EP3301362B1 - Method of controlling turbulent flows - Google Patents

Description

background

The present disclosure is concerned with regulating flows of a fluid in a combustion device. In particular, the present disclosure is concerned with regulating flows of fluids such as air in the presence of turbulence.

Fluctuations in the air ratio λ occur due to changes in air temperature and / or air pressure. Combustion devices are therefore set with an excess of air. This measure serves to avoid unsanitary combustion. A disadvantage of the adjustment of combustion devices to an excess of air is a reduced efficiency of the system.

Speed sensors and air pressure switches can also be used to measure the air throughput. A disadvantage of speed sensors is that they are not sensitive to fluctuations in air temperature and air pressure. A disadvantage of air pressure switches is that air pressure monitoring is only possible at a certain pressure. After all, by using several switches, air pressure can be monitored at several pressures. However, readjustment in the entire operating range of the combustion device has hitherto hardly been possible. A solution for adjustment at one point has also previously required two units.

The occurrence of turbulence further complicates the problem because the signal of a flow sensor is strongly influenced by its installation position in the middle of a turbulent flow. In addition, the measurement signal is very noisy due to the turbulence.

The European patent EP1236957B1 was issued on November 2, 2006 and deals with the adaptation of a burner-operated heater to an air-exhaust system. EP1236957B1 discloses a pressure sensor / air mass sensor 28 which is arranged in the air supply 14 or exhaust gas discharge of a heating device. A controller 30 regulates a blower 26 based on the signal from the sensor 28. An operating characteristic curve 40 is stored in order to adjust the instantaneous air volume flow to a required air volume flow. A temperature sensor 35 is provided to improve the control behavior in the event of large temperature differences and with regard to emergency running properties.

The European patent EP2556303B1 is issued on February 24, 2016 and deals with a pneumatic system with mass balancing. EP2556303B1 discloses a Venturi nozzle 5, which generates negative pressure, with a mass flow sensor 6 in an additional channel 7. A controller 9 regulates the speed of a blower 1 as a function of the signal from the sensor 6.

The German patent DE102004055715B4 was issued on March 22, 2007 and deals with the setting of the air ratio of a combustion device. According to DE102004055715B4 an air mass flow m _L is adjusted to an increased value so that hygienic combustion occurs. Other methods for controlling a burner device are from the EP1243857 , the DE102010010952 and the US2009 / 111065 known.

The aim of the present disclosure is to improve the regulation of flows in combustion devices, in particular in the presence of turbulence.

Summary

The present disclosure teaches an improved method for controlling a burner device according to claim 1.

A control device is now connected to at least one first, controlled actuator and to at least one second, controlled actuator. The desired flow of air is set with both actuators. In order to achieve a desired flow of air through the main duct, the control device first sets the controlled actuator for the fuel according to the desired flow in the main duct (supply and / or discharge) on the basis of values stored and / or determined in the control device. 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 the second, regulated actuator based on the difference formed.

The aforementioned control in the presence of turbulence problem is based on the main claims of the present disclosure tackled. Particular embodiments are dealt with in the dependent claims.

It is a related goal that the determination of the desired flow of air or fuel is the result of a higher-level temperature control. The temperature of a medium and / or good in the heat consumer is kept at a target setpoint with the aid of a temperature control.

It is a further related goal that the quantity setting of one or more actuators for setting the air flow is determined from a given air flow via a respectively stored functional relationship. One of the actuators for setting the air flow is regulated with the aid of the flow sensor in the side channel in such a way that the predetermined value of the air flow is reached.

It is a further related goal that the quantity setting of the fuel and the air flow, the value of which is determined with the aid of the flow sensor in the side channel, are assigned to one another. This can be done either by a fixed assignment and / or by an assignment as a result of a λ regulation.

It is another related goal that the burner output is determined via the air flow, which is determined via the mass flow sensor in the side channel. With the aid of the mass flow sensor, influences such as air temperature and / or barometric pressure on the air are compensated. If the air ratio λ is kept constant by means of a control system, the burner output remains (almost) the same regardless of the type of fuel.

It is a related object of the present disclosure, a method and / or an apparatus for controlling To provide flows in combustion devices, the method and / or the device being designed for fail-safe control of a flow in a combustion device.

It is a further object of the present disclosure to provide a method and / or a device for regulating flows in combustion devices, the method and / or the device being designed to detect errors in the combustion device, in particular to detect errors in the actuators Incinerator.

It is a further object of the present disclosure to provide a method and / or a device for regulating flows in combustion devices, at least one actuator being controlled and / or regulated using a pulse-width-modulated signal.

It is a further object of the present disclosure to provide a method and / or a device for regulating flows in combustion devices, at least one actuator being controlled and / or regulated using a converter.

It is a further related object of the present disclosure to provide a method and / or a device for measuring flows in combustion devices, in which the noise generated by turbulence in the signal of the mass flow sensor is filtered using an (electronic and / or digital) circuit. It is advantageous to filter using a moving average filter and / or using a filter with a finite impulse response and / or using a filter with an infinite impulse response and / or using a Tschebyscheff filter.

Brief description of the figures

• FIG 1 zeigt schematisch ein System mit Verbrennungseinrichtung, worin die Strömung eines Fluids in einer Luftzuführung gemessen wird, welches nicht zur Erfindung gehört.
• FIG 2 zeigt schematisch und detailliert den Seitenkanal.
• FIG 3 zeigt schematisch ein System mit einer Verbrennungseinrichtung und mit einer druckseitig angeordneten Luftklappe, welches nicht zur Erfindung gehört.
• FIG 4 zeigt schematisch ein System mit Verbrennungseinrichtung und mit einer Mischeinrichtung vor dem Gebläse, welches nicht zur Erfindung gehört.
• FIG 5 zeigt schematisch einen Seitenkanal mit Umgehungskanal gemäß der Erfindung.
• FIG 6 zeigt schematisch einen Regelkreis für das System.

Various details will become apparent to those skilled in the art from the following detailed description. The individual embodiments are not restrictive. The drawings that accompany the description can be described as follows:

• FIG. 1 shows schematically a system with combustion device, wherein the flow of a fluid in an air supply is measured, which is not part of the invention.
• FIG 2 shows the side channel schematically and in detail.
• FIG 3 shows schematically a system with a combustion device and with an air flap arranged on the pressure side, which is not part of the invention.
• FIG 4 shows schematically a system with a combustion device and with a mixing device in front of the fan, which is not part of the invention.
• FIG 5 shows schematically a side channel with bypass channel according to the invention.
• FIG 6 shows schematically a control loop for the system.

Detailed description

FIG. 1 shows a system comprising a burner 1, a heat consumer 2, a blower 3 with adjustable speed and a motor-adjustable flap 4. The motor-adjustable flap 4 is arranged after the air inlet 27. The heat consumer 2 (heat exchanger) can be, for example, a hot water boiler. The flow (particle flow and / or mass flow) 5 of the fluid air can be according to FIG. 1 can be set both by the motor-adjustable flap 4 and by the speed setting 22 of the fan.

If the flap 4 is missing, the air flow rate 5 can also be adjusted solely by the speed of the fan 3. Pulse width modulation can be used, for example, to adjust the speed of the fan 3. According to another embodiment, the motor of the fan is connected to an inverter. The speed of the fan is therefore adjusted via the frequency of the converter.

According to another embodiment, the fan runs at a fixed, unchangeable speed. The air flow rate 5 is then determined by the position of the flap 4. In addition, further actuators are possible which change the air throughput 5. This can be, for example, an adjustment of the nozzle of the burner and / or an adjustable flap in the exhaust duct.

The flow rate 6 (for example particle flow and / or mass flow) of the fluid fuel through the fuel supply channel 38 is set by a fuel flap 9. According to one embodiment, the fuel flap 9 is a (motor-adjustable) valve.

For example, combustible gases such as natural gas and / or propane gas and / or hydrogen are suitable as fuel. A liquid fuel such as heating oil can also be used as fuel. In this case, the flap 9 is motorized adjustable oil pressure regulator in the return of the oil nozzle replaced. The safety shutdown function and / or closing function is implemented by the redundant safety valves 7-8. According to a special embodiment, the safety valves 7-8 and / or the fuel flap 9 are implemented as an integrated unit (s).

According to a further embodiment, the burner 1 is an internal combustion engine. In particular, an internal combustion engine of a plant with cogeneration is possible.

