EP3301362A1 - Régulation d'écoulements turbulents - Google Patents

Régulation d'écoulements turbulents Download PDF

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Publication number
EP3301362A1
EP3301362A1 EP16191924.6A EP16191924A EP3301362A1 EP 3301362 A1 EP3301362 A1 EP 3301362A1 EP 16191924 A EP16191924 A EP 16191924A EP 3301362 A1 EP3301362 A1 EP 3301362A1
Authority
EP
European Patent Office
Prior art keywords
flow
fuel
signal
actuator
channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP16191924.6A
Other languages
German (de)
English (en)
Other versions
EP3301362B1 (fr
Inventor
Rainer Lochschmied
Mike Schmanau
Bernd Schmiederer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to ES16191924T priority Critical patent/ES2792874T3/es
Application filed by Siemens AG filed Critical Siemens AG
Priority to PL16191924T priority patent/PL3301362T3/pl
Priority to HUE16191924A priority patent/HUE049484T2/hu
Priority to EP16191924.6A priority patent/EP3301362B1/fr
Priority to RU2017133736A priority patent/RU2674104C1/ru
Priority to CN201710917791.8A priority patent/CN107883399B/zh
Priority to US15/722,129 priority patent/US11175039B2/en
Publication of EP3301362A1 publication Critical patent/EP3301362A1/fr
Application granted granted Critical
Publication of EP3301362B1 publication Critical patent/EP3301362B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/02—Regulating fuel supply conjointly with air supply
    • F23N1/025—Regulating fuel supply conjointly with air supply using electrical or electromechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/02—Regulating fuel supply conjointly with air supply
    • F23N1/022—Regulating fuel supply conjointly with air supply using electronic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/60—Devices for simultaneous control of gas and combustion air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/02—Regulating fuel supply conjointly with air supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/02—Regulating fuel supply conjointly with air supply
    • F23N1/027—Regulating fuel supply conjointly with air supply using mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/18—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel
    • F23N2005/181—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel using detectors sensitive to rate of flow of air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2223/00—Signal processing; Details thereof
    • F23N2223/12—Integration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2223/00—Signal processing; Details thereof
    • F23N2223/14—Differentiation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2225/00—Measuring
    • F23N2225/04—Measuring pressure
    • F23N2225/06—Measuring pressure for determining flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2233/00—Ventilators
    • F23N2233/06—Ventilators at the air intake
    • F23N2233/08—Ventilators at the air intake with variable speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/02—Air or combustion gas valves or dampers
    • F23N2235/06—Air or combustion gas valves or dampers at the air intake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/02—Air or combustion gas valves or dampers
    • F23N2235/10—Air or combustion gas valves or dampers power assisted, e.g. using electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/18—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel

Definitions

  • the present disclosure deals with the control of flows of a fluid in a combustion device.
  • the present disclosure addresses the control of flows of fluids, such as air, in the presence of turbulence.
  • speed encoders are not sensitive to fluctuations in air temperature and pressure.
  • a disadvantage of air pressure switches is that an air pressure monitoring succeeds only at a certain pressure. After all, can be monitored by using multiple switches air pressure at several pressures. Nevertheless, a readjustment in the entire operating range of the combustion device is hardly possible so far. A solution for adjustment at one point further requires two units.
  • EP1236957B1 issued on November 2, 2006, deals with the adaptation of a burner-operated heater to an air-exhaust system.
  • EP1236957B1 discloses a pressure sensor / air mass sensor 28 disposed in the air supply 14 or exhaust discharge of a heater.
  • a regulator 30 regulates a fan 26 based on the signal from the sensor 28.
  • An operating characteristic 40 is stored for balancing the instantaneous air volume flow to a required air volume flow.
  • a temperature sensor 35 is provided.
  • EP2556303B1 is issued on February 24, 2016 and deals with a mass balance pneumatic joint.
  • EP2556303B1 discloses a Venturi nozzle 5, which generates negative pressure, with a mass flow sensor 6 in an additional channel 7.
  • a control or regulation 9 regulates the rotational speed of a blower 1 as a function of the signal of the sensor 6.
  • German patent DE102004055715B4 is issued on March 22, 2007 and deals with the adjustment of the air ratio of a firing device. According to DE102004055715B4 an air mass flow m L is so controlled to an increased value that a hygienic combustion occurs.
  • the aim of the present disclosure is to improve the control of flows in combustion devices, especially in the presence of turbulence.
  • a side channel is connected to a feed and / or with a discharge for a gaseous fluid in the combustion device.
  • the side channel is connected to the supply or discharge such that a fluid from the supply and / or discharge can flow into the side channel.
  • at least one flow resistance element is introduced.
  • the mass flow sensor in the side channel becomes insensitive to solid components and / or droplets in the fluid that might otherwise impact the mass flow sensor. If necessary, impinging solid components and / or droplets in the fluid can damage the mass flow sensor.
  • the flow resistance element reduces the turbulence of the flow at the mass flow sensor.
  • a control device is now connected to at least a first, controlled actuator and at least one second, controlled actuator. Both actuators set the desired flow of air.
  • the controller initially sets the controlled actuator for the fuel according to the desired flow in the main channel (supply and / or discharge) based on values stored and / or determined.
  • the control device now determines the flow in the main channel based on the signal of the mass flow sensor in the side channel. It then forms the difference to the setpoint.
  • the control device regulates based on the difference formed the second, controlled actuator.
  • the determination of the desired flow of air or fuel is the result of a higher temperature control.
  • the temperature of a medium and / or goods in the heat consumer is maintained at a target desired value by means of a temperature control.
  • the quantity setting of one or more actuators for adjusting the air flow is determined via a respective stored functional relationship from a predetermined air flow.
  • one of the actuators for adjusting the air flow with the help of the flow sensor in the side channel is adjusted so that the predetermined value of the air flow is achieved.
