EP2951420A1

EP2951420A1 - Facility with a gas turbine and method for regulating said facility

Info

Publication number: EP2951420A1
Application number: EP14703056.3A
Authority: EP
Inventors: Khalil SAIKALY; Benjamin LAULAN; Damien MENARD; Delphine THOREL; Sofiene KACHROUDI
Original assignee: Dalkia SA
Current assignee: Dalkia SA
Priority date: 2013-02-04
Filing date: 2014-02-04
Publication date: 2015-12-09
Also published as: FR3001768B1; US20150369129A1; FR3001768A1; RU2015133940A; WO2014118384A1

Abstract

The invention concerns a facility with a gas turbine, comprising: - a refrigerating machine (100) comprising: ° a high-pressure circuit (110) with a generator (114) supplied by a pump (112) and subjected to a heat source, ° a low-pressure circuit (120) with an evaporator (108) supplied by an expansion member (106) and forming a first cold source, ° an intermediate-pressure circuit (130) with an ejector (102) and a condenser (104) positioned downstream from said ejector (102), - a gas turbine (200) with a compressor (202), in which the air supply conduit (210) of the compressor is subjected to a cold source and the exhaust gas conduit (212) belongs to said heat source. Application to the production of electricity by stationary co-generation.

Description

The present invention relates to the field of gas turbines and in particular to improving the energy efficiency of installations with a gas turbine. In particular, but not limited to, the present invention relates to the production of electricity by co-generation in stationary.

In the aforementioned field, many air cooling techniques at the inlet of a gas turbine (CTIAC for "Combustion Turbine InletAir Cooling") have been described.

In these techniques of air cooling at the inlet of a gas turbine there are a number of problems.

Thus, for water spray systems ("fogging and evaporative cooler") the possible cooling is limited by external conditions: the amount of water that can contain air is limited. For example, in a humid environment, one can (almost) not cool.

For mechanical compression systems, there is no limitation of cooling due to external conditions. On the other hand, the machine consumes a lot of electricity: to produce lkWh of cold, it consumes between 0.2 and 0.4 kWh of electricity.

Also, with absorption systems, there is no limitation of cooling due to external conditions and the machine consumes little electricity: to produce lkWh of cold, it consumes between 0.07 and 0.1 kWh of electricity. On the other hand, these machines are expensive and often not very flexible to use.

The present invention aims to provide a gas turbine installation to overcome the disadvantages of the prior art and in particular to allow an increase in mechanical power, and possibly the available thermal power supplied by a gas turbine with a possible adaptation to variations in climatic conditions in the environment in which the installation is located.

For this purpose, according to a first aspect, the present invention relates to a gas turbine plant which implements cooling CTIAC refrigerating machine with ejector. More specifically, it proposes a gas turbine installation, characterized in that it comprises:

a refrigerating machine operating with a fluid (a liquid, for example water, or a gas or more generally a fluid able to change phase, which is liquid or gaseous as a function of its position in the machine), comprising:

A high pressure circuit with a generator powered by a pump and subjected to a source of heat,

A low pressure circuit with an evaporator fed by an expansion element and forming a first cold source, an intermediate pressure circuit with an ejector and a condenser placed downstream of said ejector,

in which the fluid leaving the generator and the fluid exiting the evaporator supply said ejector and the fluid leaving the condenser feeds said pump and said expansion member,

a gas turbine with a compressor supplied with air by an air supply line and whose outlet is connected to the inlet of a combustion chamber supplied with fuel (for example natural gas), the outlet of the combustion chamber being connected with the inlet of a turbine having an outlet with exhaust gases flowing in an exhaust pipe,

wherein the air supply line is subjected to a source of cold and the exhaust pipe belongs to said heat source.

The CTIAC by ejector refrigerating machine according to the invention makes it possible to cool the air at the inlet of the turbine to any temperature value, in the limit of the phenomena of condensation and icing, whatever the external conditions (temperature, humidity ..), although the performances (COP or coefficient of thermal and electrical performance) of such a system vary with the external conditions.

In addition, the CTIAC ejector refrigerating machine according to the invention operates from the heat discharges of a gas turbine, and its power consumption is almost negligible. Furthermore, the CTIAC by ejector refrigerating machine according to the invention operates from low temperature thermal discharges of a gas turbine, up to about 80 ° C.

In addition, the ejector refrigeration machine CTIAC according to the invention is more flexible than an absorption system using the H ₂ 0 / LiBr couple and it has an affordable cost which is less than that of a system using the ejector. NH ₃ / H ₂ 0 couple.

Thus, the use of an ejector overcomes the disadvantages of conventional cooling systems of a gas turbine: there is no limitation of cooling related to external conditions, little power consumption (comparable to absorption) , and the implementation of this technique is cheaper and more flexible than for absorption.

An ejector such as that described in WO 2011/006251 may be used in the context of the present invention.

In the foregoing, either the exhaust pipe forms the source of heat or it participates as one of the components of the heat source.

Furthermore, according to a second aspect, the present invention relates to a control method adapted for a gas turbine installation as described above.

The application of such a method of regulation on a gas turbine installation which implements a CTIAC cooling by refrigerating machine with ejector makes it possible to adapt to the variations of the external conditions, the variations of the stresses on the system (thermal demand , electrical demand), while ensuring optimal operation of the ejector.

Other advantages and characteristics of the invention will become apparent on reading the following description given by way of example and with reference to the appended drawings in which:

FIG. 1 is a schematic view showing an installation with a gas turbine according to the invention,

FIGS. 2 to 5 represent alternative embodiments of the gas turbine installation according to the invention, FIGS. 6 to 8 represent several possible configurations for the implementation of the gas turbine installation according to the invention within a heating network, and

- Figures 9 to 18 are diagrams showing different control methods according to the invention applicable to these gas turbine plants.

In Figures 1 to 8, there is first, a refrigerating machine 100 used in the installation with gas turbine according to the invention.