Fuel is added to the air stream 5 in and / or upstream of the burner 1. The mixture is burned in the combustion chamber of the heat consumer 2. The heat is transported in the heat consumer 2. For example, heated water is discharged to heating elements via a pump and / or an item is heated (directly) in industrial furnaces. The exhaust gas flow 10 is discharged (into the environment) via an exhaust gas path 30, for example a chimney.

A regulating and / or control and / or monitoring device 16 coordinates all actuators in such a way that the correct throughput 6 of fuel is set 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 λ. According to a special embodiment, the regulating and / or control and / or monitoring device 16 is designed as a microcontroller.

For this purpose, the regulating and / or control and / or monitoring device 16 sets the blower 3 via the signal 22 and the air flap 4 via the signal 23 to the in the regulating and / or control and / or monitoring device 16 (in the form of a Characteristic). The regulating and / or control and / or monitoring device 16 preferably comprises a (non-volatile) memory. Those are in the memory Values stored. The position of the fuel flap 9 is specified via the signal 26. In operation, 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.

If faults in a flap 4, 9 and / or in the blower 3 (for example in the (electronic) interface or control device of the flap and / or the blower) are to be uncovered, this can be done by a safety-related feedback of the position of the flap 4 via the (bidirectional ) Signal line 23 for the flap 4 and / or via the (bidirectional) signal line 26 for the flap 9. A safety-related position report can be implemented, for example, using redundant position transmitters. If a safety-related feedback about the speed is required, this can take place via the (bidirectional) signal line 22 using (safety-related) speed sensors. For this purpose, redundant speed sensors can be used, for example, 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 provided in front of the burner. A small amount of outflowing air 15 flows out through the side channel 28. Ideally, the air 15 flows out into the room from which the fan 3 draws the air. According to another embodiment, the outflowing air 15 flows into the combustion chamber of the heat consumer 2. According to a further different 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 the return (at least locally). The side channel 28 forms a flow divider together with the burner 1 and the exhaust gas path 30 of the heat consumer 2. For a fixed flow path through burner 1 and exhaust gas path 30 flows for a value of Airflow 5 (reversibly unique) from an associated value of an airflow 15 through the side channel 28. The flow path through burner 1 and exhaust gas path 30 only has to be defined for each performance point. It can therefore vary over the performance (and therefore over the air flow).

The person skilled in the art recognizes that 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 an orifice) 14 is attached in the side channel 28. With 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 orifice 14 as a defined flow resistance can also be realized by a tube of a defined length (and diameter). The person skilled in the art further recognizes that the function of the orifice 14 can also be realized using a laminar flow element and / or by means of another defined flow resistance.

According to a special embodiment, the passage area of the flow resistance element 14 is adjustable by a motor. The passage area of the flow resistance element 14 can be adjusted in order to avoid and / or eliminate blockages caused by floating particles. 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 eliminate 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 via characteristic values stored in the (non-volatile) memory for the measured values of the flow 15 for each passage area used Flow resistance elements 14 deposited. The value of flow 5 can thus be determined from the measured values of flow 15.

With this arrangement, 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 density of the air are compensated for by changes in the absolute pressure and / or the air temperature by the mass flow sensor 13. The flow 15 is normally very much smaller than the air flow 5. The air flow 5 is therefore (practically) not influenced by the side channel 28. According to a special embodiment, the (particle and / or mass) flow 15 through the side channel 28 is at least a factor 100, preferably at least a factor 1000, more preferably at least a factor 10000, less than the (particle and / or Mass) stream 5 through the air duct 11.

In FIG 2 the detail in the area of the side channel 28 is shown enlarged. With the aid of a mass flow sensor 13, the value of the air flow 15 in the side channel 28 is recorded. The signal from the sensor is transmitted to the regulating and / or control and / or monitoring device 16 via the signal line 21. In the regulating and / or control and / or monitoring device 16, the signal is mapped to a value of the air flow 15 through the side duct 28 and / or the air flow 5 through the air duct 11. According to a further embodiment, 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 (to a value of the air flow) processed 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 velocities especially in connection with Incinerators in operation. Typical values of such flow velocities are 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 which are suitable for the present disclosure are, for example, 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. In other words, lower limits like 0.1 m / s can be combined with upper limits like 5 m / s, 10 m / s, 15 m / s, 20 m / s, or even 100 m / s.

Regardless of whether the signal processing takes place in the regulating and / or control and / or monitoring device 16 or at the location of the mass flow sensor 13, the signal processing device can contain a filter. The filter averages over fluctuations in the signal caused by turbulence. To this end, the person skilled in the art chooses a suitable filter, such as a moving average filter, a filter with a finite impulse response, a filter with an infinite impulse response, a Chebyshev filter, etc. According to a special embodiment, the filter is designed as a (programmable) electronic circuit.

The combination of damming probe 12, flow resistance element 14 and filter is advantageous. The filter allows frequency portions of the fluctuations in the signal of the mass flow sensor 13 to be compensated for, which can hardly be compensated for via the damming probe 12 and / or the flow resistance element 14. The damming probe 12 preferably 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 preferably 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. Complementary to this, the filter integrates fluctuations in the range greater than 1 Hz, preferably greater than 10 Hz. According to a further special embodiment, individual or all signal lines 21 - 26 are designed as (eight-wire) computer network cables with (or without) energy transmission integrated in the cable. The units connected to the signal lines 21-26 advantageously communicate not only via the signal lines 21-26, but are also supplied with energy for their operation via suitable signal lines 21-26. Power up to 25.5 watts can ideally be transmitted through signal lines 21-26. It is provided that individual or all of the units connected to the signal lines 21 - 26 have internal energy stores such as accumulators and / or (super) capacitors. This ensures in particular the energy supply to the connected units in the event that the powers of those units exceed the powers which can be transmitted via the signal lines 21-26. Alternatively, the signals can also be transmitted via a two-wire, bidirectional bus, eg a CAN bus.

In the FIG 2 The 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 the burner 1 is (in many cases) turbulent. The flow fluctuations due to turbulence are of the same order of magnitude as the average value of the air flow 5. This makes a direct measurement of the value of the air flow 5 (considerably) more difficult. The flow fluctuations occurring in the side duct 28 are significantly smaller than the flow fluctuations in the air duct 11 generated by the fan 3 FIG 2 Arrangement shown a significantly improved signal-to-noise ratio of the signal of the mass flow sensor 13. The side channel 28 is constructed so that (practically) no relevant macroscopic flow profile of the air flow 15 is obtained. In the side channel 28, the air flow 15 preferably sweeps laminarly over the mass flow sensor 13. The person skilled in the art uses, among other things, the Reynolds number Re _D for dividing the mass flow 15 of a fluid in the side channel 28 with diameter D into laminar or turbulent. According to one Embodiments apply flows with Reynolds numbers Re _D < 4000, particularly preferably with Re _D <2300, further preferably with Re _D <1000 as laminar.

The passage area of the flow resistance element 14 is preferably dimensioned to allow a defined, preferably laminar, flow profile (of a mass flow 15) to arise in the side channel 28. A defined flow profile in the side channel 28 is characterized by a defined speed distribution of a mass flow 15 as a function of the radius of the side channel 28. The mass flow 15 is therefore not chaotic. A defined flow profile is unique for each flow quantity 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 therefore 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. In particular, a defined flow profile (of a mass flow 15) in the side channel 28 can have a (parabolic) speed distribution depending on the radius of the side channel 28.

In the order according to FIG 2 however, it is not an indirect pressure measurement. In contrast to a pressure measurement, changes in the mass flow due to a change in temperature are also recorded. The device disclosed here can also compensate for temperature changes with the aid of the regulating and / or control and / or monitoring device 16. The mass flow sensor 13 is easy to install on the pressure side of practically any system.

In order to further reduce the influence of turbulence, the air flow 15 can be conducted into the side channel 28 via a damming probe 12. The damming probe 12 is arranged in the air duct 11. The damming probe 12 is in the form of a tube with any cross section (for example round, angular, triangular, trapezoidal, preferably round). 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. There are several on the side of the damming probe 12 in the direction from which the air flow 5 comes Openings (for example slots and / or bores) 31 are provided. Through the openings 31, a fluid such as air from the air duct 11 can enter the damming probe 12. Consequently, the damming probe 12 is in fluid communication with the air duct 11 via the openings 31. The total area of the openings 31 (the cross-section through which the openings 31 can flow) is significantly larger than the passage area of the flow resistance element 14. The passage area of the flow resistance element 14 is therefore (practically) decisive for the value of the air flow 15 through the side channel 28. According to a special embodiment the total cross-section through which the openings 31 can flow through is at least a factor of 2, preferably at least a factor of 10, particularly preferably at least a factor of 20, larger than the passage area of the flow resistance element 14.