  • the amount adjustment of the fuel and the air flow are assigned to each other. Such can be done either by a fixed assignment and / or by an assignment as a result of a ⁇ -control.
  • Another related goal is to determine burner performance via the air flow rate determined by the side channel mass flow sensor.
  • the mass flow sensor compensates for influences such as air temperature and / or barometric pressure on the air. If the air ratio ⁇ is kept constant by means of a control, the burner output remains (almost) the same regardless of the type of fuel.
  • the filter is filtered on the basis of a moving average filter and / or on the basis of a filter with finite impulse response and / or on the basis of a filter with infinite impulse response and / or on the basis of a Chebyshev filter.
  • FIG. 1 shows a system comprising a burner 1, a heat consumer 2, a fan 3 with adjustable speed and a motorized flap 4.
  • the motorized flap 4 is disposed after the air inlet 27.
  • the heat consumer 2 heat exchanger
  • the flow (particle flow and / or mass flow) 5 of the fluid air can according to FIG. 1 be adjusted both by the motorized flap 4 and by the speed specification 22 of the blower.
  • the speed of the fan 3 can also be adjusted by the speed of the fan 3 in the absence of flap 4, the air flow 5.
  • the speed of the fan 3 for example, pulse width modulation comes into question.
  • the motor of the fan is connected to a converter. The speed of the fan is thus adjusted via the frequency of the inverter.
  • the fan runs at a fixed, unchangeable speed.
  • the air flow rate 5 is then determined by the position of the flap 4.
  • other actuators are possible, which change the air flow 5. This may be, for example, a nozzle adjustment of the burner and / or an adjustable flap in the exhaust duct.
  • the flow 6 (eg, particle flow and / or mass flow) of the fluid fuel through the fuel supply passage 38 is adjusted by a fuel flap 9.
  • the fuel flap 9 is a (motor-adjustable) valve.
  • the flap 9 is powered by a motor adjustable oil pressure regulator replaced in the return of the oil nozzle.
  • the safety shutdown function and / or closing function is implemented by the redundant safety valves 7 - 8.
  • the safety valves 7 - 8 and / or the fuel flap 9 are implemented as an integrated unit (s).
  • the burner 1 is an internal combustion engine.
  • an internal combustion engine of a plant with combined heat and power in question is an internal combustion engine.
  • Fuel is added to the air stream 5 in and / or in front of the burner 1.
  • the mixture is burned in the combustion chamber of the heat consumer 2.
  • the heat is transported on in the heat consumer 2.
  • heated water is removed via a pump to heating elements and / or heated in industrial furnaces a good (direct).
  • the exhaust stream 10 is discharged via an exhaust path 30, such as a chimney, (in the environment).
  • a regulation and / or control and / or monitoring device 16 coordinates all actuators such that the correct flow rate 6 of fuel is adjusted via the position of the flap 9 to the corresponding throughput 5 of air for each power point. This results in the desired air ratio ⁇ .
  • the control and / or control and / or monitoring device 16 is designed as a microcontroller.
  • control and / or control and / or monitoring device 16 the blower 3 via the signal 22 and the air damper 4 via the signal 23 in the control and / or control and / or monitoring device 16 (in the form of a Characteristic curve).
  • the regulation and / or control and / or monitoring device 16 comprises a (non-volatile) memory. In the store are those Values stored. The position of the fuel flap 9 is specified via the signal 26.
  • the safety shut-off valves 7, 8 are opened via the signals 24, 25. The safety shut-off valves 7, 8 are kept open during operation.
  • a safety-related position message can be realized, for example, via redundant position encoders. If a safety-related feedback on the speed is required, this can be done via the (bidirectional) signal line 22 using (safety-related) speed sensors. For this example, redundant speed sensor can be used and / or the measured speed can be compared with the target speed.
  • the control and feedback signals can be transmitted via different signal lines and / or via a bidirectional bus, for example a CAN bus.
  • a side channel 28 is attached. Through the side channel 28 flows a small amount of outflowing air 15 to the outside. Ideally, the air 15 flows into the space from which the blower 3 attracts the air. According to another embodiment, the outflowing air 15 flows into the combustion chamber of the heat consumer 2. According to yet another embodiment, the air flows back into the air duct 11. In this case, a flow resistance element (an orifice) is arranged in the air duct 11 between the tap and return (at least locally).
  • the side channel 28 can be both an outflow channel and an inflow channel with respect to the air channel 11, depending on the pressure conditions.
  • a flow resistance element in the form of a diaphragm 14 is attached.
  • the flow resistance element 14 the amount of outflowing air 15 of the flow divider is defined.
  • the person skilled in the art recognizes that the function of the diaphragm 14 as a defined flow resistance can also be realized by a tube of defined length (and diameter).
  • the skilled person further recognizes that the function of the diaphragm 14 can also be realized by means of a laminar flow element and / or by another defined flow resistance.
  • the passage area of the flow resistance element 14 is adjustable by motor. To avoid and / or remedy obstruction by suspended particles, the passage area of the flow resistance element 14 can be adjusted. In particular, the flow resistance element 14 can be opened and / or closed. The passage area of the flow resistance element is preferably adjusted several times in order to avoid and / or remedy blockages.
  • the flow rate 15 in the side channel 28 depends on the passage area of the flow resistance element 14. Therefore, the value of the flow 5 is above values stored in the (non-volatile) memory for the measured values of the flow 15 for each passage area used Flow resistance element 14 deposited. Thus, the value of flow 5 can be determined from the measured values of the flow 15.
  • the flow (particle flow and / or mass flow) through the side channel 28 is a measure of the air flow 5 through the burner.
  • influences due to changes in the density of the air are compensated, for example, by changes in the absolute pressure and / or the air temperature by the mass flow sensor 13.
  • the flow 15 is much smaller than the air flow 5.
  • the air flow 5 (practically) is not affected by the side channel 28.