This refrigerating machine 100 is an ejector system, composed of the following elements:

An ejector 102: it plays the role of "thermal compressor". The high pressure flow of a high pressure circuit 110, accelerated at the inlet of the ejector 102, sucks the low pressure flow of a low pressure circuit 120. These two streams mix to form a flow at intermediate pressure of an intermediate pressure circuit 130.

The intermediate pressure circuit 130:

a condenser 104: at the outlet of the ejector 102, the intermediate pressure stream is cooled in order to condense it. This exchange is typically with a source at room temperature.

• The low pressure circuit 120:

o An expansion member 106: a portion of this intermediate pressure stream is expanded.

o An evaporator 108: the low pressure stream obtained is reheated and evaporated. This low pressure steam then enters the ejector 102. This heat exchange corresponds to the cold produced. This heat exchange is carried out with a heat source typically at room temperature (10 to 30 ° C).

• The high pressure circuit 110:

a pump 112: the rest of the intermediate pressure stream is compressed by the pump 112. This pump 112, operating on liquid, consumes little electricity.

a generator 114: the high pressure stream obtained is reheated and evaporated. This high-pressure steam then enters the ejector 102. This heat exchange is carried out with a heat source typically between 80 and 120 ° C. According to the invention, as can be seen in FIG. 1, this refrigerating machine 100 is associated with a gas turbine engine 200, while operating as previously described.

The gas turbine 200 comprises a compressor 202, a combustion chamber 204, a turbine 206 and a gas turbine generator 208 adapted to drive the main shaft of the turbine 206 and the compressor 202.

The combustion chamber 204 is supplied with fuel by a fuel supply line 211.

The exhaust gases of the turbine 206 flow in an exhaust pipe 212.

The air of the air supply line 210 for cooling, enters the gas turbine 200 at the compressor 202, and allows upstream of the gas turbine 200 to evaporate the fluid of the low pressure circuit. 120 passing through the evaporator 108. The fumes exiting the turbine 206 through the exhaust pipe 212, and which are to be cooled, allow the high-pressure fluid to be evaporated at the level of the generator 114, by heat exchange at 114. If the installation further comprises (not shown) a cogeneration heat exchanger, the latter is placed upstream of the said generator 114 on the exhaust pipe 212.

The fluid of the intermediate pressure circuit 130 is condensed by the heater type condenser 104.

Thus, the installation that is the subject of the invention cools air that enters, via the air supply line 210, into the compressor 202 connected to the turbine 206. This air leaves the compressor, and is mixed with a fuel (eg natural gas) arriving through the fuel supply line 211 into the combustion chamber 204. Then, the combustion takes place. The fumes obtained are expanded in the turbine 206, which drives the air compressor 202 and the alternator forming the gas turbine generator 208. The fumes enter the cogeneration heat exchanger, if it exists, in which they are cooled. (case not shown in Figure 1). Then, the fumes are cooled in the generator 114 of the ejector system formed of the refrigerating machine 100. Finally, the fumes are released into the atmosphere. This configuration of FIG. 1, in which the exhaust pipe 212 forms the heat source of the high pressure circuit 110 and the air supply pipe 210 is subjected to said first cold source (formed in this example of the evaporator 108) constitutes a first embodiment of the first aspect of the invention.

Referring now to FIGS. 2 to 4, the installation of FIG. 1, formed of the refrigerating machine 100 associated with the gas turbine engine 200, is configured according to another arrangement forming a second embodiment of the first aspect. of the invention.

This is the case of a cogeneration: instead of placing the generator 114 directly on the exhaust pipe 212 containing the fumes, the generator 114 is placed on an intermediate water loop 220 between an existing recovery boiler 222 (Located on the flue gas exhaust line 212) and a customer-side exchanger 224 which is connected to the hot water or steam distribution network to the customer (distribution water loop 226).

Thus, in this case, it is understood that the installation according to the invention further comprises an intermediate water loop 220 also belonging to said heat source and comprising a recovery boiler 222 traversed by the exhaust pipe 212, and an exchanger 224 (customer-side exchanger) capable of supplying heat to another distribution water loop 226.

The connection of the installation according to this second embodiment of the first aspect of the invention can be carried out according to several variants.

According to a first variant, visible in FIG. 2, this connection is called "in parallel" and the installation further comprises a water pipe 230 forming a bypass of the intermediate water loop 220 at the location of a outlet 231 located downstream of the recovery boiler 222 passing through the generator 114 to form said source of heat to which said generator 114 of the refrigerating machine 100 is subjected and opening into the intermediate water loop 220 downstream of said exchanger 224 of the intermediate water loop 220 (socket 232 in Figure 2).

In this case, the temperatures in the intermediate loop

220 remain the same, only the flow of circulating water is changed. he can it is necessary to change the water circulation pump (not shown) of the intermediate loop 220. On the other hand, the operating conditions of the exchanger 224 on the customer side remain identical to those in the absence of the water pipe 230 forming the bypass of the intermediate water loop 220.

According to a second variant and a third variant, this connection is called "in series".

According to this second variant, visible in Figure 3, the installation further comprises a water pipe 230 'forming a bypass of the intermediate water loop 220 at the location of a plug 232 located downstream of said exchanger 224 intermediate water loop 220 passing through the generator 114 to form said heat source to which is subjected said generator 114 of the refrigerating machine 100 and opening into the intermediate water loop 220 downstream of said outlet 232 and upstream of the recovery boiler 222, at a plug 233.

According to this third variant, visible in Figure 4, the installation further comprises a water pipe 230 "forming a bypass of the intermediate water loop 220 at the location of a socket 231 located downstream of the boiler recovery 222 passing through the generator 114 to form said heat source which is subjected to said generator 114 of the refrigerating machine 100 and opening into the intermediate water loop 220 upstream of said exchanger 224 of the water loop intermediate 220, at a jack 234.

According to this second variant and this third variant, the temperatures in the intermediate water loop 220 change, the flow rate can remain the same. The investment is lower; on the other hand, the operating conditions of the exchanger 224 on the client side are modified.

Referring now to Figure 5 showing an alternative embodiment applied to the first embodiment of Figure 1, and which would be applicable to the variants of Figures 2, 3 and 4 previously described.

