the thermal output is changed by combined control of hot water in front of the compressor station.

From the point of view of the compressor, whose reference parameter is, among other things, the suction volume Q _g , not the direct suction mass G _s , this means that while maintaining a slightly changing suction volume Q$ within the characteristic range, the processed suction mass G _{s of} the working medium and therefore the amount of heat supplied in the steam can change quite significantly, if proportionally

CS 266 824 Bl changed the sucked mass G _g , the steam pressure in the suction of the thermocompressor P _g and therefore other thermodynamic parameters of the medium will also change. A state similar to the throttling of the machine will then be created. Unlike throttling, which is a phenomenon associated with losses, there will be no losses here, because the compressor will be regulated by the entire system, i.e. by the amount of heat, i.e. thermal energy, passing through the element upstream of the compressor, e.g. the evaporator. This amount of heat can change very significantly with respect to the properties of the technological elements, while the actual sucked volume Q _g at the suction of the compressor may change little or not at all. The regulating element of the system that will control the compressor in this way can be diverse and again depends on the properties of the technology being operated.

When producing heating and technological steam from hot water, for example in an expander or steam generator, and its subsequent compression in a thermocompressor, this can be done by regulating the amount of hot water supplied by a conventional control valve or by regulating the supplied water, i.e. the temperature, and thus reducing the proportion of steam released either by mixing it with colder water or directly by supplying and withdrawing colder water from the energy source, e.g. as part of regulating this source in the summer-winter period, or during the day. It is also possible to regulate the intensity of the ongoing technological process in the upstream element of the technology by reducing the supply of heat and other media to this element and/or by reducing the temperature, i.e. the pressure, at which we operate this process.

In reality, however, the operating point of the compressor on the characteristic will change, because the suction pressure will change, but the discharge pressure P _v , passing through the design point NB, will usually be required to be constant. This can be seen from Fig. 1, where the diagram shows the discharge pressure P _v and the suction weight G _g , showing the network of classical compressor characteristics and the actual characteristics of the thermocompressor at the design amount of heat $ ^náv where q is the amount of heat and q _n á _v is the designed amount of heat and at non-design values , qj, where ^l ^náv'

In this case, the thermocompressor will be regulated along the line p = P , = const.

vv náv (6) $2 ^náv where P _v p

v náv is the pressure at the discharge and is the design pressure at the discharge, and the actual regulation will be implemented by the regulating body on the upstream element of the technology. The design point NB of course also corresponds to the design suction weight G _{g náv} · The figure also shows the pumping limit PH, the exhaust limit MO, the compressor characteristics KOP for constant suction steam pressure P _gi and the actual characteristics KC of the thermocompressor. The actual regulation range SR is also shown here.

If regulation along the characteristic were also required, i.e. setting a non-constant pressure at the discharge P _y , this operation would be ensured either by changing the resistance characteristic of the downstream consumer, or by a conventional control damper in the discharge of the thermocompressor.

However, it follows from the above cases that the above-described, considerably steep characteristic of the thermocompressor is in fact, from the point of view of regulation, considerably advantageous, because it enables regulation at a constant discharge pressure P _y over a considerable range of flow masses and therefore also the intensity of the operated technology, i.e. the heat supplied, and regulation at a changing discharge pressure P _v over a considerable range at an almost constant intensity of the operated technology.

CS 266 824 Bl Let us now consider a much more general system, including not only a system with a thermocompressor and consumer technology, but also its own, often quite remote, energy source with its respective connections.

When describing the entire thermodynamic cycle, the heating method of heat supply using steam from the steam-water network PS and hot water from the hot water network HS in the conditions of combined production of electricity and heat (Fig. 2), it is shown that in a system where the regulation of heat supply to the consumer is implemented by changing the temperature of the heat transfer medium, e.g. the temperature of hot water in the energy source E, the thermodynamic efficiency of the entire system is almost constant, provided that the change in the temperature of the heat transfer medium causes a lower or higher pressure of the generated saturated steam in the suction of the thermocompressor Kp. During the above heat transformation, the total loss of mechanical energy of the heating circuit practically does not change, as follows from the relations below. The nominal state is given by the relation (9) where ·\) vc 9 E óc $KS is the total specific loss of mechanical energy in the system, is the specific loss of mechanical energy in the source, is the specific loss of mechanical energy in the pumping station and is the specific loss of mechanical energy in the compressor station.