The person skilled in the art chooses a small area for the total area of the openings 31 in relation to the cross section of the damming probe 12. Fluctuations in the turbulent main flow 5 therefore have no (practical) effect. A calm back pressure builds up in the tube of the damming probe. According to a special embodiment, the total cross-section through which the openings 31 can flow is smaller by at least a factor of 2, preferably at least a factor of 5, particularly preferably at least a factor of 10, than the cross-section of the congestion probe 12.

Another advantage of the arrangement is that suspended particles and / or droplets are less likely to get into the side channel 28. Due to the much lower speeds of the air in the side channel 28 and due to the dynamic pressure in the dynamic probe 12, suspended particles and / or droplets in the turbulent main stream 5 whirled on. Larger solid particles and / or droplets can hardly get into the damming probe 12 due to the dynamic pressure and the openings 31. They are whirled past the accumulation probe 12. For this purpose, the individual openings of the inlet 31 preferably have diameters of less than 5 mm, more preferably less than 3 mm, particularly preferably less than 1.5 mm.

The person skilled in the art makes the openings 31 along the damming probe 12 such that the mean value of the damming pressure is formed in the damming probe 12 via a macroscopic flow profile of the air flow 5. The person skilled in the art chooses a damming probe 12 of a defined length in order to smooth a macroscopic flow profile of the air flow 5 in the interior of the tube. It adjusts the respective flow conditions for differently designed air channels 11 over a length of the damming probe 12 adapted to the air channel 11. This applies in particular to air ducts with different diameters.

FIG 3 shows as opposite FIG. 1 modified embodiment a system with a motor-adjustable air flap 4. The air flap 4 is arranged downstream of the blower 3. The air flap 4 is also arranged downstream of the side channel 28. The system out FIG 3 allows the position of the air flap 4 and / or the fan speed to be determined for each power point. This results (reversibly clearly) from each flow value 5 and the (reported) position of the air flap 4 and / or the (reported) speed of the fan 3, a flow value 15 in the side channel 28.

FIG 4 shows as opposite FIG. 1 and FIG 3 modified embodiment a system with mixing device 17 in front of the blower 3. In contrast to the systems FIG. 1 and from FIG 3 fuel is not mixed with air at burner 1. Instead, fuel is added to the air flow 5 by means of a mixing device 17 upstream of the blower 3. Accordingly, the fuel-air mixture is found in the blower 3 (and in the duct 11). The The fuel-air mixture is then burned in the burner 1 in the combustion chamber of the heat consumer 2.

In contrast to FIG. 1 and FIG 3 the air 15 flows in on the suction side via the mass flow sensor 13. The blower 3 generates a vacuum at this location. In other words, the side channel 28 is an inflow channel. The side channel 28 is advantageously arranged in front of the mixing device 17. A possible negative pressure generated by the mixing device 17 thus has no effect on the flow 15 (particle flow and / or mass flow) through the side channel 28.

Changes in the amount of gas as a result of adjustments to the motor-adjustable fuel flap 9 do not influence the flow 15 through the side channel 28. The mixing device 17 no longer acts (practically) in the region of the side channel 28. If the negative pressure in the supply of the blower 3 is not sufficient, a defined flow resistance can be generated with a flow resistance element 18 at the inlet 27 of the blower supply. A flow divider is implemented together with the flow resistance element 14 in the side channel 28.

In FIG 4 the fluid flow 5 can only be adjusted via the blower 3 with the aid of the signal line 22. The specialist recognizes that a (motorized adjustable flap) can also be installed. Such a flap is arranged on the pressure side or suction side of the blower 3. According to another embodiment, the flap can be installed instead of the flow resistance element 18. It is then practically designed as a motor-adjustable flow resistance element (with feedback).

The mass flow sensor 13 is easy to attach to practically any system on the suction side. Also in FIG 3 and FIG 4 compensate disclosed systems Changes in density of the air such as FIG. 1 spelled out. The particle and / or mass flow 5 of the fluid through the burner 1 is determined in each case.

The flow 15 in the side channel 28 is measured with a mass flow sensor 13. The mass flow sensor 13 is arranged in the inflow / outflow channel 28. The mass flow sensor 13 advantageously works on 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 in a measuring element arranged in front of the heating resistor. The reference temperature measuring element can also be designed as a resistor, for example in the form of a PT-1000 element.

Ideally, the heating resistor and the reference temperature resistor are arranged on one chip. The person skilled in the art recognizes that the heating must be sufficiently thermally decoupled from the reference temperature measuring element.

The anemometer can be operated in two possible ways. According to a first embodiment, the heating resistor is heated with a constant, known heating power, heating voltage and / or heating current. The temperature difference between the heater and 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).

According to a second embodiment, the heater is heated in a closed temperature control loop. This results in a constant temperature of the heater. The temperature of the heater (apart from fluctuations due to the control) is equal to the temperature of the setpoint of the control loop. The setpoint of the temperature of the heater is determined by a constant temperature difference to the measured temperature of the Reference temperature measuring element is added. The constant temperature difference corresponds to the excess temperature of the heater compared 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 thus also a measure of the flow 5 (particle flow and / or mass flow) of the main flow.

Under certain circumstances, a small flow 15 in the side channel 28 can correspond to the measuring range of the flow sensor. Consequently, if the blower pressure is sufficiently high, the passage area of the flow resistance element 14, which determines the flow rate 15, must be made small. With such small passage areas, there is a risk that the flow resistance element 14 will be blocked by floating particles. FIG 5 teaches how a pressure divider with bypass channel 29 can be constructed in such cases.

A second flow resistance element 19 is then located behind the first flow resistance element 14 with a larger passage area. The pressure is therefore divided between the two flow resistance elements 14 and 19. The passage areas of the flow resistance elements 14 and 19 determine the division of the pressure. A further flow resistance element 20 is arranged in front of the mass flow sensor 13 in the bypass channel 29. The person skilled in the art chooses the passage area of the flow resistance element 20 to be sufficiently large. The person skilled in the art also selects a passage area of the flow resistance element 20 which is adapted to the mass flow sensor 13. The sub-flow divider constructed in this way can then be used (reversibly unambiguously) to determine the flow rate 5 (particle flow and / or mass flow) through channel 11.

For a fail-safe execution of the measurement process, the mass flow sensor 13 can be implemented redundantly (twice) with a comparison of results. The double version initially affects the Mass flow sensor 13 itself and the signal processing device. The result comparison can then be carried out in secure hardware and / or software at the location of the sensors and / or in the regulating and / or control and / or monitoring device 16. According to a further embodiment, the side channel 28 is implemented redundantly (twice). Each redundantly present side channel 28 preferably includes a flow resistance element 14. This allows errors due to clogged flow resistance elements 14 to be detected. In this case, the branch for the second side channel is preferably between the flow resistance element 14 and the damming probe 12. The damming probe 12 can be assumed to be fail-safe due to the (comparatively) large openings 31.

mit den Grenzen ε ₁ und ε ₂. Mit Hilfe einer Kennlinie der jeweiligen Grenzwerte ε ₁ und ε ₂ über dem Sollwert des Durchflusses 5 kann die Differenz Δ für jeden Sollwert des Durchflusses 5 verglichen und bewertet werden.Other errors, such as the formation of deposits on the mass flow sensor 13, scratches and / or other damage which have an influence on the measurement signal, can be identified. The (double) redundant structure of the signal processing device also allows errors in the signal processing device to be recognized. According to one embodiment, the measured values of the redundant mass flow sensors 13, preferably with additional averaging in each case, are compared with one another by subtraction. The difference Δ then lies within a threshold value band $$-{\epsilon }_1\le \mathrm{\Delta }\le {\epsilon }_{\mathrm{2nd}}$$

with the limits ε ₁ and ε ₂ . With the aid of a characteristic curve of the respective limit values ε ₁ and ε ₂ above the setpoint value of the flow rate 5, the difference Δ for each setpoint value of the flow rate 5 can be compared and evaluated.

With the arrangement described, the flow rate 5 (particle flow and / or mass flow) through channel 11 can be regulated by means of the sensor signal 21 via the blower 3. To achieve the setpoint of flow 5, all air actuators 4, with the exception of the speed of the fan 3, are each set to a permanently entered setpoint position. The target positions are for the required flow rate 5 (particle flow and / or mass flow) through channel 11 in the regulating and / or control and / or monitoring device 16. Using a closed control loop, the speed of the fan 3 is adjusted until the sensor measured value 21 reaches the value for the required flow rate stored in the memory.