Indeed, on some turbines, especially on sites where winter temperatures are often cold (near or less than 0 ° C), There is a system called "anti-icing" (or de-icing), which allows when the outside temperature is too low (and the humidity too high) to reheat even when the turbine returns.

In this case, said gas turbine further comprises a deicing system 240 forming a second cold source and the air supply pipe 210 is subjected to said second source of cold.

In the case of FIG. 5, it can be seen that the deicing system 240 comprises a water supply line 242 and a heat exchanger 244.

In this case, there already exists a heat exchanger 244 on the air flow at the inlet of the gas turbine 200, namely on the air supply line 210.

Also, the ejector 102 can use this exchanger 244 to cool the air when the temperatures are too high (and therefore when the defrosting system 240 is not currently used): the ejector 102 cools the passing water in this exchanger 244 of the defrosting system 240. The idea is to install the evaporator 108 of the refrigerating machine 100 on the pipe 242 of water. The water of this water supply pipe is "hot" in winter, in order to defrost the air of the pipe 210 and is cold (that is to say cooled by the refrigerating machine 100) in summer, when it's warmer

This configuration of FIG. 5 can of course be coupled with those previously described in FIGS. 2 to 4.

On many gas turbines, there is not a single chimney but two exhaust gas exhaust chimneys. Indeed, as can be seen in FIGS. 6 to 8, an adjustable valve 300 (also called "diverter") makes it possible to adjust the flow coming out of the exhaust pipe 212 on the chimneys 302 and 304. Thus, in the current practice, no heat recovery is made in the first chimney 302 of which the fumes come out very hot, but with a flow rate that is often low in the exhaust pipe 312 of the first chimney 302.

Thus, currently, the heat recovery, in particular for the cogeneration, is carried out in the second chimney 304 through the recovery boiler 222, with flow rates being higher. However, in this second chimney 304, the fumes then come out warmer than those leaving the first chimney 302.

Referring to FIGS. 6 to 8 illustrating several possible configurations for the implementation of the gas turbine installation according to the invention (100 and 200) within a heating network comprising a water loop dispenser 226 connected to an intermediate water loop 220 by a customer-side exchanger 224 and a recovery boiler 222.

It is then possible to place the ejector system 100 in three different places:

• On the first chimney 302 (Figure 6): the exhaust pipe 312 of the first chimney 302 passes into the generator 114, while the exhaust pipe 314 of the second chimney 304 is directed on the recovery boiler 222.

In this case, the exhaust pipe 212 comprises at least a first chimney 302 and a second chimney 304 for exhausting the flue gases, the second chimney being placed downstream of the first chimney with, between the first chimney 302 and the second chimney 302. chimney 304, an exhaust control valve 300, and the fumes exiting the first chimney 302, through the exhaust duct 312 of the first chimney 302, form said heat source.

• On the second stack 304, after the recovery boiler 222. The ejector system 100 will not be put before the recovery boiler 222 to avoid being unable to meet the customer's need (the heat used by the ejector system 100 must to be heat not valued by the customer), according to Figure 7. In this case, the exhaust pipe 314 of the second chimney 304 first passes through the recovery boiler 222, then downstream of the recovery boiler 222 the generator 114 of the ejector system 100. In this situation, said intermediate water loop 220 forms said heat source since said intermediate water loop 220 is connected via the recovery boiler 222 to the steam generator 114 of the cooling circuit. high pressure 110.

· On the intermediate hot water loop 220, after the recovery boiler 222. There are always three configurations feasible: in parallel, in series on the go and in series on the return. Only the parallel configuration is shown here in FIG. 8: the exhaust pipe 314 of the second chimney 304 passes firstly through the recovery boiler 222 which is placed on the intermediate water loop 220, downstream of the exchanger 224 on the client side. In this case, and more generally, the exhaust pipe 212 comprises at least a first chimney 302 and a second chimney 304 for the exhaust of the fumes, the second chimney 304 being placed downstream of the first chimney 302. with, between the first chimney 302 and the second chimney 304, an exhaust regulating valve 300, and the fumes exiting the second chimney 304 through the exhaust pipe of the second chimney 314, passing through said recovery boiler 222.

In the case of the parallel configuration illustrated in Figure 8, there is the water pipe 230 forming a bypass of the intermediate water loop 220 at the location of a catch 231 located downstream of the recovery boiler 222 passing through the generator 114 to form said heat source which is subjected to said generator 114 of the refrigerating machine 100 and opening into the intermediate water loop 220 downstream of said exchanger 224 of the intermediate water loop 220 (taken 232 in Figure 8).

This application makes it possible to value the heat that is rarely used today (heat from gas turbines below 100 ° C), and to use it to increase the electric power produced by the turbine 206.

The installation according to the present invention is accompanied by an optimal regulation allowing to operate all year round (that is to say whatever the external conditions and the electrical and thermal load constraints imposed on the turbine 206 ).

Indeed, according to a second aspect of the invention, the applicant has established a regulation, based on experimental results obtained on a prototype, which is based on taking into account the heat available in the fumes exiting the turbine. gas 200 through the exhaust pipe 212, a limitation of the minimum temperature of the air admitted to the inlet of the gas turbine 200 in the air supply pipe 210 (minimum value Tf depending on the conditions external) and an optimal operating model of the ejector system 100.

In general, as shown in FIGS. 9 and 10, the ejector system 100 is controlled through two variables: the speed of rotation V of the pump 112 and the degree of opening 0 of the expansion device 106 (solenoid valve).

The objective of the control of the system is to cool as much as possible the air entering the turbine 206 (within the limits of the technical operating conditions of the turbine 206) by ensuring the best possible performance of the ejector system 100, and taking into account the constraints that are the ambient temperature Tamb and the heat available in the fumes CHdispo, either in the exhaust pipe 212 (Figures 1 to 5), or at the outlet of the chimney 302 or 304 (Figures 6 to 8) ), namely in the exhaust duct of the first chimney 312 or in the exhaust duct of the second chimney 314.