The state during regulation is given by the relation = 9; +P _e '+i) _K ;, (10) assuming that where q _e ^Q P ^q hv are the differences $E $E' $P %' is the temperature from the energy source, is the heat consumption in steam and is the heat consumption in hot water, ^q hv ^q hv ^; C (11) >0;AÍ) _KS = Ό - i) ' Z o £i £j £ι ΛΡ ΛΟ X\D (12) and in qualitative regulation it is valid that (13) which implies that (14)

In this schematic diagram (Fig. 2), as well as in the following figures, the steam circuit is indicated by a thick line, the hot water circuit by a thin line and the steam condensate circuit by a dashed line for clarity. Also shown are the pumping station C, the steam generator GP, the steam releaser UP, the throttle control element š, the steam heat consumer and the hot water heat consumer S _HV . The mass flow of hot water in the heat pipe G is constant in this case, as is the steam pressure in the compressor discharge P^, the temperature of the return condensate T _v „ and the efficiency of the compressor _{M v} . The temperature of hot water in the supply branch of the heat pipe T„„ varies within certain limits from the nominal value to the minimum value, as does the steam pressure at the compressor inlet P„ and the temperature of hot water in the return branch of the heat pipe T„„_. The —b ^— JtlVK temperature of hot water in the return branch of the hot water network T„- _n and the temperature of water in the hot water network T _tt _ are also indicated. ' “HoK —HS

CS 266 824 Bl

In this case, for example, a lower temperature of the heat transfer medium causes a lower specific loss of electrical energy in the energy source E, due to the lower temperature at the inlet to the transport heat pipe and greater cooling of the return water, i.e. the heat transfer medium, which to a certain extent compensates for the increased requirements for the specific consumption of mechanical energy of the thermocompressor K _p at a higher relative steam compression, when the outlet steam pressure is required to be constant. The thermodynamic efficiency of the compressor during regulation almost does not change, because the transported volume of the sucked steam changes only to a small extent.

From the energy point of view, that is, the total loss of mechanical energy, the above-mentioned control method is therefore advantageous mainly in heat transport, when the distance between the energy source E and the transformation compressor station KS is relatively small. At a greater distance of the energy source E from the compressor station KS, it is appropriate to use quantitative control directly in the energy source E at a constant temperature of the heat transfer medium (Fig. 3), because the increased specific consumption of mechanical energy, i.e. the work of the thermocompressor K _p is then compensated by a change, i.e. a decrease in the amount of pumping work of the heat transfer medium in the heat pipe between the energy source E and the compressor station KS. In this case, the nominal state is again given by the relationship (9). '

The state during regulation is given by equation (10), assuming that $e °e ^{! q} p Qp ^{; q} hv ®hv ^; Te Ve t ¹ · ⁵ ' where Q _£ is the heat of the energy source,

Qp is the heat consumption in steam and q _hv is the heat consumption in hot water, there are differences

- ^v 'c>^{0; Δν} κ _Ξ = ^S -^KS< ° (16) and in quantitative regulation it is true that ^<17) which implies that relation (14) is valid again.

The described embodiment differs from the previous example in particular in that the temperature of the hot water in the supply branch of the heat pipe T^ is constant here and, conversely, the mass flow of hot water in the heat pipe G varies within certain limits from the nominal value to the minimum value. The other parameters either remain constant or vary in the same way as in the previous embodiment.

The most advantageous regulation for remote heat supply in a hybrid or steam heating system in terms of total mechanical energy losses is combined, i.e. both qualitative and quantitative regulation of the heat transfer medium in the source E (Fig. 4). This method of regulation saves not only the absolute loss of electrical energy in the source E, but also the mechanical work in the pumping station C of the heat pipeline. In some cases, the combined method of regulation can not only compensate for the increased gain in mechanical energy, i.e. the work of the thermocompressor K _p , but can also reduce the total relative loss of mechanical energy of the entire system than occurs during nominal operation, as can be seen from the relations below.