FIG 6 shows the control loop. The setpoint 32 associated with the required flow rate 5 (particle flow and / or mass flow) through channel 11 for the flow rate 15 in the side channel 28 is stored in the memory of the regulating and / or control and / or monitoring device 16. A comparison between the setpoint 32 and the signal 21 of the mass flow sensor 13 results in a setpoint-actual deviation 33 via a (device for) difference formation 35. By means of a controller 37, which is used, for example, as a (self-adapting) PI controller or as (self-adapting) ) PID controller can be executed, the control signal 22 is given for the blower 3. In response to the actuating signal 22, the blower 3 generates the throughflow 5 (particle flow and / or mass flow) through channel 11. The signal 21 is, 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 Jam probe 12 generated. The signal 21 is a (reversibly unique) measure of the flow rate 5 (particle flow and / or mass flow) through channel 11. The control circuit disclosed here compensates for changes in air density. Such changes occur, for example, as a result of temperature fluctuations and / or changes in absolute pressure.

The person skilled in the art recognizes that the controller 29 can also be implemented as a fuzzy logic controller and / or as a neural network. The person skilled in the art further recognizes that the control signal 22 for the blower 3 can be a pulse-width-modulated signal, for example. According to an alternative embodiment, the control signal 22 for the fan 3 is an alternating current generated by a (matrix) converter. The frequency of the AC corresponds to (is proportional to) the speed of the fan 3.

If the system is to be designed fail-safe, the target positions of the actuators 4 must be determined fail-safe. This is done, for example, using two position sensors (angle sensors, stroke sensors, light barriers, etc.).

The optional (electronic) filter 36 smoothes the measurement signal. The filter 36 can be designed adaptively according to one embodiment. For this purpose, the measurement signal is averaged over a long, maximum integration time (for example two seconds to five seconds) as a comparison value using a moving average filter. If a measured value deviates from the mean value of the measured values or alternatively from the target value 32 outside a predetermined range, a target value jump is assumed. The measured value is now used directly as the actual value. The control loop therefore reacts immediately with the sampling rate of the control loop.

If the measured values are again within the defined range, the integration time is increased step by step with (each) scan of the control loop. The value integrated in this way is used as the actual value. This continues until the maximum integration time is reached. The control loop is now considered stationary. The value averaged in this way is now used as the actual value. The disclosed method enables an exact stationary measurement signal with maximum dynamics.

According to one embodiment, in the case of a regulating and / or control and / or monitoring device 16 designed as a microcontroller, the assignment of the positions 23 of the at least one air actuator 4 and the setpoint 32 for the mass flow sensor 13 is a function of the flow rate 5 (particle flow and / or mass flow) through channel 11. In a particularly preferred embodiment, the Function stored in a table. Intermediate values between the points defined by the table are interpolated linearly. As an alternative, intermediate values between the points defined by the table are interpolated by a polynomial over several neighboring values and / or over (cubic) splines. The person skilled in the art recognizes that other forms of interpolation can also be implemented.

According to one embodiment, the regulating and / or control and / or monitoring device 16 has a reading device for identification on the basis of radio-frequency waves (RFID reading device). The regulating and / or control and / or monitoring device 16 is designed to use the reading device to read operating parameters such as formulas (of polynomials defined in sections) and / or like the aforementioned tables from a so-called (RFID) transponder. The operating parameters are then stored in the (non-volatile) memory of the regulating and / or control and / or monitoring device 16. If necessary, they can be read out and / or used by a microprocessor.

The table below shows the setpoint for the mass flow sensor 13 in the side channel 28 and the values for the motorized flap 4. The table below also shows the values for a further (motor-adjustable) flap or valve which acts on the flow 5 (particle flow and / or mass flow) through channel 11. Depending on the embodiment, further actuators can be added in the form of columns. According to a special embodiment, none of the flaps are present. This eliminates the corresponding columns. Flow 5 (particle flow and / or mass flow) through channel 11 (Motorized adjustable) flap or valve 4 (Motor-adjustable) additional flap or valve Setpoint 32 for flow 15 (particle flow and / or mass flow) through side channel 28 Value 1 Angle 1 Angle 1 Flow value 1 Value 2 Angle 2 Angle 2 Flow value 2 ... ... ... ... Value n Angle n Angle n Flow value n

If a specific value of flow rate 5 (particle flow and / or mass flow) through channel 11 is to be set, the two values between which the desired value of flow rate 5 lies are searched in the table. The position between the two values is then determined. If the desired value of the flow rate 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 approached k + 1. The same applies to the angle (the position) of the (motor-adjustable) further flap or the further valve. The flow rate 5 can be specified as an absolute number and / or relative to a value, preferably to the flow rate 5 at the greatest power value. The flow value is then stored, for example, as a percentage of the flow 5 of the greatest power value.

According to a further embodiment, the positions of the at least one air actuator 4 are stored as a polynomial as a function of the flow rate 5 (particle flow and / or mass flow) through channel 11 instead of the aforementioned table. According to yet another embodiment, the positions of the at least one air actuator 4 are stored as functions defined in sections as a function of the flow rate 5 (particle flow and / or mass flow) through channel 11. According to another embodiment, the positions of the at least one air actuator 4 are stored as a (valve) opening curve (s).

In order to exclude an incorrectly assumed value of the air throughput, for example due to failed components and / or defective supply lines, etc., the design can be made fail-safe. This means that the at least one actuator 4 from the aforementioned table can monitor its position. This also means that the flow 15 (particle flow and / or mass flow) through the side channel 28 is detected in a safety-related manner.

If a predetermined flow rate 5 through channel 11 is to be set, the correct combination of positions of the at least one actuator 4 and flow rate 15 through side channel 28 is determined and started. This also happens if the characteristic curve of individual actuators is not linear. With a sequence of characteristic points with a sufficiently close distance from one another, an (almost) linear scale for the flow rate 5 is obtained. This is of great advantage for the operation of the combustion device.

The position of the actuator 9 with which the fuel throughput 6 is set can also be included in the table shown above. 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 from the fuel throughput 6.

This means that the correct fuel flow rate 6 has always been assigned for a preset air ratio λ for each air flow rate 5. The air throughput 5 thus becomes synonymous with the performance value, since the fuel throughput 6 and the air throughput 5 are firmly connected to one another. Conversely, the fuel throughput 6 or the position of the fuel actuator 9 can be defined for setting the power. The assigned air throughput 5 can be determined in the table on the basis of the characteristic curve and / or on the basis of the linear interpolation between the table values. The positions of the air actuators 4 and the setpoint value of the mass flow 32 in air can be as above described are interpolated in a table and / or determined using another mathematical assignment.

According to one embodiment, the values for the flow rate 5 are given absolutely in the regulating and / or control and / or monitoring device 16. According to another embodiment, the values for the flow rate 5 are specified in the regulating and / or control and / or monitoring device 16 relative to a specific value of the flow rate. The values for the flow are preferably specified in the regulating and / or control and / or monitoring device 16 relative to the maximum throughput 5 (in air) at maximum output.

In a further particularly preferred embodiment, the fuel throughput 6 is not directly assigned to the air throughput 5. In this embodiment, the position of the fuel flap or the fuel valve 9 is assigned to the fuel throughput 6 in a second functional assignment. As with air, this can be done using a table as shown below. Fuel flow 6 (Motor-adjustable) fuel flap or fuel valve 9 Value 1 Angle 1 Value 2 Angle 2 ... ... Value n Angle n

Interpolation (linear) between the individual values is also possible here. The assignment can of course also be done using polynomials that are defined at least in sections.

The fuel throughput 6 stored in the table is an absolute or relative value for an air ratio λ ₀ . The fuel throughput 6 stored in the table is also a absolute or relative value for the fuel present in the fuel supply during a setting process. The air ratio λ ₀ is usually specified during the setting process. The functional assignment takes place during the setting process mentioned. In this case, the fuel throughput 6 of the delivered fuel is assigned to the air throughput 5 defined in the linearized scale at a defined air ratio λ ₀ . The position of the fuel actuator 9 is thus mapped onto a linear scale of the fuel throughput 6.