According to a first embodiment of the second aspect, illustrated in FIG. 9, there is provided a method for regulating a gas turbine installation as described above, in which a regulation of said refrigerating machine (ejector system 100 ) by regulating the speed V of said pump 112 and the opening level (O) of said expansion member 106, from a set temperature (TCair) for the air of said air supply line 210 located downstream of the cold source (Tf), namely at the inlet of the compressor 202, using a double PID regulator.

In this case, it is necessary to decorrelate the influence of the two input parameters (here the speed V of the pump 112 and the opening O of the expansion member 106) and use a PID regulator on each input, namely a first PID regulator 402 at the inlet of the pump 112 to adjust its speed V and a second PID regulator 404 at the inlet of the expansion member 106 to adjust its degree of opening O.

According to a second embodiment of the second aspect, illustrated in FIG. 10, there is provided a method of regulating a gas turbine installation as previously described, in which regulation of said refrigerating machine 100 is carried out by regulating the speed V of said pump 112 and the opening level O of said expansion element 106, from a set temperature (TCair) for the air of said air supply pipe 210 situated downstream of the cold source (Tf), using an optimal and / or robust control multi-variable taking into account the ambient air temperature Tamb, the heat available in the CHdispo exhaust (energy in J or power in W) and the actual temperature of the air in the air supply line 210 at the inlet of the compressor 202 (realized Tf). It is therefore an optimization of the input values of the ejector system 100.

Thus, this type of ejector system 100 can be regulated for example by using a multi-variable control based on an operating model of this system. The regulation will then consist in an optimization of the input values (pump speed V 112 and opening O of the expansion device 106) by knowing the measured values of the output (cooled air temperature Tf achieved) and the stresses ( external temperature Tamb and heat available in CHdispo fumes).

The optimization calculation consists of an inversion of the model chosen to represent the ejector system 100.

This model can take different forms:

a set of charts connecting the performance of the system and the cooled air temperature Tf carried out, at the outside temperature Tamb, at the heat available in the CHdispo fumes, at the speed V of the pump 112 and at the opening O of the detent 106.

a model identified from a set (sufficiently large) of measurements made on the ejector system 100. This model can take the form of state equations.

a deterministic model, that is to say a set of equations (and a calculation algorithm) linking together the different parameters (notably realized Tf, Tamb, CHdispo, V and O ....). This model is often expressed in the form of state equations.

The solution to be chosen between these three possibilities depends on the available data, the required refresh rate of the input values and the possibility or not of having deterministic physical models. Indeed, these solutions require more or less important computing times: for example, the use of graphs allows a very fast calculation (a few seconds), whereas the use of a deterministic model requires much more time (up to a few minutes)

According to a third embodiment of the second aspect, illustrated in FIG. 11, there is provided a method for regulating an installation with a gas turbine as previously described according to the second embodiment of the second aspect, in which regulation is carried out. primary of said refrigerating machine 100 by regulating (with PIDs for example) the speed V of said pump 112 and the opening level 0 of said expansion member 106, from the setpoint of at least two primary control parameters selected among parameters of the refrigerating machine 100 comprising the temperature of the fluid during the change of state in the evaporator (Tevap), the temperature of the fluid during the change of state in the generator (Tg), the flow of fluid in the low pressure circuit (ml or primary flow), the fluid flow in the high pressure circuit (m2 or secondary flow), the difference (Lift) between the temperature at the change state condition in the condenser (Tcond) and during the change of state in the evaporator (Tevap) and the ratio between the fluid flow rate (ml) in the low pressure circuit 110 and the fluid flow rate (m2) in the high pressure circuit 120 (called training rate w), and

- Secondary control of said refrigerating machine 100 in which a control system is used to calculate the set values of said selected primary control parameters.

"Primary" regulation, which we can also call

"Low level regulation", allows to directly control the pump 112 (speed V) and the expansion member 106 (the opening level O of the expansion member 106, which is usually a valve). The outputs of the primary control are therefore control variables, in this case the speed of the pump 112 (V) and the opening level of the expansion member 106 (O). In input, the primary regulation presents two measurements and two instructions calculated by the "secondary" regulation. These two measurements and these two setpoints must correspond to the same pair of parameters. For example, if one of the instructions is the Tevap evaporation temperature, this temperature must be measured. It is also possible to use a mathematical tool (called observer) which makes it possible to deduce from other measurements the value of the current evaporation temperature. In the case where the lift (Tcond - Tevap) and / or the training rate (w = m2 / ml) are used, an observer is essential (these quantities can not be measured directly).

The definition of this primary regulation must include a model (simple) linking the quantities measured at the speed of the pump 106 (V) and the opening of the expansion member 106 (0).

The "secondary" regulation makes it possible to calculate, using the measurements of the stresses imposed on the system comprising the gas turbine engine 200 and the refrigerating machine 100, the "primary" regulation instructions.

FIG. 12 shows a variant of the third embodiment of the second aspect, in which the secondary regulation regulating system is a PID regulator system based on a set temperature (TCair) for the air of said air supply line 210 located downstream of the cold source, namely at the inlet of the compressor 202.

In Figures 13 to 18:

- "Inputs" means the measurements or data necessary for the operation of the regulation.

- "Outputs" refers to the results obtained, which serve here as reference for the regulation of the ejector (primary regulation).

- "Correlations" means experimental or bibliographical data linking the Hamb outdoor humidity to the minimum safety temperature to prevent any icing in the turbine (minimum Tf).

According to a fourth embodiment of the second aspect, illustrated in FIG. 13 in solid lines, there is provided a method of regulating a gas turbine installation as previously described according to the third embodiment of the second aspect, in which the secondary regulating system comprises a first mathematical model of the ejector system 100 which supplies the setpoint of the fluid flow at the generator output (optimal ml) from a first series of quantities including the temperature of the ambient air Tamb.

The first model calculates the optimal point, that is to say without any constraint taken into account. Its only input is the outside temperature Tamb (or the condensing temperature of the water that depends directly on the outside temperature Tamb).