The nominal state is again given by equation (9) and the state during regulation by equation (10).

Assuming that ^Q E > ^Q E ^{! Q} P ^{7 Q} P ^{! Q} HV > ^Q HV (18)

CS 266 824 Bl where Q _e is the heat of the energy source,

Qp is the heat consumption in steam and

Q _hv is the heat consumption in hot water, the differences are '

A^e ⁼ ^e^e ⁼ c °'^^ks ⁼ ^ks ”^ks ⁰ < ¹⁹ >

and in the case of combined control it is true that (20) XU L. ΛΟ which implies that

( ₂₁ ⁾

In the given case, the steam pressure at the compressor outlet is again constant, the temperature of the return condensate T _v _ and the compressor efficiency j _v . The temperature of the hot water in the supply branch of the heat pipe and the mass flow of hot water in the heat pipe G change here within the limits between the nominal and minimum values.

It therefore turns out that even the regulation of heat supply when adjusting the parameters of the heat carrier before the steam generator GP is not entirely optimal, whether it is quantitative regulation, i.e. by passing the heat carrier medium into the return branch of the heat pipe, or combined with a simultaneous reduction in the temperature of the heat carrier before the steam generator GP according to the diagram in Fig. 5. In any case, from the point of view of the entire energy system, this is a regulation that is also lossy and shows increased consumption of mechanical energy in the compressor station KS. The advantage of this device is the readiness of the regulation, which can be used during rapid changes in the load of the heating system, or when it is necessary to quickly limit the consumption of mechanical work of the compressor station KS. However, even in this case, quantitative regulation of the mass flow of hot water through the heat pipe will be advantageous. By reducing the flow rate, not only part of the mechanical work in the pumping stations C is obtained, but also electrical power in the energy source E and in the compressor station KS with reduced heat supply to the steam and hot water systems, as can be seen from equations (9) and (10).

provided that

Q _e >Q-; Q _p >q;> Q _hv > Qh _V ; G ⁺ > G- (22) where Q _e is the heat of the energy source,

P _p is the heat consumption in steam,

Q„„ is the heat consumption in hot water and

HV

G ⁺ is the mass flow of hot water in the heating pipe, it will be =M _e - /' 4 0; VA)) = V - y- 0 (23) from which it follows that with combined control it will be

S)é-^c· ⁽²⁴⁾

A somewhat more demanding regulation of heat supply to a hybrid or steam system is provided by a compressor station system with a cascade connection of steam releasers with compressors. Here, a flow of hot water between the individual releasers is necessary during qualitative or quantitative,

CS 266 824 Bl or combined controls can be partially regulated directly in the compressor station in order to maintain the balance of the system load of individual bodies, i.e. stages or sections of the compressor unit when changing the heat supply.

Better control conditions for heat supply occur when steam generators, e.g. steam generators, steam transformers, etc., are used for steam generation in the system instead of steam releasers, where on the side of the primary heat transfer medium in the steam generator, medium control can be implemented in a ^single -phase state of the heat transfer medium.

To a certain extent, this advantage can be used in a cascade system of connecting a compressor station, where we use classic steam generators as upstream steam generators and steam releasers will be used as the last or next in the cascade series, where regulation will be carried out by throttling the heat transfer medium, i.e. hot water at a two-phase outlet.

In this case, the thermal potential in the suction of the low-pressure compressor body is not lost due to heat transfer in the exchanger part of the steam generator and the consumption of mechanical energy in the compressor station is saved. At the same time, the main regulation of the entire cascade system is carried out by a single regulating organ, the steam releaser.

The control method according to the invention can be characterized in a simplified manner, firstly, for the case where the heat carrier in front of the steam releaser and the generated steam are the same environment, so that either qualitative control or quantitative control is performed.