The air flow rate 5 with the formula symbol V̇ _L known on a linear scale and the fuel flow rate 6 with the formula symbol V̇ _G known on a linear scale are then related via the equation V hängen _L = λ · L _min · V̇ _G. L _min is the minimum air requirement of the fuel, ie the ratio of air throughput 5, which is necessary under conditions of stoichiometry, to fuel throughput 6. L _min is a quantity that depends on the composition of the fuel or the type of fuel.

zwischen dem Luftdurchsatz während des Einstellvorgangs V̇ _L0, der Luftzahl während des Einstellvorgangs λ ₀, dem Mindestluftbedarf während des Einstellvorgangs L _min0 und dem Brennstoffdurchsatz während Einstellvorgangs V̇ _G0. Am maximalen Leistungspunkt besteht der Zusammenhang $${\dot{V}}_{L0\mathit{max}}={\lambda }_0\cdot L_{\mathit{min}0}\cdot {\dot{V}}_{G0\mathit{max}}$$

mit dem Luftdurchsatz am maximalen Leistungspunkt V̇ _L0max und mit dem Brennstoffdurchsatz V̇ _G0max am maximalen Leistungspunkt. Jeweils im Verhältnis zum Luftdurchsatz 5 bzw Brennstoffdurchsatz 6 bei maximaler Leistung, wie während des Einstellvorgangs festgelegt, ergibt sich für jeden Betriebszustand der Zusammenhang $$\frac{{\dot{V}}_L}{{\dot{V}}_{L0\mathit{max}}}=\frac{\lambda }{{\lambda }_0}\cdot \frac{L_{\mathit{min}}}{L_{\mathit{min}0}}\cdot \frac{{\dot{V}}_G}{{\dot{V}}_{G0\mathit{max}}}$$

für den Luftdurchsatz 5 in Abhängigkeit vom Brennstoffdurchsatz 6. Mit dem jeweiligen relativen Wert vom Luftdurchsatz 5 $\frac{{\dot{V}}_L}{{\dot{V}}_{L0\mathit{max}}}=$

V̇_RL und dem relativen Wert vom Brennstoffdurchsatz 6 $\frac{{\dot{V}}_G}{{\dot{V}}_{G0\mathit{max}}}={\dot{V}}_{\mathit{RG}}$

wird der Zusammenhang: $${\dot{V}}_{\mathit{RL}}=\frac{\lambda }{{\lambda }_0}\cdot \frac{L_{\mathit{min}}}{L_{\mathit{min}0}}\cdot {\dot{V}}_{\mathit{RG}}$$

During the setting, the fuel composition has the minimum _{air requirement} L _min0 . This means that there is a connection during the setting process $${\dot{V}}_{L0}={\lambda }_0\cdot L_{\mathit{min}0}\cdot {\dot{V}}_{G0}$$

between the air flow rate during the setting process V̇ _{L 0} , the air ratio during the setting process λ ₀ , the minimum air requirement during the setting process L _{min 0} and the fuel flow rate during the setting process V̇ _{G 0} . The connection exists at the maximum credit point $${\dot{V}}_{L0\mathit{Max}}={\lambda }_0\cdot L_{\mathit{min}0}\cdot {\dot{V}}_{G0\mathit{Max}}$$

with the air throughput at the maximum power point V̇ _{L 0 max} and with the fuel throughput V̇ _{G 0 max} at the maximum power point. In each case in relation to the air throughput 5 or fuel throughput 6 at maximum output, such as during the The setting process determines the relationship for each operating state $$\frac{{\dot{V}}_L}{{\dot{V}}_{L0\mathit{Max}}}=\frac{\lambda }{{\lambda }_0}\cdot \frac{L_{\mathit{min}}}{L_{\mathit{min}0}}\cdot \frac{{\dot{V}}_G}{{\dot{V}}_{G0\mathit{Max}}}$$

for the air flow rate 5 depending on the fuel flow rate 6. With the respective relative value of the air flow rate 5 $\frac{{\dot{V}}_L}{{\dot{V}}_{L0\mathit{Max}}}=$

V̇ _RL and the relative value of the fuel throughput 6 $\frac{{\dot{V}}_G}{{\dot{V}}_{G0\mathit{Max}}}={\dot{V}}_{\mathit{RG}}$

the relationship becomes: $${\dot{V}}_{\mathit{RL}}=\frac{\lambda }{{\lambda }_0}\cdot \frac{L_{\mathit{min}}}{L_{\mathit{min}0}}\cdot {\dot{V}}_{\mathit{RG}}$$

If you have conditions like the setting regarding air ratio λ and gas composition, then V̇ _RL = V̇ _RG . The relative air throughput is therefore equal to the relative fuel throughput as was also determined during the setting process based on the maximum values.

wird. Dann muss der Brennstoffdurchsatz 6 um den Faktor 1/F erhöht werden, falls die Luftzahl λ beim gleichen Wert bleiben soll. Mit anderen Worten muss bei einer Änderung der Zusammensetzung des Brennstoffs, bei der sich der Mindestluftbedarf L_min um den Faktor F erhöht, für gleichbleibende Luftzahl λ der Brennstoffdurchsatz 6 um den Faktor F gegenüber den Einstellbedingungen verringert werden. Alternativ kann auch der Luftdurchsatz 5 um den Faktor F erhöht werden.If, for example, the gas composition changes, the minimum air requirement L _{min also changes} , so that $\frac{L_{\mathit{min}}}{L_{\mathit{min}0}}=F\ne 1$

becomes. Then the fuel throughput 6 must be increased by a factor of 1 / F if the air ratio λ is to remain at the same value. In other words, in the event of a change in the composition of the fuel in which the minimum air requirement L _min increases by the factor F, the fuel throughput 6 must be reduced by the factor F compared to the setting conditions for a constant air ratio λ. Alternatively, the air flow rate 5 can be increased by a factor of F.

If you want to change the air ratio λ by the factor F, the fuel throughput 6 must also be reduced by the factor F or the air throughput 5 must be increased by the factor F.

Both values, air throughput 5 and fuel throughput 6, are each on an almost linear scale. It is therefore sufficient to know the factor F for one performance point in order to calculate the fuel throughput 6 for each performance point from the values stored in the setting if the air throughput 5 is used as the performance variable. If the fuel throughput 6 is used as the output variable 5, the correct air throughput 5 can be calculated for each output point.

With the respective assignments of the positions for the air actuators 4 or for the setpoint 32 in the outflow channel to the air throughput 5 and the assignment of the position of the fuel actuator 9 to the fuel throughput 6, the corresponding positions can then be set for a predetermined power value. The delivery rate of the blower 3 can be adjusted accordingly.

The current value for fuel throughput 6 is thus assigned to the current value of air throughput 5 via a fixed factor. A base factor is determined during the setting as shown above. For a direct representation of air throughput 5 or fuel throughput 6, it is λ ₀ · L _{min 0} . For a representation of air throughput 5 or fuel throughput 6 relative to the respective maximum values from the setting process, it is preferably set to one.

If the conditions change by a factor F compared to the settings with regard to the air ratio A or the composition of the fuel, the air throughput 5 or the fuel throughput 6 are adjusted by the factor 1 / F compared to the stored setting values.

If, in a further embodiment, the factor F is determined by changing the composition of the fuel using A control, this value also applies to all Credit points. With the help of the linear scales for air throughput 5 and fuel throughput 6, the output can be changed much faster than the λ control would allow. As a result, λ control and power adjustment are decoupled from each other. This is very advantageous because, due to the system runtimes and the time constants of the system, the A control loop regulates environmental changes much more slowly than the performance should be changed in comparison. Typical environmental changes are air temperature, air pressure, fuel temperature and / or fuel type. Such changes usually occur so slowly that the λ control loop is sufficiently fast for this.

A λ control can be implemented with the help of an O ₂ sensor in the exhaust gas. The person skilled in the art can easily calculate the air ratio λ from the derived measured value of an O ₂ sensor in the exhaust gas.

The use of the flow sensor 13 is a particular advantage in the method presented FIG 6 Outlined control loop, density fluctuations in the air 5 are corrected due to temperature changes and / or barometric pressure fluctuations. There is therefore already a compensated value for the linearized scale of air throughput 5. The λ control loop only has to compensate for fluctuations in the gas composition.

If the air throughput 5 is selected as the output variable, the fuel throughput 6 is readjusted via the λ control loop when the composition of the fuel changes, so that the burner output remains almost constant. The reason for this is that the energy content for most commonly used fuels correlates (approximately) linearly with the minimum air requirement L _min .