  • the (particle and / or mass) flow 15 through the side channel 28 is at least a factor of 100, preferably at least a factor of 1000, more preferably at least a factor of 10000 less than the (particle and / or Mass) stream 5 through the air duct 11th
  • FIG. 2 the section in the area of the side channel 28 is shown enlarged.
  • a mass flow sensor 13 By means of a mass flow sensor 13, the value of the air flow 15 in the side channel 28 is detected.
  • the signal of the sensor is transmitted via the signal line 21 to the control and / or control and / or monitoring device 16.
  • the control and / or control and / or monitoring device 16 the signal is mapped to a value of the air flow 15 through the side channel 28 and / or the air flow 5 through the air duct 11.
  • a signal processing device is present at the location of the mass flow sensor 13.
  • the signal processing device has a suitable interface in order to transmit a signal (processed to a value of the air flow) to the regulating and / or control and / or monitoring device 16.
  • Sensors such as the mass flow sensor 13 allow the measurement at high flow rates, especially in conjunction with Incinerators in operation. Typical values of such flow rates are in the ranges between 0.1 m / s and 5 m / s, 10 m / s, 15 m / s, 20 m / s, or even 100 m / s.
  • Mass flow sensors suitable for the present disclosure include OMRON® D6F-W or Type SENSOR TECHNICS® WBA sensors.
  • the usable range of these sensors typically begins at speeds between 0.01 m / s and 0.1 m / s and ends at a speed such as 5 m / s, 10 m / s, 15 m / s, 20 m / s, or even 100 m / s.
  • lower limits such as 0.1 m / s can be combined with upper limits such as 5 m / s, 10 m / s, 15 m / s, 20 m / s, or even 100 m / s.
  • the signal processing device may include a filter.
  • the filter averages over fluctuations in the signal caused by turbulence.
  • a suitable filter such as a moving average filter, a finite impulse response filter, an infinite impulse response filter, a Chebyshev filter, etc.
  • the filter is implemented as a (programmable) electronic circuit.
  • the combination of stagnation probe 12, flow resistance element 14 and filter is advantageous.
  • the filter can be compensated frequency components of the fluctuations of the signal of the mass flow sensor 13, which can hardly compensate for the jam probe 12 and / or over the flow resistance element 14.
  • the jam probe 12 integrates pressure fluctuations of the mass flow 5 in the feed channel 11 of greater than 10 Hz, more preferably greater than 50 Hz.
  • the flow resistance element 14 dampens pressure fluctuations of the mass flow 5 in the feed channel 11 by a factor of 5, more preferably more than a factor of 10 or even more than a factor of 40.
  • the filter integrates fluctuations in the range greater than 1 Hz, preferably greater than 10 Hz.
  • individual or all signal lines 21-26 are designed as (eight-wire) computer network cables with (or without) integrated energy transmission in the cable.
  • the units connected to the signal lines 21-26 not only communicate via the signal lines 21-26, but they are also supplied with energy for their operation via suitable signal lines 21-26.
  • powers up to 25.5 watts can be transmitted through signal lines 21-26.
  • individual or all units connected to the signal lines 21-26 have internal energy stores such as accumulators and / or (super) capacitors.
  • the power supply of the connected units is ensured in the event that the power of those units exceeds the powers that can be transmitted via the signal lines 21-26.
  • the signals may also be transmitted over a two-wire bidirectional bus, e.g. a CAN bus are transmitted.
  • FIG. 2 illustrated form of measuring a flow in a side channel 28 is particularly advantageous for combustion devices.
  • the air flow 5 in the air duct 11 between the fan 3 and burner 1 is (often) turbulent.
  • the flow fluctuations due to turbulence are in the same order of magnitude as the average value of the air stream 5. This makes a direct measurement of the value of the air stream 5 (considerably) more difficult.
  • the flow fluctuations occurring in the side channel 28 fall significantly lower than the flow fluctuations generated in the air duct 11 by the blower 3.
  • the side channel 28 is constructed so that one receives (practically) no relevant macroscopic flow profile of the air stream 15.
  • In the side channel 28 of the air flow 15 preferably laminar sweeps over the mass flow sensor 13.
  • the expert uses, inter alia, the Reynolds number Re D for dividing the mass flow 15 of a fluid in the side channel 28 with diameter D in laminar or turbulent.
  • Reynolds numbers Re D ⁇ 4000 more preferably with Re D ⁇ 2300, further preferably with Re D ⁇ 1000 as laminar.
  • the passage area of the flow resistance element 14 is dimensioned to give rise to a defined, preferably laminar, flow profile (of a mass flow 15) in the side channel 28.
  • a defined flow profile in the side channel 28 is characterized by a defined velocity distribution of a mass flow 15 as a function of the radius of the side channel 28. The mass flow 15 thus does not run chaotically.
  • a defined flow profile is unique for each flow rate 15 in the side channel 28. With a defined flow profile, the flow value measured locally on the mass flow is representative of the flow rate in the side channel 28. It is thus representative of the flow rate 5 in the feed channel 11.
  • a defined flow profile (of a mass flow 15) in the side channel 28 is preferably not turbulent.
  • a defined flow profile (of a mass flow 15) in the side channel 28 may have a (parabolic) velocity distribution as a function of the radius of the side channel 28.
  • the air flow 15 can be directed via a baffle probe 12 into the side channel 28.
  • the jam probe 12 is arranged in the air channel 11.
  • the jam probe 12 is in the form of a tube of any cross-section (for example, round, angular, triangular, trapezoidal, preferably round) executed.
  • the end of the tube 12 in the direction of the main air flow 5 is closed.
  • the end of the tube, which protrudes from the tube with the main flow 5 forms the beginning of the side channel 28. That end opens into the side channel 28.
  • several Openings for example, slots and / or holes
  • the total area of the openings 31 (the cross-section through the openings 31) is significantly greater than the passage area of the flow resistance element 14.
  • the passage area of the flow resistance element 14 is (practically) determining the value of the air flow 15 through the side channel 28.
