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EP2715213B1 - Système de chauffage de gaz pour systèmes de réduction de pression de gaz et procédé d'obtention dudit effet de chauffage - Google Patents

Système de chauffage de gaz pour systèmes de réduction de pression de gaz et procédé d'obtention dudit effet de chauffage Download PDF

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Publication number
EP2715213B1
EP2715213B1 EP12729195.3A EP12729195A EP2715213B1 EP 2715213 B1 EP2715213 B1 EP 2715213B1 EP 12729195 A EP12729195 A EP 12729195A EP 2715213 B1 EP2715213 B1 EP 2715213B1
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EP
European Patent Office
Prior art keywords
gas
heating
temperature
outlet duct
fluid
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EP12729195.3A
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German (de)
English (en)
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EP2715213A1 (fr
Inventor
Angelo Mapelli
Francesco Jamoletti
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/06—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10L—FUELS NOT OTHERWISE PROVIDED FOR; NATURAL GAS; SYNTHETIC NATURAL GAS OBTAINED BY PROCESSES NOT COVERED BY SUBCLASSES C10G, C10K; LIQUEFIED PETROLEUM GAS; ADDING MATERIALS TO FUELS OR FIRES TO REDUCE SMOKE OR UNDESIRABLE DEPOSITS OR TO FACILITATE SOOT REMOVAL; FIRELIGHTERS
    • C10L3/00—Gaseous fuels; Natural gas; Synthetic natural gas obtained by processes not covered by subclass C10G, C10K; Liquefied petroleum gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17D—PIPE-LINE SYSTEMS; PIPE-LINES
    • F17D1/00—Pipe-line systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17D—PIPE-LINE SYSTEMS; PIPE-LINES
    • F17D1/00—Pipe-line systems
    • F17D1/02—Pipe-line systems for gases or vapours
    • F17D1/04—Pipe-line systems for gases or vapours for distribution of gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17D—PIPE-LINE SYSTEMS; PIPE-LINES
    • F17D1/00—Pipe-line systems
    • F17D1/02—Pipe-line systems for gases or vapours
    • F17D1/04—Pipe-line systems for gases or vapours for distribution of gas
    • F17D1/05—Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17D—PIPE-LINE SYSTEMS; PIPE-LINES
    • F17D1/00—Pipe-line systems
    • F17D1/02—Pipe-line systems for gases or vapours
    • F17D1/065—Arrangements for producing propulsion of gases or vapours
    • F17D1/075—Arrangements for producing propulsion of gases or vapours by mere expansion from an initial pressure level, e.g. by arrangement of a flow-control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17D—PIPE-LINE SYSTEMS; PIPE-LINES
    • F17D1/00—Pipe-line systems
    • F17D1/08—Pipe-line systems for liquids or viscous products
    • F17D1/16—Facilitating the conveyance of liquids or effecting the conveyance of viscous products by modification of their viscosity
    • F17D1/18—Facilitating the conveyance of liquids or effecting the conveyance of viscous products by modification of their viscosity by heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17D—PIPE-LINE SYSTEMS; PIPE-LINES
    • F17D1/00—Pipe-line systems
    • F17D1/20—Arrangements or systems of devices for influencing or altering dynamic characteristics of the systems, e.g. for damping pulsations caused by opening or closing of valves

Definitions

  • the present invention relates to a system for heating the gas inside systems for reducing the gas pressure in a main gas pipeline.
  • the present invention also concerns a method for heating the gas inside gas pressure reducing systems in a main gas pipeline.
  • distribution networks are used to transfer gas between remote geographical regions, and particularly to distribute fuel gas from a source to where it is supplied to the various industrial or civil users.
  • Such networks comprise a plurality of pipelines through which the gas being distributed flows.
  • the gas is delivered from a source into a gas main by means of which it is transported at a pre-set pressure, which typically varies in the range of 12 to 74 bars.
  • first-stage stations for the purpose of providing the physical connection between the gas main and the line reaching the users.
  • a primary purpose of these stations is to achieve a decompression of the gas, reducing it from the above-mentioned delivery pressure to a lower pressure for the line delivering the gas to the user, i.e. to pressure values typically in the range of 1.5 to 5 bars, and up to 12 bars in certain applications.