According to a variant of the fourth embodiment of the second aspect, illustrated in FIG. 13 with the additional elements in dashed lines, there is provided a method for regulating a gas turbine installation as described above, in which the regulating system of FIG. the secondary regulation further comprises a third mathematical model of the ejector system (100), called the "ejector model 3", located downstream of the first mathematical model of the ejector system called "model of the ejector 1", which provides a variety of information on the optimal operating point of the installation from a third set of magnitudes including the actual air temperature of the air supply line 210 at the inlet of the compressor 202 (Tf achieved) and the set temperature (TCair) for the air of said air supply line 210 calculated by the first mathematical model.

In this case, therefore, a control calculation (for example a PID) is added to the output of the first model of the ejector, which takes into account the difference between the actual air temperature of the air supply line. (210) at the inlet of the compressor (202) after cooling (Tf achieved) and the set temperature (TCair) calculated by the first mathematical model.

According to another variant of the fourth embodiment of the second aspect, illustrated in FIG. 16 in solid lines, there is provided a method of regulating a gas turbine installation as previously described according to the third embodiment of the second aspect, wherein the secondary regulating regulating system further takes into account the humidity of the ambient air Hamb to determine the minimum value of the air temperature of the air supply line 210 at the inlet of the compressor (Tf minimum) and the regulating system of the secondary regulation further comprises a third mathematical model of the ejector system 100 which provides several information on the optimal operating point of the installation from a third series of quantities including the actual air temperature of the air supply line 210 at the compressor inlet (Tf achieved) and the minimum acceptable air temperature at the turbine inlet 206 (TARmin).

The third model calculates the operation of the system taking into account the air cooling limit temperature (which can be fixed or calculated) or more generally the minimum acceptable air temperature at the inlet of the turbine (TARmin) . Its input data are: the operation of the ejector system 100 without this constraint (therefore the result of the first model and in particular the cooled air temperature reached according to the operating point of the first model of the ejector is Tf achieved) and the air cooling limit temperature TARmin.

According to a fifth embodiment of the second aspect, illustrated in FIG. 14 in solid lines, there is provided a method for regulating a gas turbine installation as previously described according to the fourth embodiment of the second aspect, in which the the secondary regulating system also takes into account quantities representative of the exhaust gases (such as inlet temperature and / or flow rate and / or heat capacity) and furthermore comprises a second mathematical model of the ejector system 100, called "Ejector model 2", which provides an optimal value of the air temperature of the air supply line at the compressor inlet (optimal Tf), from a second series of quantities comprising the heat available in the exhaust gases (CHdispo), the temperature of the fluid in the condenser (Tcond) and the flow rate of fluid at the generator outlet (ml achieved).

The second mathematical model calculates the second point of operation of the system taking into account the available heat in the CHdispo exhaust. Its input data are: the operation of the ejector system 100 without this constraint (hence the result of the first model) and the heat available in the exhaust gas (CHdispo) (exhaust pipe 212). To do this, we perform upstream of this second mathematical model, the comparison between the heat consumed at the first point of operation of the system, with the maximum possible power, namely the heat actually available in the exhaust gases (fumes) CHdispo.

According to a first variant of the fifth embodiment of the second aspect, illustrated in FIG. 14 with the additional elements in dashed lines, there is provided a method of regulating a gas turbine installation as described above, in which the regulating system of the secondary regulation further comprises a third mathematical model of the ejector system (100), located downstream of the second mathematical model of the ejector system, which provides several information on the optimal operating point of the installation from a third series of quantities including the actual air temperature of the air supply line (210) at the inlet of the compressor (202) (Tf achieved) and the set temperature (TCair) for the air of said air supply line 210 calculated by the first mathematical model.

In this case, a control calculation (for example a PID) is added to the output of the second model of the ejector, which takes into account the difference between the actual air temperature of the air supply line. (210) at the compressor inlet (202) after cooling (realized Tf) and the set temperature (TCair) calculated by the second mathematical model.

According to a second variant of the fifth embodiment of the second aspect, illustrated in FIG. 17 in solid lines, there is provided a method for regulating a gas turbine installation as previously described in relation with FIG. 14 and according to the fifth embodiment of the second aspect, wherein the secondary regulating regulating system further takes into account a minimum predetermined temperature value of the air of the air supply line 210 at the inlet of the compressor 202 (minimum Tf fixed) and the maximum between said optimum value of the air temperature of the air supply line 210 at the inlet of the compressor 202 (optimal Tf) and a predetermined minimum value of the air temperature of the pipe 210 at the inlet of the compressor 202 (Tf minimum), said maximum being the largest value between optimal Tf and minimum Tf and forming the actual temperature of the air of driving supply air 210 to the inlet of the compressor 202 (Tf achieved), and wherein the secondary regulating regulator system further comprises a third mathematical model of the ejector system 100 which provides several information on the optimal operating point of the installation from a third series of quantities comprising the actual temperature of the air of the air supply line 210 at the inlet of the compressor (Tf achieved) and the minimum temperature of the air acceptable to the turbine inlet 206 (TARmin).

Note that in most cases TARmin = Tf minimum and corresponds to the air temperature after cooling by the ejector system (refrigerating machine 100): in effect TARmin is the minimum cooled air temperature acceptable at the input of the turbine 206 and minimum Tf is the minimum predetermined value of the air temperature of the air supply line 210 at the inlet of the compressor 202.

The second mathematical model calculates the first operating point of the system taking into account the available heat CHdispo. Its input data are: the operation of the ejector system 100 without this constraint (hence the result of the first model) and the heat available in them in the exhaust (CHdispo) (exhaust pipe 212). To do this, it is performed upstream of this second mathematical model, the comparison between the heat consumed at the first operating point of the system, with the maximum possible power, namely the heat actually available in the exhaust gas (fumes) CHdispo .

