EP2348255B1 - Dual circuit combustion system and method for operating such a dual circuit combustion system - Google Patents

Description

Field of application and state of the art

The invention relates to a two-circuit burner system according to the preamble of claim 1 and a method for operating such a dual-circuit burner system according to the preamble of claim 9.

From the US 6,325,619 B2 For example, a gas burner with multiple burners is known, wherein the described gas burner has a first central burner arranged in the middle and a second burner arranged circularly around the central burner and at a distance therefrom. Furthermore, it is described that the gas burner has a flame sensor and / or an electrical ignition means. The flame sensor or the ignition means are preferably arranged in the flame region of the central burner and the only ignition means or the only flame sensor. Furthermore, the gas burner has two separate gas inputs, one for the gas supply of the central burner and one for the gas supply of the outer burner, wherein the control of the gas supply to the burner in each case by means of a separate, Separate control valve takes place to be able to modulate the central burner and the outer burner flexible and each separately. For each burner, therefore, a separate control valve and a separate shut-off valve must be provided. Furthermore, to set a total burner output, a corresponding partial burner output for the central burner and the outer burner must be set separately.

Furthermore, the documents reveal US Pat. No. 3,606,612 and US 2,781,779 A each a two-circuit burner system. The document US 2,765,810 A describes a burner system with a main burner, a simmer burner and a two-way gas valve.

Task and solution

The invention has for its object an initially mentioned two-circuit burner system and a method for operating such a dual-circuit burner system to create, with which problems of the prior art can be eliminated. This object is achieved by a two-circuit burner system having the features of claim 1 and by a method for operating such a dual-circuit burner system having the features of claim 9. Advantageous and preferred embodiments of the invention are the subject of further claims and are explained in more detail below , Some of the following, but not exhaustive, features and properties apply to both the dual circuit burner system and the process. They are sometimes described only once, but apply regardless of both the dual-circuit burner system and the process. The wording of the claims is incorporated herein by express reference.

It is a dual-circuit burner system for a gas hob provided with an operating device for setting a target total burner power and a preferably electronically controllable modulation valve with a control range. The dual-circuit burner system has an inner circle with an inner circle gas supply line and an inner circle burner with a maximum inner burner output. The inner circle gas supply leads in gas flow direction from the modulation valve to the inner circuit burner. Furthermore, the dual-circuit burner system has an outer circuit with an outer-circuit gas supply line and an outer-circle burner with a maximum outer burner output. The outer circle burner is disposed outside and around the inner circle burner, and the outer circle gas supply leads in the gas flow direction from the modulation valve to the outer circle burner. Furthermore, a control unit is provided. In this case, the control unit is designed to control at least the modulation valve. Particularly advantageously, the control unit is designed to control the entire two-circuit burner system. Preferably, the two-circuit burner system is electronically controlled or has an electronic control.

The modulation valve has a valve gas inlet, at least one valve gas outlet to the inner circle, and at least one valve gas outlet to the outer circle. Furthermore, the modulation valve has a single actuator for adjusting the gas flow rate to the inner circle and thus to control the internal burner power and to adjust the gas flow rate to the outer circuit and thus to control the outdoor burner power. Furthermore, an electronically controllable servomotor with an output shaft in the modulation valve is advantageously provided for driving the actuator. The servomotor can drive the actuator either directly or indirectly. In a preferred embodiment, the actuator is driven indirectly via a transmission, so the gas flow rate to the inner and outer circle and thus the overall burner performance can be finer. By means of the modulation valve, a required gas flow rate to the inner circle and the outer circle can be set in dependence on a set nominal total burner output.

A two-circuit burner system according to the invention is designed such that only one internal burner output is variable by means of the actuator in a part of the setting range and an outside burner output is zero. Furthermore, such a two-circuit burner system is designed so that in another Adjustment range by means of this actuator only the outside burner power can be changed and the internal burner power is maximum. The sum of the internal burner output and the sum of the external burner output results in the total burner output of the dual-circuit burner system. In this case, a maximum total burner output of the two-circuit burner system results from the sum of the maximum internal burner output and the maximum external burner output. In a preferred embodiment, the burner capacities of the inner circle burner and the outer circle burner are chosen such that the maximum internal burner power is less than the maximum external burner power.

Thus, a previously described two-circuit burner system is designed such that in the one setting range an overall burner line can be changed or adjusted or modulated by modifying only the internal burner output and that in the other setting range the total burner output is changed. Burner power can be changed or controlled by only the outer burner power is changed. To change the internal or external burner power thus only a modulation valve or even a common actuator is required.

According to the invention, the dual-circuit burner system has only a single modulation valve with a single actuator. In this case, the modulation valve is designed for the simultaneous control of the gas flow rate to the inner circle and the gas flow rate to the outer circle.

In an advantageous embodiment of the outer circle burner is preferably circular and arranged at some distance around the inner circle burner around and in particular arranged concentrically around the inner circle burner around.

According to the invention, such a dual-circuit burner system to a modulation valve that is designed so that over its entire control range of the valve gas outlet is only open to the outer circle, when the valve gas outlet is open to the inner circle and the opening cross-section to the inner circle and thus thereby set gas flow rate to the inner circle exceeds a defined minimum value. This means that the modulation valve is designed so that the valve gas outlet to the outer circle and thus the gas supply to the outer circle can only be opened when the opening cross section to the inner circle is so large that set by this opening cross-section, defined gas flow to the inner circle has a minimum value exceeds. In particular, the actuator and the valve gas outputs to the inner circle and the outer circle are thus designed so that never only the valve gas outlet to the outer circle can be opened alone. The modulation valve is thus designed so that in the control range in which only the internal burner power is variable, the valve gas outlet to the outer circuit is always closed and thus the outside burner power is constantly zero. In a preferred embodiment, the minimum value corresponds to a gas flow rate required for the maximum internal burner output.