  • said stations provide for a phase in which the natural gas coming from the main is heated so that its temperature downstream of the pressure reducer does not drop to values below 0°C due to the effect of expansion.
  • Natural gas in fact, contains a very small percentage of water, which would freeze and could pose problems for the instrumentation and the pressure regulator at the station.
  • the temperature of the gas leaving said stations is therefore maintained preferably at an optimal value above zero, and advantageously at around 6°C.
  • This heating phase typically takes place through suitable systems with water/gas tube bundle heat exchangers fed with water that has been preheated with methane gas boilers.
  • the water/gas tube bundle heat exchangers release energy in the form of heat to the natural gas in transit.
  • the water preheating circuit preferably consists of one or more boilers for the production of hot water, preferably relying on thermopile power systems, plus a series of gate valves for intercepting the flow of water, one or more open expansion tanks, one or more circulators located on the delivery side of the hot water circuit, two or more water/gas heat exchangers, and all the necessary connection piping.
  • the natural gas is preheated, as mentioned earlier, before its pressure is reduced.
  • the temperature of the gas Downstream of the pressure regulators that reduce the pressure of the gas, the temperature of the gas is measured by means of a thermostat on the pipeline.
  • This pipeline thermostat controls the temperature of the outgoing gas and governs the switching on/off of the boilers, and the switching on/off of the circulators.
  • the preheating temperature for the hot water circuit is set manually by means of the thermostats installed on the boilers.
  • the switching on/off of the boilers and/or circulators is consequently governed by means of the pipeline thermostat.
  • the temperature of the water in the preheating circuit comes to be at a pre-set value that is adjusted manually by an operator taking action on the thermostats on the boilers.
  • the water temperature value is therefore set at said fixed value irrespective of the actual demand for energy to heat the gas.
  • the heating system for gas pressure reducing units of the known type has several drawbacks, however.
  • a first drawback lies in that, although the system is controlled by a pipeline thermostat, it constantly generates increases and decreases in the temperature of the gas leaving the unit. This temperature departs all the more from the optimal value of 6°C, the more the temperature of the water coming from the boilers differs from (i.e. it exceeds) the optimal minimum value sufficient to heat the gas.
  • Another drawback of the known art relates to the measurement of the temperature of outgoing gas.
  • the pipeline thermostat measures the ambient temperature instead of the temperature of the gas in transit, since the lack of consumption means there is no flow of gas, which remains practically at a standstill inside the pipeline. Due to the effect of the above-described conditions, the pipeline thermostat pointlessly enables the water to be heated in the boilers, with a further wastage of energy for the unit.
  • the object of the present invention is to overcome at least some of the drawbacks of the known art.
  • a further object of the invention is to optimise the thermal energy used in the heating systems of first-stage gas receiving and pressure reducing stations.
  • the present invention is based on the general consideration that the object is to provide a system for heating the gas inside a gas pressure reducing system in which the thermal power needed to heat the gas is adjusted on the basis of the instantaneous flow rate of the gas measured after the reduction of its pressure.
  • the subject of the present invention is a gas heating system according to claim 1, i.e. a gas heating system applicable to a gas in transit between an inlet duct and an outlet duct, wherein the pressure of said gas inside said inlet duct is higher than the pressure of said gas inside said outlet duct, and comprising:
  • the system comprises means for measuring the temperature of the gas in the outlet duct that are connected to the means for controlling the thermal power generation means.
  • the thermal power generation means preferably comprise means for heating a heating fluid, and means for exchanging thermal energy between the heating fluid and the gas.
  • the control means advantageously comprise means for controlling the temperature of the heating fluid.
  • the thermal power generation means preferably comprise a line for delivering the fluid from the heating means to the exchanger means, and a line for returning the fluid from the exchanger means to the heating means.
  • the system comprises means for measuring the temperature of the fluid in said delivery line.
  • the system comprises means for measuring the temperature of the fluid in the return line.
  • the heating means preferably comprise a boiler for the production of hot water.
  • the exchanger means preferably comprise a tube bundle heat exchanger.
  • the means for measuring the gas flow rate advantageously comprise a gas meter operatively connected to a volume corrector suitable for producing the value of the gas flow rate as an output.
  • the control means preferably comprise a PLC unit.