  • the total flow-through cross section of the openings 31 is at least a factor of 2, preferably at least a factor of 10, particularly preferably at least a factor of 20, greater than the passage area of the flow resistance element 14.
  • the person skilled in the art will choose a small area for the total area of the openings 31 in relation to the cross section of the jam probe 12. Thus fluctuations of the turbulent main flow 5 (practically) do not affect. In the tube of the jam probe builds a calm back pressure.
  • the total flow-through cross section of the openings 31 is at least a factor of 2, preferably at least a factor of 5, particularly preferably at least a factor of 10, smaller than the cross section of the jam probe 12.
  • a further advantage of the arrangement is that suspended particles and / or droplets are less likely to enter the side channel 28. Due to the much lower speeds of the air in the side channel 28 and the back pressure in the jam probe 12 are suspended particles and / or droplets in the turbulent main flow. 5 further swirled. Larger solid particles and / or droplets can hardly reach the jam probe 12 due to the dynamic pressure and due to the openings 31. You will be whirled past the jam probe 12.
  • the individual openings of the inlet 31 preferably have a diameter of less than 5 mm, more preferably less than 3 mm, particularly preferably less than 1.5 mm.
  • the person skilled in the art applies the openings 31 along the baffle probe 12 such that the mean value of the dynamic pressure forms over a macroscopic flow profile of the air flow 5 in the baffle probe 12.
  • the person skilled in the art will select a jam probe 12 of defined length in order to smooth a macroscopic flow profile of the air flow 5 in the interior of the tube. It adjusts via a matched to the air duct 11 length of the jam probe 12, the respective flow conditions for differently designed air ducts 11 at. This is especially true for air ducts with different diameters.
  • FIG. 3 shows as opposite FIG. 1 modified embodiment, a system with a motorized air damper 4.
  • the air damper 4 is located downstream of the fan 3.
  • the louver 4 is also located downstream of the side channel 28.
  • the system off FIG. 3 allows the determination of a position of the air damper 4 and / or the fan speed for each power point. This results (reversibly unambiguously) from each flow value 5 and the (confirmed) position of the air damper 4 and / or the (feedback) speed of the blower 3, a flow value 15 in the side channel 28th
  • FIG. 4 shows as opposite FIG. 1 and FIG. 3 modified embodiment, a system with mixing device 17 in front of the blower 3.
  • Fuel is not mixed with the burner 1 with air. Instead, fuel is mixed by means of a mixing device 17 in front of the blower 3 the air stream 5. In the blower 3 (and in the channel 11) is therefore the fuel-air mixture.
  • the Fuel-air mixture is then burned in the burner 1 in the combustion chamber of the heat consumer 2.
  • the air 15 flows on the suction side via the mass flow sensor 13.
  • the blower 3 generates a negative pressure at this location.
  • the side channel 28 is an inflow channel.
  • the side channel 28 is advantageously arranged in front of the mixing device 17. Thus, a possible negative pressure generated by the mixing device 17 does not affect the flow 15 (particle flow and / or mass flow) through the side channel 28.
  • the fluid flow 5 can be adjusted only via the fan 3 by means of the signal line 22.
  • a (motorized flap) can be additionally installed. Such a flap is arranged on the pressure side or suction side to the blower 3.
  • the flap may be installed instead of the flow resistance element 18 according to another embodiment. It is then practically designed as a motor-adjustable flow resistance element (with feedback).
  • the mass flow sensor 13 is (for the skilled person easy) suction side to attach virtually any system. Also in FIG. 3 and FIG. 4 compensate for the disclosed systems Density changes of the air like to FIG. 1 explained. In each case, the particle and / or mass flow 5 of the fluid through the burner 1 is determined.
  • the measurement of the flow 15 in the side channel 28 takes place with a mass flow sensor 13.
  • the mass flow sensor 13 is arranged in the inflow channel / outflow channel 28.
  • the mass flow sensor 13 operates advantageously according to the anemometer principle.
  • an (electrically) operated heater heats the fluid.
  • the heating resistor can also be used as a temperature measuring resistor.
  • the reference temperature of the fluid is measured.
  • the reference temperature measuring element can also be designed as a resistor, for example in the form of a PT-1000 element.
  • the heating resistor and reference temperature resistor are arranged on a chip.
  • the person skilled in the art recognizes that in this case the heating must be thermally sufficiently decoupled from the reference temperature measuring element.
  • the anemometer can be operated in two possible ways.
  • the heating resistor is heated with a constant, known heating power, heating voltage and / or heating current.
  • the differential temperature of the heater to the reference temperature measuring element is a measure of the flow (particle flow and / or mass flow) in the side channel 28. It is thus also a measure of the flow 5 (particle flow and / or mass flow) of the main flow (through channel 11).
  • the heater is heated in a closed temperature control loop. This results in a constant temperature of the heater.
  • the temperature of the heater is the same as the temperature of the setpoint of the control loop (except for variations due to regulation).
  • the setpoint of the temperature of the heater is determined by a constant temperature difference to the measured temperature of the heater Reference temperature measuring element is added.
  • the constant temperature difference thus corresponds to the overtemperature of the heater relative to the reference temperature measuring element.
  • the power introduced into the heater is a measure of the flow (particle flow and / or mass flow) in the side channel 28. It is therefore also a measure of the flow 5 (particle flow and / or mass flow) of the main flow.
  • the measuring range of the flow sensor may under certain circumstances correspond to a low flow 15 in the side channel 28. Consequently, with sufficiently high blower pressure, the passage area of the flow resistance element 14, which determines the flow 15, must be made small. With such small passage areas there is a risk that the flow resistance element 14 is clogged by suspended particles.
  • FIG. 5 teaches how in such cases a pressure divider with bypass channel 29 can be constructed.
  • a second flow resistance element 19 Behind the first flow resistance element 14 with a larger passage area is then a second flow resistance element 19.
  • the passage surfaces of the flow resistance elements 14 and 19 determine the division of the pressure.