The control loop after FIG 6 also compensates for errors in the fan and / or regulates them. Faults in the blower 3 are, for example an increased slip of the fan wheel and / or errors in the (electronic) control. Furthermore, gross errors of the blower 3, which can no longer be corrected, can be detected. For this purpose, it is detected whether the control rotational speed 22 of the blower 3 lies outside a band predetermined for each flow 5 through the duct 11. For this purpose, upper and lower limit values of the speed and / or the control signals 22 of the fan 3 are advantageously stored in the aforementioned table for given flow rates 5 (particle flow and / or mass flow) through the channel 11. The values are particularly preferably stored in a (non-volatile) memory of the regulating and / or control and / or monitoring device 16. According to a further embodiment, upper and lower limit values for the speed and / or the control signals 22 of the blower 3 are stored on the basis of functions (defined in sections) such as, for example, straight lines and / or polynomials.

The person skilled in the art recognizes that the flow rate 5 through channel 11 can also be regulated by another actuator. For example, in FIG 6 replace the regulation of the blower 3 by regulating the (motor-adjustable) flap 4. In this case, for each setpoint 32 of the flow rate 5, all actuators including the blower 3, with the exception of the regulated position of the (motor-adjustable) flap or of the valve 4, are set to a permanently entered setpoint position. The respective target position for a given flow rate 5 (particle flow and / or mass flow) through channel 11 is stored in the (non-volatile) memory of the regulating and / or control and / or monitoring device 16. The positions of the actuators and the setpoint 32 of the flow 15 through the side channel 28 are also stored here as a function of the flow 5 through channel 11, as already mentioned above. The interpolation is carried out as described above.

For the above table, the regulation of the (motor-adjustable) flap or valve 4 means that the position of that Actuator is replaced by the speed of the fan 3. A correspondingly adjusted table is shown below: Flow 5 (particle flow and / or mass flow) through channel 11 Fan 3 (Motor-adjustable) additional flap or valve Setpoint 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

If the system is to be designed fail-safe, the target positions of the actuators must be determined fail-safe. This is done, for example, using two position sensors (angle sensors, stroke sensors, speed sensors, Hall sensors, etc.). Using 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 for the required flow rate stored in the memory. According to a special embodiment, the speed of the fan 3 cannot be changed. The flow rate 5 through channel 11 is set exclusively via the (motor-adjustable) further flap or the further valve.

In both of the above embodiments with regulation of the air flow rate 5 via the (motor-adjustable) flap 4, the flap position 9 can also be directly included in the table. However, a second assignment for the fuel quantity 6 can also be formed here. The assignment of the linearized scale from fuel throughput 6 to the linearized scale from air throughput 5 is determined by a factor as described above.

Parts of a control device or a method according to the present disclosure can be implemented as hardware, as a software module, which is executed by a computing unit, or using a cloud computer, or using a combination of the aforementioned options. The software may include firmware, a hardware driver that runs within an operating system, or an application program. The present disclosure therefore also relates to a computer program product which contains the features of this disclosure or carries out the necessary steps. When implemented as software, the functions described can be stored as one or more commands on a computer-readable medium. Some examples of computer-readable media include working memory (RAM), magnetic working memory (MRAM), only readable memory (ROM), flash memory, electronically programmable ROM (EPROM), electronically programmable and erasable ROM (EEPROM), registers of a computing unit A hard drive, a removable storage device, optical storage, or any suitable medium that can be accessed by a computer or other IT devices and applications.

The present disclosure teaches a method according to the invention.

• Anfordern eines Durchflusses 5 eines Fluids durch den Zufuhrkanal 11,
• Zuordnen des angeforderten Durchflusses 5 durch den Zufuhrkanal 11 auf eine (einen Wert der) Stellung des mindestens einen ersten Aktors 4, 3,
• Generieren eines ersten Signals 23, 22 für den mindestens einen ersten Aktor 4, 3, wobei das generierte erste Signal 23, 22 eine Funktion der dem angeforderten Durchfluss 5 durch den Zufuhrkanal 11 zugeordneten Stellung des mindestens einen ersten Aktors 4, 3 ist,
• Ausgeben des generierten ersten Signals 23, 22 an den mindestens einen ersten Aktor 4, 3,
• Generieren eines zweiten Signals 21 durch den Massenstromsensor 13, wobei das zweite Signal 21 eine Funktion eines Durchflusses 15 durch den Seitenkanal 28 ist,
• Verarbeiten des durch den Massenstromsensor 13 generierten zweiten Signals 21 zu einem Ist-Wert des Durchflusses 15 durch den Seitenkanal 28,
• Verarbeiten des angeforderten Durchflusses 5 durch den Zufuhrkanal 11 zu einem Soll-Wert 32 des Durchflusses 15 durch den Seitenkanal 28,
• Generieren eines Regelsignals 22, 23 durch den Regler 37 für den mindestens einen zweiten Aktor 3, 4 als Funktion des Ist-Wertes des Durchflusses durch den Seitenkanal 28 und als Funktion des Soll-Wertes 32 des Durchflusses 15 durch den Seitenkanal 28,
• Ausgeben des generierten Regelsignals 22, 23 an den mindestens einen zweiten Aktor 3, 4.

In other words, the present disclosure teaches, as a preferred embodiment, a method for controlling a burner device with a mass flow sensor 13 in a side channel 28 of a feed channel 11 of the burner device, a controller 37, at least one first actuator 4, 3 acting on the feed channel 11 and at least one second actuator 3, 4 acting on the feed channel 11, the at least one first actuator 4, 3 and the at least one second actuator 3, 4 (each) being designed to receive signals, the method comprising the steps:

• Requesting a flow 5 of a fluid through the feed channel 11,
• Assigning the requested flow 5 through the supply channel 11 to a (a value of) the position of the at least one first actuator 4, 3,
• Generating a first signal 23, 22 for the at least one first actuator 4, 3, the generated first signal 23, 22 being a function of the position of the at least one first actuator 4, 3 assigned to the requested flow 5 through the supply channel 11,
• Output of the generated first signal 23, 22 to the at least one first actuator 4, 3,
• Generating a second signal 21 by the mass flow sensor 13, the second signal 21 being a function of a flow 15 through the side channel 28,
• Processing the second signal 21 generated by the mass flow sensor 13 to an actual value of the flow 15 through the side channel 28,
• Processing the requested flow 5 through the feed channel 11 to a desired value 32 of the flow 15 through the side channel 28,
• Generating a control signal 22, 23 by the controller 37 for the at least one second actuator 3, 4 as a function of the actual value of the flow through the side channel 28 and as a function of the target value 32 of the flow 15 through the side channel 28,
• Output of the generated control signal 22, 23 to the at least one second actuator 3, 4.

The side channel 28 and the feed channel 11 of the burner device are 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 in series (in a row) on the feed channel 11. The at least one first actuator 4, 3 and the at least one second actuator 3, 4 are arranged in a row (in the feed channel 11).

The present disclosure further teaches the aforementioned method as a preferred embodiment, wherein the processing of the requested flow 5 through the supply channel 11 to a desired value 32 of the flow 15 through the side channel 28 reversibly and unambiguously assigns (the requested flow 5 through the supply channel 11) includes the target value 32 of the flow 15 through the side channel 28).

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, wherein a control signal is generated (by the controller 37) for the at least one second actuator 3, 4 using a proportional-integral controller 37.

According to a special embodiment, the proportional-integral controller 37 is a self-adaptive controller.

As a preferred embodiment, 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 using a proportional-integral-derivative controller 37.

According to a special embodiment, the proportional-integral-derivative controller 37 is a self-adaptive controller.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, the at least one a second actuator of the burner device comprises a blower 3 with adjustable speed, wherein the blower 3 with adjustable speed comprises a drive, and wherein the blower 3 is preferably arranged in the feed channel 11 of the burner device.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, the generated control signal 22, 23 to the at least one second actuator 3, 4 being a pulse-width-modulated signal.

As a preferred embodiment, the present disclosure also teaches one of the aforementioned methods, the generated control signal 22, 23 to the at least one second actuator 3, 4 being a converter signal with a frequency that corresponds to the speed of the fan 3.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, the at least one first actuator of the burner device comprising 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.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, wherein when the control signal 22, 23 is generated by the controller 37, a difference between the setpoint value 32 and the actual value 21 is formed for the at least one second actuator 3, 4.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, the processing of the second signal 21 generated by the mass flow sensor 13 comprising filtering the second signal 21 generated by the mass flow sensor 13.