Qualitative regulation is carried out by changing the temperature of hot water before the steam release UP and reducing it to a lower pressure by the throttle control element S into the steam release UP, where saturated steam is generated with the required steam pressure in the suction P of the thermocompressor K , . 8 p which is sucked in and compressed by the thermocompressor Kp to the steam pressure for the steam system, i.e. the heating consumer network and industrial technology. This method of regulating the system of the steam release

UP and thermocompressor Kp is characterized by the fact that the change in the heat supply in the steam varies over a wide range due to the change in the specific gravity of the saturated steam in the vapor releaser UP and in the suction of the thermocompressor Kp, while the suction volume either does not change or changes only to a small extent. For this reason, the thermodynamic efficiency of the compressor also changes only slightly.

Quantitative regulation of the flow rate of hot water at a constant temperature is carried out before the steam releaser UP and its reduction to a lower pressure is carried out through the throttle control element š into the steam releaser UP, where the generated system steam with the required pressure P _g of steam is created in the suction of the thermocompressor κ , which is sucked in and compressed in the thermocompressor K .

P P

Combined regulation is created by combining the above-described regulation methods.

In the second place, a method of regulating the supply of heat to a system for generating and treating steam in the form of a GP steam generator, for example a steam generator, a steam transformer, etc.

and thermocompressor K^ where the input heat transfer medium on the primary side of the steam generator

GP may not be the same substance as the emerging and subsequently compressed steam, because it is separated by the exchanger wall and where the actual control processes of the entire system take place mainly on the side of the input heat transfer medium and the steam circulation parameters are a response to these control processes, which can be simply characterized in the second order by the control methods listed below.

Through qualitative control of the primary environment, i.e. by changing the temperature upstream of the steam generator GP. The response on the secondary steam side of the steam generator GP and in the thermocompressor Kp is analogous as described in the previous qualitative control of the first order and the regulation of the heat supply is conditioned by the change in the saturated steam pressure at the suction of the thermocompressor K^.

By quantitative control of the primary medium at constant temperature, either upstream or downstream of the GP steam generator. The control response on the secondary side of the steam circuit is the same as described for the previous second-order qualitative control.

CS 266 824 Bl

Through combined regulation of the primary environment, which is a combination of the qualitative and quantitative second-order regulation described above, with the same effect and procedure.

The systems for regulating the generated steam of the second order are suitable for use in operations where it is not possible to mix the primary temperature environment with the steam of the secondary circuit and where finer regulation is expected, because the regulation of the primary environment can be implemented in a single-phase state of the environment. The disadvantage of this system is a somewhat higher specific consumption of mechanical work of the compressor compared to the solutions described in the first order.

For the case of heat supply regulation in a heating system in the form of an energy source E, for example with combined production of electricity and heat, a pumping station č and a heat pipe, a compressor station KS with a steam releaser UP and a thermocompressor K _p , a steam and hot water network, the control method according to the invention can be characterized in a simplified manner in the third order by the control methods listed below.

By qualitative regulation, i.e. by changing the temperature of hot water in the energy source E and reducing it to a lower pressure by the throttling element š to the steam releaser UP, where steam is generated with the required regulated steam pressure in the suction of the thermocompressor K _p , which is sucked in and compressed by the steam thermocompressor K _p to the steam pressure for the steam heating network or industrial technology. The expanded hot water from the steam releaser UP is discharged into the hot water heating network (Fig. 2), or for other technological needs. The course, procedure and effects of regulation in the compressor station KS are similar to those of first-order qualitative regulation, with the only difference being that the qualitative adjustment, i.e. the change in the temperature of hot water, is carried out in the energy source E. The above-mentioned method of regulation is characterised by the fact that in the case of heat supply from the energy source E with combined production of electricity and heat, the total loss of mechanical energy of the entire system practically does not change even with variable heat supply, because the difference in mechanical energy for the thermocompressor K _p is compensated by the change in the lost electrical energy in the energy source E.