  • the subject of the present invention is a system according to claim 6, i.e. a system for reducing the pressure of a gas between an inlet duct and an outlet duct, comprising pressure reducing means between said inlet duct and said outlet duct, the system comprising a heating system as described above.
  • the subject of the present invention is a method according to claim 7, i.e. a method for heating a gas in transit between an inlet duct and an outlet duct, wherein the pressure of said gas in the inlet duct is higher than the pressure of said gas in the outlet duct, comprising a phase for heating said gas between said inlet duct and said outlet duct, wherein said phase for heating said gas is controlled on the basis of the flow rate of said gas through said outlet duct, by calculating, by means of said control means of said system using said flow rate (Qu, gas) the value of the thermal power to be transferred to said incoming gas in said inlect duct by said thermal power generation means.
  • the gas heating phase prefferably controlled on the basis of the temperature of the gas inside the outlet duct.
  • the gas heating phase comprises a phase for heating a fluid and a phase for exchanging the thermal energy of the fluid with the gas.
  • the temperature of the fluid in the heating phase is advantageously controlled on the basis of the gas flow rate in the outlet duct.
  • the temperature of the fluid in the fluid heating phase is controlled on the basis of the temperature of the gas in the outlet duct.
  • the temperature of the fluid in the fluid heating phase is controlled on the basis of the difference between the temperature of the gas in the outlet duct and a pre-selected reference temperature.
  • the thermal energy used in the gas heating phase is calculated preferably in relation to the efficiency of the heating system.
  • This efficiency value is preferably an estimated value.
  • the method advantageously comprises phases for recalculating the estimated efficiency value in relation to a real efficiency value for the heating system.
  • the system according to the invention as described below is particularly suitable for reducing the pressure of the gas in a network for distributing gas to industrial and/or civil users.
  • Figure 1 is the functional diagram for a system 1 for reducing the pressure of a gas according to a preferred embodiment of the invention.
  • Figure 2 shows a system 1 for reducing the pressure of a gas consistently with the content of the diagram in figure 1 .
  • the system 1 is used to reduce the pressure of natural gas coming from a gas main 2 and being delivered to an outlet duct 3.
  • the system 1 substantially consists of a pressure regulating and measuring unit, or first-stage pressure reducing station, wherein the gas main 2 is the primary line for carrying the natural gas and the outlet duct 3 is the line for delivering the gas to the users.
  • the gas main 2 and the outlet duct 3 are intercepted by respective opening/closing valves 2a and 3a.
  • the gas main 2 is the primary line for carrying the natural gas, which travels at a pre-set pressure Pi,gas that is typically in the range of 12 to 74 bar, and at a pre-set temperature Ti,gas that is typically in the range between 5°C and 20°C, with mean values around 5°C.
  • the outlet duct 3 is the line for delivering the gas to the users at a pressure Pu,gas typically in the range between 1.5 and 5 bar (and as high as 12 bar in certain applications), and at a pre-set temperature Tu,gas that may typically vary between 5°C and 15°C. It is preferably, as we shall see below, for the temperature Tu,gas of the gas at the outlet to be kept at values as close as possible to 6°C.
  • gas heating means 4 are located upstream of the gas pressure reducing means 5.
  • the gas pressure reducing means 5 preferably comprise piloted pressure regulators.
  • the heating means 4 (which are easier to see in figure 2 ) preferably comprise a water/gas tube bundle heat exchanger 6 connected to a boiler 7 for the production of hot water.
  • a filter 13 designed to remove any impurities contained in the natural gas to protect the regulating and measuring instruments.
  • the boiler 7 is preferably of the free-standing type with a thermopile power system.
  • the boiler 7 is preferably complete with a thermostat 7a for controlling the temperature of the heated water, which is connected in series with the digital thermostat typically installed on the boiler 7.
  • expansion tank 12 connected to the delivery line 8 that is designed to compensate for variations in the volume of water in the heating circuit and to maintain the appropriate quantity of heating water.
  • the expansion tank could be connected to the return line 9 instead of the delivery line 8.
  • Circulators 30 are also located along the delivery line 8 (there are two of these in the embodiment illustrated) to enable a forced recirculation of the water in the heating circuit, since the expansion tank is open, in order to reduce the system's hysteresis times.