As a preferred embodiment, 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, the 3dB threshold of the filtering being set up in this way is that fluctuations in the signal 21 of a frequency greater than 1 Hz, preferably greater than 10 Hz, are integrated.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, wherein the requested flow 5 through the supply channel 11 is assigned to a (a value of) the position of the at least one first actuator 4, 3 on the basis of a predetermined table, in which values the requested flow 5 through the supply channel 11 values of the positions of the at least one first actuator 4, 3 are assigned.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, wherein the requested flow rate 5 through the supply channel 11 is assigned to a (a value of) the position of the at least one first actuator 4, 3 on the basis of a predetermined table with subsequent interpolation, whereby Values of the requested flow 5 through the supply channel 11 are assigned 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 in the predetermined table.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, wherein the assignment of the requested flow 5 through the supply channel 11 to a (a value of) the position of the at least one first actuator 4, 3 on the basis of a predetermined (sectionally defined) function (polynomial ) in which values the requested flow 5 through the supply channel 11 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, are assigned.

As a preferred embodiment, 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 target value 32 and the actual value 21 is formed and the amount of the difference between the target value 32 and the actual value 21 is compared with a predetermined threshold value, and
wherein the threshold value is preferably a function of the target value 32.

• Vergleichen des generierten Regelsignals 22 - 23 mit einem (vorgegebenen) oberen Schwellwert und / oder mit einem (vorgegebenen) unteren Schwellwert,
• Generieren eines Signals 24 - 25 zur Abschaltung der Brennereinrichtung, falls das generierte Regelsignal 22 - 23 über dem (vorgegebenen) oberen Schwellwert oder unter dem (vorgegebenen) unteren Schwellwert liegt,
• Ausgeben des generierten Signals 24 - 25 zur Abschaltung der Brennereinrichtung an das mindestens eine Sicherheits-Absperrventil 7 - 8, falls das generierte Regelsignal 22 - 23 über dem (vorgegebenen) oberen Schwellwert oder unter dem (vorgegebenen) unteren Schwellwert liegt.

As a preferred embodiment, the present disclosure further teaches one of the two aforementioned methods, the burner device additionally comprising a fuel supply channel 38 with at least one safety shut-off valve 7-8 for closing the fuel supply channel 38, the at least one safety shut-off valve 7-8 being designed, to receive a signal 24-25 for switching off the burner device and in response to receiving a signal 24-25 for switching off the burner device to close the fuel supply channel 38, the method additionally comprising the steps:

• Comparing the generated control signal 22-23 with a (predetermined) upper threshold and / or with a (predetermined) lower threshold,
• Generating a signal 24-25 for switching off the burner device if the generated control signal 22-23 lies above the (predetermined) upper threshold value or below the (predetermined) lower threshold value,
• Output of the generated signal 24-25 for switching off the burner device to the at least one safety shut-off valve 7-8 if the generated control signal 22-23 is above the (specified) upper threshold or below the (specified) lower threshold.

• Vergleichen des Ist-Wertes des Durchflusses 15 durch den Seitenkanal 28 mit einem (vorgegebenen) oberen Schwellwert und / oder mit einem (vorgegebenen) unteren Schwellwert,
• Generieren eines Signals 24 - 25 zur Abschaltung der Brennereinrichtung, falls der Ist-Wert des Durchflusses 15 durch den Seitenkanal 28 über dem (vorgegebenen) oberen Schwellwert oder unter dem (vorgegebenen) unteren Schwellwert liegt,
• Ausgeben des generierten Signals 24 - 25 zur Abschaltung der Brennereinrichtung an das mindestens eine Sicherheits-Absperrventil 7 - 8, falls der Ist-Wert des Durchflusses 15 durch den Seitenkanal 28 über dem (vorgegebenen) oberen Schwellwert oder unter dem (vorgegebenen) unteren Schwellwert liegt.

As a preferred embodiment, the present disclosure further teaches one of the two aforementioned methods, the burner device additionally comprising a fuel supply channel 38 with at least one safety shut-off valve 7-8 for closing the fuel supply channel 38, the at least one safety shut-off valve 7-8 being designed, to receive a signal 24-25 for switching off the burner device and in response to receiving a signal 24-25 for switching off the burner device to close the fuel supply channel 38, the method additionally comprising the steps:

• Comparing the actual value of the flow 15 through the side channel 28 with a (predetermined) upper threshold value and / or with a (predetermined) lower threshold value,
• Generating a signal 24 - 25 for switching off the burner device if the actual value of the flow 15 through the side channel 28 is above the (predetermined) upper threshold value or below the (predetermined) lower threshold value,
• Output of the generated signal 24-25 for switching off the burner device to the at least one safety shut-off valve 7-8 if the actual value of the flow 15 through the side channel 28 is above the (predetermined) upper threshold value or below the (predetermined) lower threshold value .

As a preferred embodiment, the present disclosure further teaches the aforementioned methods, the (predetermined) lower threshold value and / or (predetermined) upper threshold value being a function of the requested flow rate 5 through the supply channel 11.

As a preferred embodiment, the present disclosure further teaches the aforementioned methods, the controller 37 comprising a (non-volatile) memory and the (predetermined) lower threshold value and / or (predetermined) upper threshold value being stored in the memory of the controller 37. The controller 37 is preferably designed to read the (predefined) lower threshold value and / or the (predefined) upper threshold value from the (non-volatile) memory.

• Anfordern eines Durchflusses 6 eines Brennstoffs durch den Brennstoffzufuhrkanal 38,
• Zuordnen des Durchflusses 6 des Brennstoffs durch den Brennstoffzufuhrkanal 38 auf eine Stellung des mindestens einen Brennstoff-Aktors 9,
• wobei vorzugsweise das Zuordnen des Durchflusses des Brennstoffs 6 durch den Brennstoffzufuhrkanal 38 auf eine Stellung des mindestens einen Brennstoff-Aktors 9 anhand einer Tabelle (idealerweise mit anschliessender Interpolation) und / oder anhand einer (zumindest abschnittsweise definierten) polynomischen Funktion erfolgt, in welcher Werten des angeforderten Durchflusses 6 durch den Brennstoffzufuhrkanal 38 Werte der Stellungen des mindestens einen Brennstoff-Aktors 9 zugeordnet sind,
• Generieren eines Brennstoff-Signals 26 für den mindestens einen Brennstoff-Aktor 9, wobei das generierte Brennstoff-Signal 26 eine Funktion der dem angeforderten Durchfluss 6 durch den Brennstoffzufuhrkanal 38 zugeordneten Stellung des mindestens einen Brennstoff-Aktors 9 ist,
• Ausgeben des generierten Brennstoff-Signals 26 an den mindestens einen Brennstoff-Aktor 9 und vorzugsweise
• Stellen des mindestens einen Brennstoff-Aktors 9 entsprechend dem ausgegebenen Brennstoff-Signal 26.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, the burner device additionally comprising a fuel supply channel 38 and at least one fuel actuator 9 acting on the fuel supply channel 38 and the fuel actuator 9 being designed to receive a (fuel) signal 26 , the procedure additionally includes the steps:

• Requesting a flow 6 of a fuel through the fuel supply channel 38,
• Assigning the flow 6 of the fuel through the fuel supply channel 38 to a position of the at least one fuel actuator 9,
• the flow of the fuel 6 through the fuel supply channel 38 preferably being assigned to a position of the at least one fuel actuator 9 using a table (ideally with subsequent interpolation) and / or using a (at least sectionally defined) polynomial function, in which values the requested flow 6 through the fuel supply channel 38 are assigned values of the positions of the at least one fuel actuator 9,
• Generating a fuel signal 26 for the at least one fuel actuator 9, the generated fuel signal 26 being a function of the position of the at least one fuel actuator 9 associated with the requested flow 6 through the fuel supply channel 38,
• Output of the generated fuel signal 26 to the at least one fuel actuator 9 and preferably
• Set the at least one fuel actuator 9 in accordance with the output fuel signal 26.

As a preferred embodiment, the present disclosure further teaches the aforementioned methods, the controller 37 comprising a (non-volatile) memory and the table and / or the polynomial function being stored in the memory of the controller 37. The controller 37 is preferably designed to read the table and / or the polynomial function from the (non-volatile) memory.

As a preferred embodiment, the present disclosure further teaches the aforementioned method, wherein the allocation of the flow of fuel 6 through the fuel supply channel 38 to values of the fuel actuator 9 using a universal table (ideally with subsequent interpolation) and / or using a universal (at least sectionally defined) one polynomial function takes place, the method additionally comprises the step:
Assignment of the position (s) of each actuator 4, 3, 9, which is different from the at least one second actuator 3, 4 of the burner device, to a flow 5 of a fluid through the supply channel 11 on the basis of the universal table or a universal polynomial function defined at least in sections.