According to a third variant of the fifth embodiment of the second aspect, illustrated in FIG. 18 in solid lines, there is provided a method of regulating a gas turbine installation as previously described, in which the secondary regulation regulating system furthermore takes into account the humidity of the ambient air Hamb to determine the minimum value of the air temperature of the air supply line 210 at the inlet of the compressor 202 (minimum Tf) and the maximum between said optimum value of the air temperature of the air supply line 210 at the inlet of the compressor 202 (optimal Tf) and a predetermined minimum value of the air temperature of the air supply line 210 at the inlet of compressor 202 (minimum fixed Tf), said maximum being the largest value between Tf and optimal Tf and forming the actual air temperature of the air supply line 210 to the inlet of the compressor 202 (Tf achieved), and wherein the secondary regulating regulator system further comprises a third model mathematical system of the ejector system 100 which provides several information on the optimal operating point of the installation from a third series of quantities including the actual air temperature of the air supply line 210 at the entrance compressor 202 (Tf achieved) and the minimum acceptable air temperature at the turbine inlet 206 (TARmin).

The second mathematical model calculates the second operating point of the system taking into account the available heat CHdispo. Its input data are: the operation of the ejector system 100 without this constraint (hence the result of the first model) and the heat available in the exhaust gas (CHdispo) (exhaust pipe 212). To do this, it is performed upstream of this second mathematical model, the comparison between the heat consumed at the first operating point of the system, with the maximum possible power, namely the heat actually available in the exhaust gas (fumes) CHdispo .

According to an alternative of the second or third variant of the fifth embodiment of the second aspect, there is provided a method for regulating a gas turbine installation as described above, in said information on the optimal operating point of the the installation comprises at least one of the fluid flow rate at the outlet of the evaporator 108 (m2 produced), the ratio (w) between the fluid flow rate at the outlet of the evaporator 108 (m2 produced) and the flow rate of generator output fluid 114 (ml produced), the evaporator state change temperature 108 (Tevap), the difference (Lift) between the condenser state change temperature 104 (Tcond) and the temperature of the change of state of the evaporator 108 (Tevap), the pressure at the generator 114 (Pg) and the pressure at the evaporator 108 (Pevap).

Thus, as seen in Figure 18:

- The second mathematical model calculates the second point of operation of the system taking into account the heat available CHdispo. Its input data are: the operation of the ejector system 100 without this constraint (hence the result of the first model) and the heat available in them in the exhaust (CHdispo) (exhaust pipe 212). To do this, it is performed upstream of this second mathematical model, the comparison between the heat consumed at the first operating point of the system, with the maximum possible power, namely the heat actually available in the exhaust gas (fumes) CHdispo , and

the third model, placed downstream of the second model, calculates the operation of the system taking into account the air cooling limit temperature (which can be fixed or calculated) or more generally the minimum air temperature acceptable to the inlet of the turbine (TARmin). Its input data are: the operation of the ejector system 100 with the actual heat stress available in the CHdispo exhaust gas (hence the result of the second model) and the TARmin air cooling limit temperature.

According to a sixth embodiment of the second aspect, illustrated in FIG. 15 in solid lines, there is provided a method for regulating a gas turbine installation as previously described according to the fourth embodiment of the second aspect, in which the the secondary regulating system furthermore takes into account a predetermined minimum air temperature value of the air supply line at the inlet of the compressor (minimum T f) and in which the secondary regulating regulating system comprises in addition a third mathematical model of the ejector system 100Q which provides several information on the optimal operating point of the installation from a third series of quantities including the actual temperature of the air of the air supply line to the compressor inlet (Tf achieved) and the minimum acceptable air temperature at the inlet of the turbine (TARmi not).

The third model calculates the operation of the system taking into account the air cooling limit temperature (which can be fixed or calculated) or more generally the minimum acceptable air temperature at the inlet of the turbine (TARmin) . Its input data is: the operation of the ejector system 100 without this constraint (therefore the result of the first model or the second model and in particular the cooled air temperature reached according to the operating point of the first model of the ejector is Tf achieved) and the cooling limit temperature of air TARmin.

The constraints are taken into account via a comparison between the operating points previously calculated and the constraint.

For example, in the second model, it will be verified whether the heat consumed by the ejector system 100 without constraints (therefore the result of the first model) is less than the available heat CHdispo. Otherwise, we will restrict the operation of the system to reduce heat consumption: the stress will be exerted first on the primary flow ml.

Similarly, in the third model, it will be verified whether the cold temperature produced in the ejector system 100 without this constraint (Tf optimal result of the first or the second model) is greater than the limit temperature (TARmin). Otherwise, we will restrict the operation of the ejector system 100 to reduce the production of cold: which will increase the temperature of the product cold (Tf achieved), decrease the secondary flow m2.

Preferably, two setpoint variables (or setpoint information) are used: one on the generator side 114 and one on the evaporator side 108. Generally, but this is not mandatory, we will take variables of the same type: two temperatures (Tevap and Tg therefore) or two pressures (Pevap and Pg) or two flow rates (ml and m2).

The lift (Tcond - Tevap) and the training rate (w = m2 / ml) are "performance indicators" which, when used together, contain enough information to serve as set variables.

According to an alternative embodiment of the second aspect of the invention, applicable to the control methods described above in relation with FIGS. 13 to 18, said third mathematical model of the ejector system (100) is corrected by adding to the optimal operating point of installing the difference between the actual air temperature of the air supply line (210) to the compressor inlet (202) after cooling (realized Tf) and the set temperature (TCair) calculated by the third mathematical model and taking into account the minimum acceptable air temperature at the inlet of the turbine (206) (TAR min).

Indeed, as can be seen in FIGS. 13 to 18 by considering the elements in dashed lines, before the third model of the ejector is added a return of the measurement of the cooled air temperature (realized Tf) resulting from the application of the instructions previously established for the installation according to the first aspect of the invention, formed of the gas turbine unit 200 and the refrigerating machine 100, by means of a regulation calculation (for example PID) which provides the setpoint temperature (TCair) at the input of the third model of the ejector.

This additional closed-loop arrangement makes it possible to correct the regulations described with reference to FIGS. 13 to 18 which, without these elements represented in dotted lines, have the particularity of being in an open loop: that is to say that it There is no return of the actual operation of the installation according to the first aspect of the invention and formed of the gas turbine unit 200 and the refrigerating machine 100. Thus, thanks to this additional arrangement, it prevents a drift on the system or that the first mathematical model and / or the second mathematical model of the refrigerating machine 100 forming the ejector system is (are) (or becomes (are)) mis-calibrated (s), and thus errors in the regulation, by which one can reach the desired operating point.