Quantitative regulation, i.e. by changing the flow rate of hot water and, at its constant temperature at the outlet from the energy source E, by reducing it by the throttle control element S to a lower pressure in the steam releaser UP. The generated steam with the required pressure P _g in the suction of the thermocompressor K is sucked in and compressed by the thermocompressor K in the same way and with the same effects PP as stated in the qualitative regulation of the third order. Also, the heat distribution in the steam and hot water network is similar to that in the qualitative regulation of the third order, according to Fig. 3. In the case that the energy source E is at a greater distance from the compressor station KS, then when regulating the amount of heat supplied, the total difference in mechanical energy in the entire system practically does not change, because the change in mechanical energy consumption by the thermocompressor K _p is largely compensated by the change in pumping work for transporting hot water through the heat pipe. However, when the flow rate is reduced, the relative heat losses in the heat pipe are greater compared to the above-mentioned qualitative regulation of the third order.

Combined regulation of hot water in energy source E, i.e. by changing the temperature and mass flow rate of hot water, which is created by combining both of the above third-order solutions. The design scheme is shown in Fig. 4 and the procedure and effects of regulation are similar, as already mentioned in the qualitative and quantitative third-order regulation method. This solution is the most effective and is characterized by minimal mechanical energy losses during heat supply.

Furthermore, in the fourth order, there are still possible variants of heat supply regulation in the heating system by cascading the steam releasers UP and thermocompressors K _p in the compressor station.

KS, where the heat carrier in front of the UP steam releaser and the generated steam are the same environment.

The control methods are identical for a separate implementation to the previously briefly described first-order control methods, in connection with the entire system, i.e. with the energy source E, the heat pipe and the consumer network, they are identical to the previously simplified characterized third-order control methods.

CS 266 824 Bl

In addition, in the fifth order, there are possible methods of regulating heat supply in a heating system with a cascade connection of steam generators GP and thermocompressors K^ in the compressor station KS, where the heat transfer medium on the primary side does not have to be identical to the generated steam for the thermocompressor K^. Variant methods of regulating the primary side of the steam generator GP are carried out before the first steam generator GP either by qualitative, quantitative or combined regulation, for a simple implementation according to the simplified characteristics listed in the second order, in connection with the entire system, i.e. with the energy source E, the heat pipe and the consumer network according to the simplified characteristics listed in the third order.

Finally, in the sixth order, there are possible variants of heat supply control in a heating system with a cascade connection of a compressor unit in the form of a steam generator GP and a thermocompressor Kp with a connected steam releaser UP, where the primary heat carrier is identical to the generated steam. Variant control methods on the primary side of the steam generator GP are performed before the first steam generator GP either by qualitative, quantitative or combined control, for a simple implementation according to the control methods characterized in the second order, and in connection with the entire system, ~ i.e. with the energy source E, the heat pipe and the consumer network, according to the control methods simply characterized in the third order.

Claims (7)

OBJECT OF THE INVENTION A method of regulating the heat supply to a consumer and / or a consumer area with steam heat consumption, wherein the energy source supplies heat in hot water and the transfer station is equipped with a steam source, for example a steam release or steam generator, and a thermal compressor arranged behind it. that the control is performed qualitatively, i.e. by changing the temperature of the heat transfer medium, and / or quantitatively, i.e. by changing the flow weight of the heat transfer medium supplied to the steam source. 2. The method according to item 1, characterized in that the control is performed before the steam source by changing the temperature of the hot water before the steam source. 3. The method according to item 1, characterized in that the control is performed before the steam source by changing the flow weight of hot water at a constant temperature before the steam source. 4. The method according to item 1, characterized in that the control is performed before the steam source, both by changing the temperature and by changing the flow weight of the hot water before the steam source. 5. Method according to one of items 2 to 4, characterized in that the control is performed by a steam source, for example a steam generator, on an inlet heat transfer medium separated, for example by an exchanger wall, from the steam generated. 6. The method according to item 1, characterized in that the qualitative and / or quantitative control is carried out before the steam source already in the energy source, for example in a conventional or nuclear power plant. 7. The method according to item 1, characterized in that the control is performed remotely.