  • a further flow resistance element 20 is arranged before the mass flow sensor 13 in the bypass channel 29, .
  • the skilled person selects the passage area of the flow resistance element 20 sufficiently large.
  • the person skilled in the art also selects a passage surface of the flow resistance element 20 adapted to the mass flow sensor 13. With the subflow divider constructed in this way, the flow 5 (particle flow and / or mass flow) through channel 11 can then be closed (reversibly unambiguously).
  • the mass flow sensor 13 can be implemented redundantly (twice) with result comparison.
  • the double version initially concerns the Mass flow sensor 13 itself and the signal processing device.
  • the result comparison can then be carried out in a secure hardware and / or software at the location of the sensors and / or in the control and / or monitoring and / or monitoring device 16.
  • the side channel 28 is implemented redundantly (twice).
  • each redundant side channel 28 includes a flow resistance element 14.
  • the branch for the second side channel is in this case preferably between flow resistance element 14 and jam probe 12.
  • the jam probe 12 can be assumed to be failsafe due to the (comparatively) large openings 31.
  • the measured values of the redundant mass flow sensors 13, preferably each with additional averaging are compared by subtraction.
  • the difference ⁇ is then within a threshold band - ⁇ 1 ⁇ ⁇ ⁇ ⁇ 2 with the limits ⁇ 1 and ⁇ 2 .
  • the difference ⁇ are compared and evaluated for each set value of the flow rate. 5
  • the flow 5 (particle flow and / or mass flow) through channel 11 can be regulated by means of the sensor signal 21 via the blower 3.
  • all air actuators 4, except for the rotational speed of the blower 3 are each set to a fixed setpoint position.
  • the target positions are for the required flow 5 (particle flow and / or mass flow) through channel 11 in the control and / or control and / or monitoring device 16 deposited. Based on a closed loop, the speed of the blower 3 is adjusted so far until the sensor measured value 21 reaches the value stored in the memory for the required flow.
  • FIG. 6 shows the control loop.
  • the required value for the required flow 5 (particle flow and / or mass flow) through channel 11 associated setpoint 32 for the flow 15 in the side channel 28 is stored in the memory of the control and / or control and / or monitoring device 16.
  • a comparison between the desired value 32 and the signal 21 of the mass flow sensor 13 results in a desired-actual deviation 33 via a (difference) device 35.
  • a controller 37 for example as a (self-adapting) PI controller or as (self-adapting ) PID controller can be executed, the control signal 22 for the fan 3 is specified.
  • the fan 3 generates in response to the control signal 22 the flow 5 (particle flow and / or mass flow) through channel 11.
  • the signal 21 with the aid of the aforementioned measuring arrangement 34 comprising the side channel 28, at least one flow resistance element 14, the mass flow sensor 13 and optionally the Stausonde 12 generated.
  • the signal 21 is a (reversibly unique) measure of the flow 5 (particle flow and / or mass flow) through channel 11.
  • the control loop disclosed here compensates for changes in air density. Such changes occur, for example, as a result of temperature fluctuations and / or changes in the absolute pressure.
  • the controller 29 can also be realized as a fuzzy logic controller and / or as a neural network.
  • the actuating signal 22 for the blower 3 can be, for example, a pulse-width-modulated signal.
  • the control signal 22 for the blower 3 is an alternating current generated by a (matrix) converter. The frequency of the Alternating current corresponds (is proportional to) the speed of the blower 3.
  • the setpoint positions of the actuators 4 must be determined to be fail-safe. This is done, for example, by means of two position sensors (angle encoder, stroke transmitter, light barrier etc).
  • the optional (electronic) filter 36 smoothes the measurement signal.
  • the filter 36 may be adaptive in one embodiment.
  • the measurement signal is averaged over a long, maximum integration time (for example, two seconds to five seconds) as a comparison value with a moving average filter. If a measured value deviates from the mean value of the measured values or, alternatively, from the desired value 32 outside of a predetermined band, a setpoint jump is assumed. The measured value is now used directly as the actual value. Consequently, the control loop immediately reacts with the sampling rate of the control loop.
  • the integration time is incrementally increased with (every) sampling of the control loop.
  • the value integrated in this way is used as the actual value. This takes place until the maximum integration time has been reached.
  • the control loop is now considered stationary.
  • the value thus averaged is now used as the actual value.
  • the disclosed method enables an accurate stationary measurement signal with maximum dynamics.
  • the Function tabulated.
  • Intermediate values between the points defined by the table are linearly interpolated.
  • intermediate values between the points defined by the table are interpolated by a polynomial over several adjacent values and / or over (cubic) splines. The person skilled in the art recognizes that other forms of interpolation can also be realized.
  • the regulating and / or control and / or monitoring device 16 has a reading device for identification by means of radiofrequent waves (RFID reading device).
  • RFID reading device The regulating and / or control and / or monitoring device 16 is designed to read in operating parameters such as formulas (of section-defined polynomials) and / or like the aforementioned tables from a so-called (RFID) transponder on the basis of the reading device.
  • the operating parameters are then stored in the (non-volatile) memory of the control and / or control and / or monitoring device 16. If required, they can be read out and / or used by a microprocessor.
  • the two values between which the desired value of the flow 5 lies are searched in the table. Subsequently, the position between the two values is determined. If the desired value of the flow 5 is an amount s% between the values k and k + 1 (1 ⁇ k ⁇ n), then the angle of the (motor-adjustable) flap or valve 4 at a distance of s% between the angles k and k + 1 approached. The same applies to the angle (position) of the (motor-adjustable) further flap or the further valve.
  • the flow value 5 may be indicated as an absolute number and / or relative to a value, preferably to the flow 5 at the highest power value. The flow value is then stored, for example, as a percentage of the flow 5 of the highest power value.