  • the boiler 7 is advantageously of the type fuelled with methane gas, in which case a suitable gas supply line 10 connects the boiler 7 to the outlet duct 3 in the system 1.
  • the heating means 4, and particularly the boiler 7, are appropriately connected to control logic 14.
  • the control logic 14 sends the thermostat 7a of the boiler 7 an indication of the temperature T1,H2O needed for the water that is to flow to the exchanger 6 through the delivery line 8.
  • a first temperature detector 15 measures the temperature of the water T1,H2O in the delivery line 8 and sends this value to the control logic 14.
  • a second temperature detector 16 measures the temperature of the water T2,H2O in the return line 9 and sends this value to the control logic 14.
  • a gas temperature detector 17 is associated with the outlet duct 3 and measures the temperature Tu,gas of the gas downstream of the gas pressure reducing means 5.
  • the gas temperature detector 17 is preferably in the form of a temperature sensor.
  • the temperature Tu,gas measurement is sent to the control logic 14.
  • Means 18 for measuring the instantaneous flow rate of the gas Qu,gas are associated with the outlet duct 3 and used to record the instantaneous flow rate of the gas downstream of the pressure reducing means 5.
  • This instantaneous gas flow rate Qu,gas measurement is sent to the control logic 14.
  • the means 18 for measuring the instantaneous gas flow rate Qu,gas comprise a gas meter 19 that sends an impulsive signal to a volume corrector 20 suited to produce the instantaneous flow rate Qu,gas as an output in the form of standard cubic metres per second, i.e. with a defined unit of time.
  • measuring device such as means for measuring mass, or a Venturi meter, to provide as output values that indicate the instantaneous flow rate of the gas Qu,gas.
  • the control logic 14 preferably consists of a programmable logic controller (PLC) unit of known type, i.e. a unit capable, among other things, of recording different signals coming from respective sensors/detectors and processing their values to generate suitable control signals.
  • PLC programmable logic controller
  • the output from the control logic 14 is a control signal for the thermostat 7a on the boiler 7 that establishes the temperature T1,H2O to which the heated water must be heated. This command overrides the digital thermostat on the boiler 7, which is installed in series with the analogical thermostat 7a.
  • the instantaneous reading by the means 18 for measuring the gas flow rate Qu,gas, combined with the gas temperature measurement Tu,gas in the outlet duct 3, enables an appropriate control of the heating means 4 so as to optimise the energy needed to heat the gas, as we shall see more clearly below from the description of how the system 1 operates.
  • Figure 3 schematically shows the operating principle behind the system 1 in a methane gas distribution network. More in particular, it illustrates the operations performed by the control logic 14.
  • a first processing unit 100 the value of the instantaneous flow rate Qu,gas of the gas at the outlet and the value of the return temperature of the water T2,H2O are processed to provide as output a first value of the temperature at which the heated water T'1,H2O has to be delivered.
  • the rated values for the system 1 are used for this calculation, which are:
  • C ⁇ 1 Qu , gas * ⁇ CH ⁇ 4 * ⁇ h , where pCH4 is the volumetric mass of the methane, expressed in kg/m3, and ⁇ h is the previously-calculated enthalpy change.
  • the next processing step takes into account the efficiency E1 of the heating system in the system 1 in order to calculate the effective thermal power C2 that the boiler 7 has to provide.
  • the value of the heating system's efficiency E1 is an estimate made by the operator, based on their know-how and experience in the field, and may depend on various factors, such as the insulation of the circuit where the water transits, the state of efficiency of the boiler, and so on. In a variant of the method, as we shall see in more detail later on, this efficiency value can be recalculated from time to time by the control logic 14, based on its processing of the values identified in the system 1. The calculated efficiency will thus tend towards the real and effective value of the efficiency of the heating system in the system 1.
  • the previously-calculated value of the thermal power C2 (at the outlet from unit 102) is subsequently processed (unit 103) to provide a temperature value ⁇ T (at the outlet from unit 103).
  • the temperature of the water in the return line T2,H2O is advantageously measured by the second temperature detector 16.
  • the water delivery temperature T'1,H2O is then calculated by adding the value of the previously-calculated temperature difference ⁇ T (at the outlet from unit 103) to the temperature T2,H2O measured in the water return line.