In order to evaluate the gains obtained by such a system, calculations were made on data corresponding to different climates for a 4.5MW turbine.

These calculations are based on several assumptions: - The humidity of the air is not taken into account,

The heat capacity of the dry air is constant with the temperature,

The cost of the ejector system is linear with the cold power to be supplied,

- The electrical consumption of the ejector is linear with the cooling power supplied, The power loss of the turbine due to the pressure drop in the evaporator depends on the cooling performed and the power of the turbine,

The airflow to be cooled is linear with the consumption of natural gas,

The system is regulated according to the method described previously with reference to FIG.

These calculations show that it is possible to obtain a gain around 2.1% compared to the power without CTIAC on such a turbine for operation from November to March (from 0.4% to 8.6% depending on the climate) or 5.1% over the whole year (from 3% to 10.5% depending on the climate). The ejector system (refrigerating machine 100) consumes around 5.3% of the power gain obtained.

These results were obtained for several different climates: wet or dry, warm or temperate. Our calculations show that the invention is interesting whatever the climate: in Abu Dhabi, Marseille, Bucharest or Warsaw.

The results obtained also show:

An electrical consumption higher than an absorption system but lower than a mechanical compression system,

A gain comparable to the absorption or mechanical compression system,

The performance of the system depends little on external conditions: the system is efficient whatever the climate considered. Indeed, the performances of the system (in particular COP or coefficient of thermal and electric performance remain fairly constant for all external conditions (thanks to the optimal regulation applied) .The differences of gain of electric power are more due to the potential gain related to the climate the performance of the system itself: any CTIAC system is more interesting in a hot climate than in a cold climate.

Claims

1. Installation with a gas turbine, characterized in that it comprises:

a refrigerating machine (100) operating with a fluid, comprising:

A high pressure circuit (110) with a generator

(114) fed by a pump (112) and subjected to a source of heat,

A low pressure circuit (120) with an evaporator (108) fed by an expansion member (106) and forming a first source of cold,

An intermediate pressure circuit (130) with an ejector (102) and a condenser (104) located downstream of said ejector (102), wherein the fluid exiting the generator (114) and the fluid leaving the evaporator (108) ) feed said ejector (102) and the fluid exiting the condenser (104) feeds said pump (112) and said expansion member (106),

- a gas turbine (200) with a compressor (202) supplied with air by an air supply line (210) and whose output is connected to the inlet of a combustion chamber (204) supplied with fuel the combustion chamber outlet (204) being connected with the inlet of a turbine (206) having an outlet with exhaust gases flowing in an exhaust pipe (212),

wherein the air supply line (210) is subjected to a source of cold and the exhaust line (212) belongs to said heat source.

2. Installation according to claim 1, characterized in that it further comprises an intermediate water loop (220) belonging to said heat source and comprising a recovery boiler (222) through which the exhaust pipe (212) ), and an exchanger (224) adapted to supply heat to another distribution water loop (226).

3. Installation according to claim 2, characterized in that it further comprises a water pipe (230) forming a bypass of the intermediate water loop (220) at the location of a plug (231) located downstream of the recovery boiler (222) passing through the generator (114) to form said heat source at which is subjected said generator (114) of the refrigerating machine (100) and opening into the intermediate water loop (220) downstream of said exchanger (224) of the intermediate water loop (220).

4. Installation according to claim 2, characterized in that it further comprises a water pipe (2300 forming a bypass of the intermediate water loop (220) at the location of a plug (232) located in downstream of said exchanger (224) of the intermediate water loop (220) passing through the generator (114) to form said source of heat to which said generator (114) of the refrigerating machine (100) is subjected and opening in the intermediate water loop (220) downstream of said inlet (232) and upstream of the recovery boiler (222).

5. Installation according to claim 2, characterized in that it further comprises a water pipe (230 ") forming a bypass of the intermediate water loop (220) at the location of a catch (231) located downstream of the recovery boiler (222) passing through the generator (114) to form said heat source to which said generator (114) of the refrigerating machine (100) is subjected and opening into the cooling loop intermediate water (220) upstream of said exchanger (224) of the intermediate water loop (220).

6. Installation according to claim 1, characterized in that said gas turbine comprises a defrosting system (240) forming a second source of cold and in that the air supply line (210) is subjected to said second source cold.

7. Installation according to claim 1, characterized in that the air supply line (210) is subjected to said first source of cold.

8. Installation according to claim 1 or claim 2, characterized in that the exhaust pipe (212) comprises at least a first chimney (302) and a second chimney (304) for exhaust fumes, the second chimney (304) being located downstream of the first chimney (302) with a regulating valve between the first chimney (302) and the second chimney (304) exhaust (300), and in that the fumes exiting the first chimney (302) form said heat source.

9. Installation according to claim 2, characterized in that said intermediate water loop 220 forms said heat source.

10. Installation according to claim 3, 4 or 5, characterized in that the exhaust pipe (212) comprises at least a first chimney (302) and a second chimney (304) for exhaust fumes, the second chimney (304) being located downstream of the first chimney (302) with, between the first chimney (302) and the second chimney (304), an exhaust regulating valve (300), and that the fumes exiting from the second chimney (304) passes through said recovery boiler (222).

11. A method of regulating a gas turbine plant according to any one of the preceding claims, wherein:

a regulation of said refrigerating machine is carried out

(100) by regulating the speed (V) of said pump (112) and the opening level (O) of said expansion member (106) from a set temperature (TCair) for the air of said an air supply line (210) located downstream of the cold source (Tf), using a double PID regulator.