  • the positions of the at least one air actuator 4 are deposited as a polynomial as a function of the flow 5 (particle flow and / or mass flow) through channel 11. According to yet another embodiment, the positions of the at least one air actuator 4 are deposited as sections defined functions as a function of the flow 5 (particle flow and / or mass flow) through channel 11. According to yet another embodiment, the positions of the at least one air actuator 4 are deposited as (valve) opening curve (s).
  • the design can be made fail-safe.
  • the at least one actuator 4 monitored from the above table can approach its position.
  • the flow 15 is detected by the side channel 28 safety-oriented.
  • a predetermined flow 5 is to be adjusted by channel 11
  • the correct combination of positions of at least one actuator 4 and flow 15 is determined by side channel 28 and started. This happens even if the characteristic curve of individual actuators is not linear. With a sequence of characteristic points with a sufficiently close distance from one another, a (nearly) linear scale for the flow rate 5 is obtained. This is of great advantage for the operation of the combustion device.
  • This position can be both the position of a flap and / or the position or opening of a fuel valve and / or a measured flow value of the fuel flow rate 6.
  • the correct fuel flow 6 has always been assigned to each air flow 5.
  • the air flow rate 5 is thus synonymous with the power value, since funded fuel flow rate 6 and air flow rate 5 are firmly connected.
  • the positions of the air actuators 4 and the desired value of the mass flow 32 in air can be as above described in table form interpolated and / or determined by another mathematical assignment.
  • the values for the flow 5 in the control and / or control and / or monitoring device 16 are indicated absolutely. According to another embodiment, the values for the flow 5 in the control and / or control and / or monitoring device 16 are indicated relative to a specific value of the flow. The values for the flow in the control and / or control and / or monitoring device 16 are preferably indicated relative to the maximum throughput 5 (in air) at maximum power.
  • the fuel flow rate 6 is not directly associated with the air flow rate 5.
  • the position of the fuel flap or the fuel valve 9 is assigned to the fuel flow rate 6 in a second functional assignment. This can be done over a table as in the case of air, as shown below.
  • Fuel throughput 6 (motor adjustable) fuel flap or fuel valve 9 Value 1 Angle 1 Value 2 Angle 2 ... ... Value n Angle n
  • the fuel flow rate 6 stored in the table is an absolute or relative value for an air ratio ⁇ 0 .
  • the fuel flow rate 6 stored in the table is also one absolute or relative value for the fuel present in the fuel supply during an adjustment process.
  • the air ratio ⁇ 0 is usually specified during the setting process.
  • the functional assignment takes place during the mentioned setting process.
  • the fuel flow rate 6 of the delivered fuel at a defined air ratio ⁇ 0 is assigned to the air flow rate 5 defined in the linearized scale.
  • the position of the fuel actuator 9 is mapped to a linear scale of the fuel flow rate 6.
  • L ⁇ ⁇ L min ⁇ V ⁇ G together.
  • L min is the minimum air requirement of the fuel, ie the ratio of air flow rate 5, which is necessary under conditions of stoichiometry, in relation to the fuel flow rate 6.
  • L min is a variable which depends on the composition of the fuel or type of fuel.
  • the fuel composition has the minimum air requirement L min0 .
  • V ⁇ L 0 ⁇ 0 ⁇ L min 0 ⁇ V ⁇ G 0 between the air flow rate during the setting process V ⁇ L 0 , the air ratio during the setting process ⁇ 0 , the minimum air requirement during the setting process L min 0 and the fuel flow rate during the setting process V ⁇ G 0 .
  • V ⁇ L V ⁇ L 0 Max ⁇ ⁇ 0 ⁇ L min L min 0 ⁇ V ⁇ G V ⁇ G 0 Max for the air flow rate 5 as a function of the fuel flow rate 6.
  • V ⁇ RL ⁇ ⁇ 0 ⁇ L min L min 0 ⁇ V ⁇ RG
  • V ⁇ RL V ⁇ RG .
  • the relative air flow rate is equal to the relative fuel flow rate as determined during the tuning process relative to the maximum values.
  • the fuel flow rate 6 must be increased by a factor of 1 / F if the air ratio ⁇ is to remain at the same value.
  • the fuel throughput 6 in the case of a change in the composition of the fuel at which the minimum air requirement L min increases by a factor F, the fuel throughput 6 must be reduced by a factor F compared to the setting conditions for a constant air ratio ⁇ .
  • the air flow rate 5 can be increased by a factor of F.
  • both values, air flow 5 and fuel flow 6, are each in a nearly linear scale. Thus, it is sufficient to know the factor F for a power point in order to calculate the fuel flow rate 6 for each power point from the values stored at the setting if the air flow rate 5 is used as the power quantity. When the fuel flow rate 6 is used as the power quantity 5, the correct air flow rate 5 can be equivalently calculated for each power point.
  • the corresponding positions can then be set for a given power value.
  • the delivery rate of the blower 3 can be adjusted accordingly.
  • the current value for the fuel flow rate 6 is thus assigned to the current value of the air flow rate 5 via a fixed factor.
  • a base factor is determined during adjustment as shown above. For a direct representation of air flow 5 or fuel throughput 6, it is ⁇ 0 ⁇ L min 0 . For a representation of air flow rate 5 or fuel throughput 6 relative to the respective maximum values from the adjustment process, it is preferably set to one.
  • the air flow rate 5 or the fuel flow rate 6 are adjusted by the factor 1 / F compared to the stored setting values.
  • the factor F is determined in a further embodiment with changing compositions of the fuel by means of a ⁇ control, this value also applies to all Credits.
  • the power can be changed much faster than the ⁇ control would allow.
  • ⁇ -control and power adjustment are decoupled from each other. This is very advantageous because, due to the system running times or the time constants of the system, the ⁇ control loop controls much slower environmental changes than comparatively the power is to be changed. Typical environmental changes are air temperature, air pressure, fuel temperature and / or fuel type. Such changes usually occur so slowly that the ⁇ -loop is sufficiently fast for this.
  • a ⁇ -control can be realized with the help of an O 2 sensor in the exhaust gas.