  • the temperature T'1,H2O calculated in this way represents a first estimate of the temperature T'1,H2O at which the heated water must flow from the boiler 7.
  • This temperature T'1,H2O is calculated with no control being performed on the effective temperature Tu,gas on the gas in the outlet duct 3.
  • Said control is performed in the next processing unit 150, as shown in figure 3 .
  • the previously-calculated first temperature value T'1,H2O is processed and corrected, taking into account the temperature of the gas Tu,gas actually measured at the outlet duct 3, and the desirable reference temperature for the outgoing gas Tu,gas_rif.
  • the final temperature value T1,H2O at which the heated water has to flow from the boiler 7 is given at the outlet from said processing unit 150. This value is transmitted by the control logic 14 to the thermostat 7a on the boiler 7.
  • the temperature of the outgoing gas Tu,gas is advantageously recorded by the gas temperature detector 17 associated with the outlet duct 3.
  • the desirable reference temperature value for the outgoing gas Tu,gas_rif is advantageously set at 6°C.
  • the processing unit 150 is basically a feedback system for controlling the final temperature T1,H2O at which the heated water has to flow from the boiler 7 as a function of the temperature of the outgoing gas Tu,gas.
  • Said control system may be of the proportional-integral-derivative type or based on any combination thereof, depending on the type and the dynamic conditions of the system.
  • the calculations performed in the processing unit 150 are implemented operatively in the control logic unit 14.
  • the temperature value T1,H2O thus represents the final temperature at which the heated water must flow from the boiler 7.
  • the thermal power needed to guarantee an optimal outgoing gas temperature can be calculated starting from the instantaneous flow rate measured for the gas in transit through the outlet duct.
  • the system consequently enables the amount of heat needed to heat the gas to be estimated using the instantaneous flow rate of the gas as a control parameter, whereas conventional systems rely on the temperature of the outgoing gas alone. This enables the inertia of the system to be limited, thereby increasing the efficiency of the system for regulating the temperature of the outgoing gas.
  • the system also enables an appropriate adjustment of the temperature of the water heated by the boiler to provide the effective thermal energy required by the system, with a consequent improvement in the system's energy efficiency by comparison with the known systems, in which the temperature of the heated water is substantially fixed.
  • a self-teaching function is included in the system 1 with a view to optimising its performance.
  • the mean value erm of the coefficient of error er the mean value C1m of the thermal power C1, and the mean value C2m of the thermal power C2 are calculated.
  • ⁇ Tc C ⁇ 2 ⁇ m / mH ⁇ 2 ⁇ O * CpH ⁇ 2 ⁇ O + erm .
  • E ⁇ ⁇ 1 C ⁇ 1 ⁇ m / C ⁇ 3.
  • this new efficiency value E'1 for the heating system in the system 1 can be used instead of the efficiency value E1 estimated in advance. In successive calculations the efficiency E'1 will gradually tend towards the real value of the efficiency of the system 1.
  • Figure 6 shows a variant of the system 1' according to the invention that differs from the one shown in figure 1 in that it includes two boilers 7, 7', instead of one, and two parallel lines for the passage of the gas, fitted with respective gas heating means 4, 4' and gas pressure reducing means 5, 5'.
  • the two boilers 7, 7' are suitably connected in parallel and are connected to the same delivery line 8 and to the same return line 9.
  • a thermostat 7a is associated with both the boilers 7 and 7', and connected to the control logic 14.
  • the gas heating system described in the previous embodiments preferably comprises a boiler for heating the heated water and a water/gas tube bundle heat exchanger.
  • the heating system may be different, however, e.g. a system with a heat pump and a tube bundle exchanger, or boilers with plate exchangers, or even heat pumps combined with plate exchangers, etc.
  • the thermal power released to the gas before its expansion will be advantageously controlled on the basis of the gas flow rate identified after its pressure has been reduced.
  • the present invention enables the previously-stated objects to be achieved.