The method of regulating a gas turbine plant according to any one of claims 1 to 10, wherein:

a regulation of said refrigerating machine (100) is carried out by regulating the speed (V) of said pump (112) and the opening level (O) of said expansion member (106), starting from a set temperature (TCair) for the air of said air supply pipe located downstream of the cold source (Tf), by multi-variable control optimization taking into account the temperature of the ambient air (Tamb), the heat available in the exhaust gas (CHdispo) and the actual air temperature of the air supply line (210) at the compressor inlet (202) (Tf achieved).

a primary control of said machine is carried out refrigerant (100) by regulating the speed (V) of said pump (112) and the opening level (V) of said expansion member (106) from the setpoint of at least two primary control parameters selected from parameters of the refrigerating machine (100) comprising the temperature of the fluid during the change of state in the evaporator (108) (Tevap), the temperature of the fluid during the change of state in the generator (114) (Tg) , the fluid flow in the low pressure circuit (120) (ml or primary flow), the fluid flow in the high pressure circuit (110) (m2 or secondary flow), the difference (Lift) between the temperature at the change of state in the condenser (Tcond) and the change of state in the evaporator (Tevap) and the ratio (w) between the fluid flow in the low pressure circuit (ml) and the fluid flow in the high pressure circuit (m2), and

- Secondary control of said refrigerating machine in which a control system is used to calculate the set values of said selected primary control parameters.

14.. A control method according to claim 13, wherein the secondary control regulating system is a PID control system from a set temperature (TCair) for the air of said supply air duct (210) located in downstream of the cold source.

The control method as claimed in claim 13, wherein the secondary regulation regulating system comprises a first mathematical model of the ejector system (100) which supplies the generator output fluid flow rate (optimal ml) from a first series of quantities including the temperature of the ambient air (Tamb).

16. The control method according to claim 15, wherein the secondary regulating regulating system also takes into account quantities representative of the exhaust gases and further comprises a second mathematical model of the ejector system 100 which provides an optimal value. of the air temperature of the air supply line at the compressor inlet (optimal Tf), from a second series of quantities including the heat available in the exhaust gas (CHdispo), the temperature of fluid in the condenser (Tcond) and the flow rate of fluid at the generator outlet (ml produced).

17.. A control method according to claim 15 or 16, wherein the secondary regulation regulating system further comprises a third mathematical model of the ejector system (100) which provides a variety of information on the optimum operating point of the installation from a third series of quantities comprising the actual air temperature of the air supply line (210) at the inlet of the compressor (202) (Tf achieved) and the set temperature (TCair) for the air of said air supply line 210 calculated by the first mathematical model.

The control method according to claim 15, wherein the secondary regulation regulating system further takes into account a predetermined minimum air temperature value of the air supply line (210) at the inlet of the compressor (Tf minimum) and wherein the secondary regulation regulating system further comprises a third mathematical model of the ejector system (100) which provides a plurality of information on the optimum operating point of the installation from a third series of quantities comprising the actual air temperature of the air supply line (210) at the inlet of the compressor (202) (Tf achieved) and the minimum acceptable air temperature at the inlet of the turbine (206) (TARmin).

19. The control method according to claim 15, wherein the secondary regulation regulating system also takes into account the humidity of the ambient air (Hamb) to determine the minimum value of the air temperature of the pipe. at the inlet of the compressor (202) (minimum Tf) and the regulating system of the secondary regulation further comprises a third mathematical model of the ejector system 100 which provides several information on the optimum operating point of the installation from a third series of quantities including the actual air temperature of the air supply line at the inlet of the compressor (202) (Tf achieved) and the minimum temperature of the air acceptable to the inlet of the turbine (206) (TARmin).

20. Control method according to claim 16, wherein the secondary regulating regulating system also takes into account a predetermined minimum value of air temperature of the air supply line at the inlet of the compressor (Tf minimum) and the maximum between said optimum value of the air temperature of the air supply line at the inlet of the compressor (202) (optimal Tf) and a predetermined minimum value of the air temperature of the air supply line (210) at the compressor inlet (202) (minimum Tf), said maximum forming the actual air temperature of the air supply line (210) at the compressor inlet (Tf performed), and wherein the secondary regulation regulating system further comprises a third mathematical model of the ejector system 100 which provides a plurality of information on the optimal operating point of the installation from a e third series of quantities including the actual air temperature of the air supply line (210) at the inlet of the compressor (202) (Tf achieved) and the minimum acceptable air temperature at the inlet of the turbine (206) (TARmin).

21. The control method according to claim 16, wherein the regulating system of the secondary regulation further takes into account the humidity of the ambient air to determine the minimum value of the air temperature of the supply pipe. in air (210) at the inlet of the compressor (202) (minimum Tf) and the maximum between said optimum value of the air temperature of the air supply line (210) at the inlet of the compressor ( 202) (optimum Tf) and a predetermined minimum air temperature value of the air supply line (210) at the inlet of the compressor (202) (Tf minimum), the maximum forming the actual temperature of the air from the air supply line (210) to the inlet of the compressor (202) (Tf produced), and wherein the regulating system of the secondary regulation further comprises a third mathematical model of the ejector system 100 which provides several information about the point of optimal operation of the plant from a third series of variables including the actual air temperature of the air supply line (210) at the compressor inlet (202) (Tf achieved) and the minimum acceptable air temperature at the inlet of the turbine (TARmin).

22. Control method according to claim 20 or claim 21, characterized in that said information on the optimal operating point of the installation comprises at least one of the fluid flow rate at the outlet of the evaporator ( 108) (m2 produced), the ratio (w) between the fluid flow rate at the outlet of the evaporator (108) (m2 produced) and the flow rate of the fluid at the generator outlet (114) (ml produced), the temperature of change of state of the evaporator (108) (Tevap), the difference (Lift) between the change of state temperature of the condenser (104) (Tcond) and the change of state temperature of the evaporator (108) ) (Tevap), the pressure at the generator (114) (Pg) and the pressure at the evaporator (108) (Pevap).

A control method according to any one of claims 18 to 22, wherein said third mathematical model of the ejector system (100) is corrected by adding to the optimal operating point of the installation the difference between the actual temperature of the the air of the air supply line (210) at the inlet of the compressor (202) after cooling (realized Tf) and the set temperature (TCair) calculated by the third mathematical model and taking into account the minimum temperature acceptable air at the inlet of the turbine (206) (TAR min).