  • the person skilled in the art can easily calculate the air ratio ⁇ from the derived measured value of an O 2 sensor in the exhaust gas.
  • FIG. 6 Sketched control loop density fluctuations of the air 5 are corrected due to temperature change and / or barometric pressure fluctuations. Thus, there is already a compensated value for the linearized scale of the air flow 5. The ⁇ control loop only needs to compensate for fluctuations in the gas composition.
  • the fuel throughput 6 is readjusted via the ⁇ control loop as the composition of the fuel changes, so that the burner output remains virtually constant.
  • the reason for this is that the energy content for most commonly used fuels (approximately) linearly correlated with the minimum air requirement L min .
  • the control loop after FIG. 6 also compensates for errors in the blower and / or regulates these. Errors in the fan 3 are for example Increased slippage of the fan wheel and / or errors in the (electronic) control. Furthermore, grosser errors of the blower 3, which can no longer be corrected, can be revealed. For this purpose, it is detected whether the drive speed 22 of the blower 3 is outside a specified for each flow 5 through the channel 11 band. For this purpose, upper and lower limit values of the rotational speed and / or the drive signals 22 of the blower 3 are advantageously stored in the abovementioned table for given flows 5 (particle flow and / or mass flow) through the channel 11.
  • the values are particularly preferably stored in a (non-volatile) memory of the control and / or control and / or monitoring device 16.
  • the deposit of upper and lower limit values for the rotational speed and / or the drive signals 22 of the blower 3 takes place on the basis of functions (section-wise defined) such as straight lines and / or polynomials.
  • the flow 5 through channel 11 can also be regulated by means of another actuator.
  • all actuators including the blower 3 are set in this case, with the exception of the regulated position of the (motorized) flap or the valve 4 to a fixed setpoint position.
  • the respective desired position for a given flow 5 (particle flow and / or mass flow) through channel 11 is stored in the (non-volatile) memory of the control and / or control and / or monitoring device 16.
  • the positions of the actuators and the set point 32 of the flow 15 through the side channel 28 are also deposited here as a function of the flow 5 through channel 11, as already mentioned above. The interpolation is done as stated above.
  • the regulation of the (motorized) flap or valve 4 means that the position of that Actuator is replaced by the speed of the fan 3.
  • An adapted table is shown below: Flow 5 (particle flow and / or mass flow) through channel 11 Blower 3 (motor adjustable) further flap or further valve Set point 32 for flow 15 (particle flow and / or mass flow) through side channel 28 Value 1 Speed 1 Angle 1 Flow value 1 Value 2 Speed 2 Angle 2 Flow value 2 ... ... ... ... ... Value n Speed n Angle n Flow value n
  • the setpoint positions of the actuators must be determined with fail-safe. This is done, for example, with the aid of two position sensors (angle sensor, stroke transmitter, speed sensor, Hall sensor, etc.).
  • the controller 37 By means of the controller 37, the (motor-adjustable) flap 4 or the valve is adjusted until the signal 21 of the mass flow sensor 13 in the side channel 28 reaches the value stored in the memory for the required flow.
  • the rotational speed of the blower 3 can not be changed.
  • the flow 5 through channel 11 is adjusted exclusively via the (motor-adjustable) further flap or the additional valve.
  • the flap position 9 can be taken directly fixed in the table.
  • the assignment of the linearized scale from the fuel flow rate 6 to the linearized scale of the air flow rate 5 is determined by a factor as described above.
  • Portions of a controller or method according to the present disclosure may be implemented as hardware, as a software module executed by a computing unit, or a cloud computer, or as a combination of the foregoing.
  • the software may include firmware, a hardware driver running within an operating system, or an application program.
  • the present disclosure also relates to a computer program product that incorporates the features of this disclosure or performs the necessary steps.
  • the functions described may be stored as one or more instructions on a computer-readable medium.
  • RAM random access memory
  • MRAM magnetic random access memory
  • ROM read only memory
  • EPROM electronically programmable ROM
  • EEPROM electronically programmable and erasable ROM
  • register Hard disk a removable storage device
  • optical storage any suitable medium that can be accessed by a computer or other IT devices and applications.
  • the side channel 28 and the supply channel 11 of the burner device are preferably in fluid communication.
  • the at least one second actuator 3, 4 is preferably designed to receive a control signal 37.
  • the flow 15 through the side channel 28 is preferably a mass flow (of a gaseous fluid).
  • the flow 5 through the feed channel 11 is preferably a mass flow (of a gaseous fluid).
  • the at least one first actuator 4, 3 and the at least one second actuator 3, 4 preferably act serially (in series) on the supply channel 11.
  • the at least one first actuator 4, 3 and the at least one second actuator 3, 4 are preferably in series (in the supply channel 11) arranged.
  • the present disclosure further teaches the aforesaid method, wherein the processing of the requested flow 5 through the supply channel 11 to a target value 32 of the flow 15 through the side channel 28 reversibly unambiguously allocates (the requested flow 5 through the supply channel 11 to the target Value 32 of the flow 15 through the side channel 28).
  • the present disclosure further teaches one of the aforementioned methods, wherein the generation of a control signal (by the controller 37) for the at least one second actuator 3, 4 takes place on the basis of a proportional-integral controller 37.
  • the proportional-integral controller 37 is a self-adaptive controller.
  • the present disclosure further teaches one of the aforementioned methods, wherein the generation of a control signal (by the controller 37) for the at least one second actuator 3, 4 takes place on the basis of a proportional-integral-derivative controller 37.
  • the proportional integral derivative controller 37 is a self-adaptive controller.
  • the present disclosure further teaches one of the aforementioned methods, wherein the at least one second actuator of the burner device comprises an adjustable speed blower 3, wherein the variable speed blower 3 comprises a drive, and wherein preferably the blower 3 is arranged in the supply channel 11 of the burner device ,
  • the present disclosure further teaches one of the aforementioned methods, wherein the generated control signal 22, 23 to the at least one second actuator 3, 4 is a pulse width modulated signal.