  • it enables the development of a gas pressure reducing system with a better energy performance than the known state of the art.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Combustion & Propulsion (AREA)
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Claims (12)

  1. Système de chauffage d'un gaz indiqué pour être appliqué à un gaz en transit entre un conduit d'entrée (2) et un conduit de sortie (3), où la pression dudit gaz dans ledit conduit d'entrée (2) est supérieure à la pression dudit gaz dans ledit conduit de sortie (3), comprenant :
    - des moyens de génération de puissance thermique (4 ; 4') aptes à chaufferledit gaz entre ledit conduit d'entrée (2) et ledit conduit de sortie (3);
    - lesdits moyens de génération de puissance thermique (4 ; 4') comprenant des moyens (7 ; 7') pour chauffer un fluide de chauffage et des moyens (6 ; 6') pour échanger l'énergie thermique entre ledit fluide de chauffage et ledit gaz ;
    - des moyens de réduction de la pression du gaz (5) ;
    - des moyens de contrôle (14) desdits moyens de génération de puissance thermique (4; 4');
    - des moyens (18) pour mesurer le débit instantané (Qu,gas) après la réduction de la pression dudit gaz dans ledit conduit de sortie (3) relié auxdits moyens de contrôle (14) desdits moyens de génération de puissance thermique (4 ; 4') ;
    caractérisé en ce que
    lesdits moyens de contrôle sont indiqués pour calculer la température de refoulement du fluide de chauffage (T1, H2O) à laquelle le fluide de chauffage doit s'écouler des moyens de chauffage (7 ; 7') en utilisant ledit débit instantané (Qu,gas) mesuré après la réduction de sa pression et une valeur estimée de l'efficience du système de chauffage (E1) et la valeur de la puissance thermique effective (C2) qui doit être transférée audit gaz d'entrée dans ledit conduit d'entrée par lesdits moyens de génération de puissance thermique (4; 4').
  2. Système selon la revendication 1), caractérisé en ce qu'il comprend des moyens de détection de la température (17) dudit gaz dans ledit conduit de sortie (3) reliés auxdits moyens de contrôle (14) desdits moyens de génération de puissance thermique (4; 4').
  3. Système selon la revendication 1), caractérisé en ce que lesdits moyens de contrôle (14) comprennent des moyens pour contrôler la température (T1, H2O) dudit fluide de chauffage.
  4. Système selon la revendication 1), caractérisé en ce que lesdits moyens de génération de puissance thermique (4; 4') comprennent une ligne de refoulement (8) dudit fluide entre lesdits moyens de chauffage (7; 7') et lesdits moyens échangeurs (6; 6'), et une ligne de retour (9) dudit fluide entre lesdits moyens échangeurs (6; 6') et lesdits moyens de chauffage (7; 7').
  5. Système selon l'une quelconque des revendications précédentes, caractérisé en ce que lesdits moyens de détection (18) aptes à mesurer le débit (Qu,gas) dudit gaz comprennent un compteur de gaz (19) relié de manière opérationnelle à un correcteur de volumes (20) apte à produire en sortie la valeur dudit débit (Qu,gas) dudit gaz.
  6. Système (1; 1') de réduction de la pression d'un gazentre un conduit d'entrée (2) et un conduit de sortie (3) comprenant des moyens de réduction de la pression (5; 5') entre ledit conduit d'entrée (2) et ledit conduit de sortie (3), caractérisé en ce qu'il comprend un système de chauffage selon l'une quelconque des revendications précédentes.
  7. Méthode pour le chauffage d'un gazen transit entre un conduit d'entrée (2) et un conduit de sortie (3), où la pression dudit gaz dans ledit conduit d'entrée (2) est supérieure à la pression dudit gaz dans ledit conduit de sortie (3), comprenant la phase de chauffage dudit gaz entre ledit conduit d'entrée (2) et ledit conduit de sortie (3), au moyen d'un système de chauffage selon l'une des revendications de 1 à 6, caractérisée en ce que ladite phase de chauffage du gaz est contrôlée sur la base du débit instantané (Qu,gas) mesuré après la réduction de la pression dudit gaz dans ledit conduit de sortie (3) et d'une valeur estimée de l'efficience du système (E1), en calculant, à l'aide desdits moyens de contrôle dudit système utilisant ledit débit (Qu,gas) et ladite efficience du système (E1), la valeur de la puissance thermique effective (C2) qui doit être transférée audit gaz d'entrée dans ledit conduit d'entrée par lesdits moyens de génération de puissance thermique (4, 4').