As a preferred embodiment, the present disclosure further teaches the aforementioned methods, the controller 37 comprising a (non-volatile) memory and the universal table and / or the universal polynomial function being 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 present disclosure further teaches one of the aforementioned methods, the method additionally comprising the step:
Mapping a flow 6 of fuel through the fuel supply channel 38 to a flow 5 of a fluid through the supply channel 11 based on a constant factor between the flow 6 of a fuel through the fuel supply channel 38 and the flow 5 of a fluid through the supply channel 11.

• Generieren eines Signals durch die Sonde im Abgaskanal 30,
• Übermitteln des Signals aus der Sonde im Abgaskanal 30 an die λ-Regelung,
• Bestimmen (durch die λ-Regelung) eines veränderlichen Faktors zwischen dem Durchfluss eines Brennstoffs 6 durch den Brennstoffzufuhrkanal 38 und dem Durchfluss 5 eines Fluids durch den Zufuhrkanal 11 als Funktion des Signals aus der Sonde im Abgaskanal 30,
• (Übermitteln des bestimmten veränderlichen Faktors an den Regler 37,)
• Zuordnen (durch die λ-Regelung und / oder durch den Regler 37) eines Durchflusses 6 eines Brennstoffs durch den Brennstoffzufuhrkanal 38 zu einem Durchfluss 5 eines Fluids durch den Zufuhrkanal 11 anhand des bestimmten veränderlichen Faktors.

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, the burner device additionally comprising an exhaust gas duct 30 with a probe in the exhaust gas duct 30 and λ control, which is designed to receive signals from the probe of the exhaust gas duct 30, the method additionally comprising the Steps:

• Generating a signal by the probe in the exhaust duct 30,
• Transmitting the signal from the probe in the exhaust duct 30 to the λ control,
• Determining (by the λ control) a variable factor between the flow of a fuel 6 through the fuel supply channel 38 and the flow 5 of a fluid through the supply channel 11 as a function of the signal from the probe in the exhaust gas channel 30,
• (Transmission of the determined variable factor to the controller 37)
• Assigning (by the λ control and / or the controller 37) a flow 6 of a fuel through the fuel supply channel 38 to a flow 5 of a fluid through the supply channel 11 on the basis of the determined variable factor.

The λ control of the burner device is preferably integrated in the controller 37.

The signal generated by the probe in the exhaust duct 30 is preferably a function of an air ratio of a fluid stream in the exhaust duct and / or a function of an oxygen content of a fluid stream in the exhaust duct.

The probe in the exhaust duct 30 is preferably a λ probe and / or an O ₂ probe (oxygen probe).

As a preferred embodiment, the present disclosure further teaches one of the aforementioned methods, the method additionally comprising the step:
Determining a performance of the burner device on the basis of the target value 32 of the controller 37 and / or on the basis of the value of the requested flow 5 through the supply channel 11.

The present disclosure further teaches, as a preferred embodiment, a non-volatile computer readable storage medium that stores an instruction set for execution by at least one processor that, when executed by a processor, also performs one of the aforementioned methods.

The above relates to individual embodiments of the disclosure. Various changes to the embodiments can be made without departing from the underlying idea and without departing from the scope of this disclosure. The subject matter of the present disclosure is defined by its claims. Various changes can be made without leaving the scope of the following claims.

Reference numerals

• 1 burner
• 2 heat consumers (heat exchanger)
• 3 blowers
• 4 (motor-adjustable) flap or valve
• 5 flow (particle and / or mass flow) or flow through duct 11 (air flow)
• 6 Fluid flow of a combustible fluid (fuel throughput)
• 7, 8 safety valve
• 9 (motorized adjustable) flap or valve
• 10 exhaust gas flow
• 11 supply duct (air duct)
• 12 Junction point, traffic jam probe
• 13 mass flow sensor
• 14 flow resistance element (orifice)
• 15 Flow or flow in the side channel
• 16 regulating and / or control and / or monitoring device
• 17 mixing device
• 18, 19, 20 flow resistance elements (orifices)
• 21 - 26 signal lines
• 27 air intake
• 28 side channel
• 29 bypass channel
• 30 exhaust duct
• 31 openings in the damming probe
• 32 Setpoint for control
• 33 Target / actual deviation
• 34 Measuring arrangement
• 35 Difference formation
• 36 filters
• 37 controllers, for example a PI (D) controller
• 38 fuel supply duct

Claims (10)

1. Method for regulating a burner device with a mass flow sensor (13) in a side duct (28) of a feed duct (11) of the burner device, a regulator (37), at least one first actuator (4, 3) acting on the feed duct (11) and at least one second actuator (3, 4) acting on the feed duct (11), wherein the at least one first actuator (4, 3) and the at least one second actuator (3, 4) are embodied for receiving signals, the method comprising the steps:

   Requesting a throughflow (5) of a fluid through the feed duct (11),

   Assigning the requested throughflow (5) through the feed duct (11) to a setting of the at least one first actuator (4, 3),

   Generating a first signal (23, 22) for the at least one first actuator (4, 3), wherein the generated first signal (23, 22) is a function of the setting of the at least one first actuator (4, 3) assigned to the requested throughflow (5) through the duct (11),

   Outputting the generated first signal (23, 22) to the at least one first actuator (4, 3),

   Generating a second signal (21) by the mass flow sensor (13), wherein the second signal (21) is a function of a throughflow (15) through the side duct (28),

   Processing of the second signal (21) generated by the mass flow sensor (13) to an actual value of the throughflow (15) through the side duct (28),

   Processing of the requested throughflow (5) through the feed duct (11) to a required value (32) of the throughflow (15) through the side duct (28),

   Generating a regulation signal (22, 23) by the regulator (37) for the at least one second actuator (3, 4) as a function of the actual value of the throughflow through the side duct (28) and as a function of the required value (32) of the throughflow (15) through the side duct (28),

   Outputting the generated regulation signal (22, 23) to the at least one second actuator (3, 4),

   wherein a first flow resistance element (14) and a second flow resistance element (19) are arranged in the side duct (28), wherein the first flow resistance element has a larger admittance surface than the second flow resistance element,

   the side duct (28) has a bypass duct (29) with a third flow resistance element (20),

   the mass flow sensor (13) is arranged in the bypass duct (29) of the side duct (28), wherein the flow resistance element (20) is arranged before the mass flow sensor (13), and

   the at least one first actuator (4, 3) and the at least one second actuator (3, 4) are arranged in series.
2. The method according to claim 1, wherein the processing of the requested throughflow (5) through the feed duct (11) to a required value (32) of the throughflow (15) through the side duct (28) comprises a reversibly unique assignment of the requested throughflow (5) through the feed duct (11) to a required value (32) of the throughflow (15) through the side duct (28).
3. The method according to one of claims 1 or 2, wherein a regulation signal is generated for the at least one second actuator (3, 4) on the basis of a proportional-integral regulator (37) or on the basis of a proportional-integral-derivative regulator (37).
4. The method according to one of claims 1 to 3, wherein the at least one second actuator of the burner device comprises a fan (3) with a rotational speed that can be set, wherein the fan (3) with a rotational speed that can be set comprises a drive, and wherein the fan (3) is arranged in the feed duct (11) of the burner device.
5. The method according to one of claims 1 to 4, wherein the generated regulation signal (22, 23) to the at least one second actuator (3, 4) is a pulse-width-modulated signal or is a converter signal with a frequency that corresponds to the rotational speed of at least one second actuator (3, 4) embodied as a fan (3).
6. The method according to one of claims 1 to 5, wherein the at least one first actuator of the burner device comprises a flap (4) with motorised adjustment with a drive and the flap (4) with motorised adjustment is arranged in the feed duct (11) of the burner device.
7. The method according to one of claims 1 to 6, wherein the processing of the second signal (21) generated by the mass flow sensor (13) comprises a filtering of the second signal (21) generated by the mass flow sensor (13).
8. The method according to one of claims 1 to 7, wherein the requested throughflow (5) through the feed duct (11) is assigned to a setting of the at least one first actuator (4, 3) on the basis of a predetermined table, in which values of the requested throughflow through the feed duct (11) are assigned to settings of the at least one first actuator (4, 3).
9. The method according to one of claims 1 to 8, the method additionally comprising the step:
   Determining a power of the burner device on the basis of the required value (32) of the regulator (37) and/or on the basis of the value of the requested throughflow (5) through the feed duct (11).
10. Non-volatile computer-readable storage medium that stores a set of instructions to be executed by at least one processor, which, when it is carried out by the processor, performs the method with the steps according to one of claims 1 to 9.

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