  • the present disclosure further teaches one of the aforementioned methods, wherein the generated control signal 22, 23 to the at least one second actuator 3, 4 is an inverter signal having a frequency which corresponds to the rotational speed of the blower 3.
  • the present disclosure furthermore teaches one of the aforementioned methods, wherein the at least one first actuator of the burner device comprises a motor-adjustable flap 4 with a drive and preferably the motor-adjustable flap 4 is arranged in the feed channel 11 of the burner device.
  • the present disclosure further teaches one of the aforementioned methods, wherein a difference between the setpoint value 32 and the actual value 21 is formed by the controller 37 for the at least one second actuator 3, 4 when the control signal 22, 23 is generated.
  • processing the second signal 21 generated by the mass flow sensor 13 comprises filtering the second signal 21 generated by the mass flow sensor 13.
  • the present disclosure further teaches one of the aforementioned methods, wherein the processing of the second signal 21 generated by the mass flow sensor 13 comprises filtering with a 3dB threshold of the second signal 21 generated by the mass flow sensor 13, wherein the 3dB Threshold of the filtering is set up so that fluctuations of the signal 21 of a frequency greater than 1 Hz, preferably greater than 10 Hz, are integrated.
  • the present disclosure further teaches one of the aforementioned methods, wherein the assignment of the requested flow 5 through the supply channel 11 to one (a value of) position of the at least one first actuator 4, 3 is based on a predetermined table, in which values of the requested flow 5 Values of the positions of the at least one first actuator 4, 3 are assigned by the supply channel 11.
  • the present disclosure further teaches one of the aforementioned methods, wherein the assignment of the requested flow 5 through the supply channel 11 to one (a value of) position of the at least one first actuator 4, 3 based on a predetermined table followed by interpolation, wherein in the given Values of the positions of the at least one first actuator 4, 3, preferably also values of the positions of each of the at least one second actuator 3, 4 different actuator assigned.
  • the present disclosure further teaches one of the aforesaid methods, wherein the assignment of the requested flow 5 through the supply channel 11 to one (one value of) position of the at least one first actuator 4, 3 is based on a predetermined (sectionally defined) function (polynomial), in which values of the requested flow 5 values of the positions of the at least one first actuator 4, 3, preferably also values of the positions of each actuator different from the at least one second actuator 3, 4, are assigned by the supply channel 11.
  • a predetermined (sectionally defined) function polynomial
  • the present disclosure further teaches one of the aforementioned methods, wherein when generating the control signal 22, 23 (by the controller 37) for the at least one second actuator 3, 4, the amount of a difference between the setpoint value 32 and actual value 21 is formed and wherein the amount of the difference between target value 32 and actual value 21 is compared with a predetermined threshold value, and wherein preferably the threshold value is a function of the desired value 32.
  • the present disclosure further teaches the aforementioned methods, wherein the (predetermined) lower threshold and / or (predetermined) upper threshold is a function of the requested flow 5 through the feed channel 11.
  • the present disclosure further teaches the aforementioned methods, wherein the controller 37 comprises a (non-volatile) memory and the (predetermined) lower threshold and / or (predetermined) upper threshold are stored in the memory of the controller 37.
  • the controller 37 is preferably designed to read the (predetermined) lower threshold value and / or the (predetermined) upper threshold value from the (non-volatile) memory.
  • controller 37 comprises a (non-volatile) memory and the table and / or the polynomial function are stored in the memory of the controller 37.
  • the controller 37 is preferably formed, the table and / or the read polynomial function from the (non-volatile) memory.
  • the present disclosure further teaches the aforementioned methods, wherein the controller 37 comprises a (non-volatile) memory and the universal table and / or the universal polynomial function are stored in the memory of the controller 37.
  • the controller 37 is preferably designed to read the universal table and / or the universal polynomial function from the (non-volatile) memory.
  • the ⁇ control of the burner device is preferably integrated in the controller 37.
  • the signal generated by the probe in the exhaust passage 30 is preferably a function of an air ratio of a fluid flow in the exhaust passage and / or a function of an oxygen content of a fluid flow in the exhaust passage.
  • the probe in the exhaust duct 30 is preferably a ⁇ -probe and / or an O 2 probe (oxygen probe).
  • the present disclosure further teaches a non-transitory computer-readable storage medium that stores an instruction set for execution by at least one processor that, when executed by a processor, performs one of the aforementioned methods.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Regulation And Control Of Combustion (AREA)
  • Flow Control (AREA)
EP16191924.6A 2016-09-30 2016-09-30 Procédé de régulation d'écoulements turbulents Active EP3301362B1 (fr)

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PL16191924T PL3301362T3 (pl) 2016-09-30 2016-09-30 Sposób regulacji przepływów turbulentnych
HUE16191924A HUE049484T2 (hu) 2016-09-30 2016-09-30 Eljárás turbulens áramlás szabályozására
EP16191924.6A EP3301362B1 (fr) 2016-09-30 2016-09-30 Procédé de régulation d'écoulements turbulents
ES16191924T ES2792874T3 (es) 2016-09-30 2016-09-30 Regulación de flujos turbulentos
RU2017133736A RU2674104C1 (ru) 2016-09-30 2017-09-28 Регулирование турбулентных потоков
CN201710917791.8A CN107883399B (zh) 2016-09-30 2017-09-30 调节紊流流动
US15/722,129 US11175039B2 (en) 2016-09-30 2017-10-02 Regulating turbulent flows

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HUE049484T2 (hu) 2020-09-28
CN107883399A (zh) 2018-04-06
RU2674104C1 (ru) 2018-12-04
EP3301362B1 (fr) 2020-03-25
US20180094809A1 (en) 2018-04-05
ES2792874T3 (es) 2020-11-12
PL3301362T3 (pl) 2020-08-24
CN107883399B (zh) 2020-01-10
US11175039B2 (en) 2021-11-16

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