  8. Méthode selon la revendication7), caractérisée en ce que ladite phase de chauffage du gaz est contrôlée sur la base de la température (Tu,gas) dudit gaz dans ledit conduit de sortie (3).
  9. Méthode selon la revendication 7) ou 8), caractérisée en ce que ladite phase de chauffage du gaz comprend une phase de chauffage d'un fluide et une phase d'échange de l'énergie thermique dudit fluide avec ledit gaz.
  10. Méthode selon la revendication 9), caractérisée en ce que la température (T1,H2O) dudit fluide dans ladite phase de chauffage du fluide est contrôlée sur la base du débit (Qu,gas) dudit gaz dans ledit conduit de sortie (3).
  11. Méthode selon la revendication 9) ou 10), caractérisée en ce que la température (T1,H2O) dudit fluide dans ladite phase de chauffage du fluide est contrôlée sur la base de la température (Tu,gas) dudit gaz dans ledit conduit de sortie (3).
  12. Méthode selon la revendication 11), caractérisée en ce que la température (T1,H2O) dudit fluide dans ladite phase de chauffagedu fluide est contrôlée sur la base de l'écart (S) de la température (Tu,gas) dudit gaz dans ledit conduit de sortie (3) par rapport à une température de référenceprédéterminée (Tu,gas_rif).
EP12729195.3A 2011-05-23 2012-05-18 Système de chauffage de gaz pour systèmes de réduction de pression de gaz et procédé d'obtention dudit effet de chauffage Active EP2715213B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT000132A ITVI20110132A1 (it) 2011-05-23 2011-05-23 Sistema di riscaldamento di un gas in sistemi di riduzione della pressione del gas e metodo atto a realizzare tale riscaldamento.
PCT/IB2012/000983 WO2012160433A1 (fr) 2011-05-23 2012-05-18 Système de chauffage de gaz pour systèmes de réduction de pression de gaz et procédé d'obtention dudit effet de chauffage

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EP2715213B1 true EP2715213B1 (fr) 2015-09-16

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GB2517725C (en) 2013-08-29 2019-12-04 Utility Io Group Ltd Heater suitable for heating a flow of natural gas
IT201600100483A1 (it) * 2016-10-06 2018-04-06 Stefano Oldrati Sistema per il controllo termico di un gas
IT201900004675A1 (it) * 2019-03-28 2020-09-28 Me Te Ma Srl Impianto e procedimento per la regolazione della pressione del gas metano proveniente dalla rete.
EP4411205A1 (fr) * 2023-02-02 2024-08-07 Enersem S.r.l. Procédé de commande du fonctionnement d'une installation de chauffage hybride pour chauffer un gaz et installation de chauffage hybride associée

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Publication number Priority date Publication date Assignee Title
US5606858A (en) * 1993-07-22 1997-03-04 Ormat Industries, Ltd. Energy recovery, pressure reducing system and method for using the same
US6155051A (en) * 1999-04-20 2000-12-05 Williams; Paul R. Method of heating natural gas in a city gate station
HU1991U (en) * 2000-09-25 2001-04-30 Fiorentini Hungary Korlstolt F Equipment group for operating gas pressure reductive station
CN2506848Y (zh) * 2001-11-20 2002-08-21 玉建军 压缩天然气调压装置
DE10246170B4 (de) * 2002-10-02 2005-08-18 Stadtwerke Homburg Gmbh Vorrichtung zur Vorwärmung eines Gases in einer Gasdruckregel- und Messanlage
EP1865249B1 (fr) * 2006-06-07 2014-02-26 2Oc Réducteur de pression de gaz et système de génération et de gestion d'énergie comprenant un réducteur de pression de gaz
CN201285515Y (zh) * 2008-09-02 2009-08-05 天津博思特石油天然气设备有限公司 天然气输气站压力控制系统
KR20110047905A (ko) * 2009-10-31 2011-05-09 유한회사 이지엠에너지홀딩스 연료전지―터보팽창기 통합에너지 회수시스템을 통한 천연가스 정압시설의 에너지 회수 장치 및 에너지 회수 방법
CN201650505U (zh) * 2010-05-04 2010-11-24 宁波九天仪表有限公司 汽车用压缩天然气减压调节器

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