According to the invention, the actuator has one or more openings and the modulation valve is designed so that one or more openings or a closed region of the actuator in response to the actuating position of the actuator overlap the valve gas outlet to the inner circle and the valve gas outlet to the outer circle in that for each parking position either a defined gas flow rate to the inner circle and a defined gas flow rate to the outer circle or only a defined gas flow rate to the inner circle and a closed valve gas outlet to the outer circle or a complete closed position of the modulation valve can be set. In the full closed position, the closed area of the actuator overlaps the valve gas outlet to the inner circle and the valve gas outlet to the outer circle respectively Completed. The valve gas outlets to the inner circle and to the outer circle are closed completely and separately from each other at the same time. In this way it can be ensured that a gas supply to the outer circuit and thus an operation of the outer circle burner is only possible if the inner circle burner is already burning and the maximum internal burner power is not sufficient to set the desired target total burner power ,

In a preferred embodiment of the invention, the actuator is. With respect to its at least one opening formed so that starting from the full closed position with an increasing set target total burner power gas flow to the outer circle is adjustable only when the gas flow to the inner circle or the corresponding internal burner power exceeds a required minimum value or its lower tolerance limit. In this case, the minimum value is preferably about 90% to 100% of the gas flow rate required for a maximum internal burner output, or 90% to 100% of the maximum internal burner output. In particular, the minimum value corresponds to the maximum internal burner power or the gas flow rate required for this power.

According to the invention, the modulation valve is a rotor disk valve and has a rotor disk as an actuator. In this case, the rotor disk is rotatably mounted on an axle or a shaft and has one or more openings for setting a defined gas flow rate to the inner circle and the outer circle. The rotor disk is arranged in the gas flow direction in front of the valve gas outlet to the inner circle and in front of the valve gas outlet to the outer circle. With regard to the structure, the function and the properties of such a rotor disk valve is at this point on the DE 10 2009 047 914 A1 the same applicant. In this case, the opening cross section of the valve gas outlet to the inner circle is preferably smaller than the opening cross section of the valve gas outlet to the outer circle.

By rotating the rotor disk and changing its angular position, an overlap of the at least one opening of the rotor disk with the valve gas outlet to the inner circle or the valve gas outlets to the inner and outer circle. Thus, a defined gas flow rate to the inner circle or to the inner and outer circle can be adjusted and thus the desired target total burner power.

In a preferred embodiment, the rotor disk is mounted directly on the output shaft of the servo motor, which is also the drive shaft of the actuator, and connected thereto in a rotationally secure manner. In a particularly preferred embodiment, the rotor disk is mounted on an output shaft of the transmission driven by the servo motor.

In a preferred embodiment, at least one opening of the rotor disk is elongate and partially formed approximately in the circumferential direction. In this case, the opening preferably has a constant, small opening width at one end and a constant, large opening width at the other end. In between, in particular, a transition region connecting these two ends is provided with increasing opening width from the small opening width to the large opening width. In this case, an opening width may be designated as large if the opening width corresponds approximately to the opening width of a valve outlet and as small if it is significantly smaller than the opening width of the valve outlet.

In one embodiment of the invention, at least one opening of the rotor disk in the circumferential direction and in approximately silverfish-shaped. In this case, the rotor disk is designed so that, starting from the complete closed position and thus of a total burner power of zero with an increasingly changing angular position of the rotor disk initially the end with the small opening width overlaps the valve gas outlet to the inner circle and the closed area of the rotor disk the valve gas outlet closes to the outer circle and thus the gas supply to the outer circuit is closed.

With a further change in the angular position with the same direction of rotation then increases by the increasing opening width of the opening cross-section to the inner circle, and thus the set gas flow to the inner circle until the overlapping of the opening of the rotor disk with the valve Gausausgang resulting opening cross-section to the inner circle is so large in that a defined gas flow rate to the inner circuit is adjustable for a maximum inner burner output, while the valve gas outlet to the outer circuit is still closed or overlapped by the closed region of the rotor disk.

With still further increasing angular position then overlaps the transition region of the opening of the rotor disk, the valve gas outlet to the inner circle and the small opening width of the valve gas outlet to the outer circle. This opens the valve gas outlet to the outer circuit and allows a defined gas flow rate to the outer circuit to be set. If the maximum burner output is reached, however, a further increase in the gas flow rate no longer leads to a further increase in the burner output, since the associated gas outlet nozzles of the burner limit an outflow of gas upwards. This means that a further increase in the gas flow rate to the inner circle or outer circle above the corresponding maximum burner power does not lead to a further increase in the internal or external burner performance when the maximum gas outlet volume at the inner circle or outer circle burner is already reached. This means that the inner circle burner can continue to be operated with its maximum power even with increasing angular position, once it has been reached or the required gas flow rate to the inner circle. Thus, in spite of an increasing angular position, a defined gas flow rate to the inner circle can be set for a maximum inner burner output. If the angular position increases further, finally the large opening width overlaps the valve gas outlet to the inner circle and at least the transition area or the large opening width the valve gas outlet to the outer circle, until the opening cross section resulting from the overlap of the opening of the rotor disc with the valve gas outlets is so large that at the same time a defined gas flow rate to the inner circle for maximum internal burner power and a defined gas flow rate to the outer circle for a maximum outdoor burner power and thus for the maximum total burner power can be adjusted to the outer circle.

In an alternative embodiment, at least one opening of the rotor disk may also be approximately crescent-shaped and partially circumferential in the circumferential direction, and each have a small opening width at both ends and a large opening width in the middle therebetween, each with a transition region from the center to the ends decreasing opening width. The large opening width of this crescent-shaped opening is at least so large that the outer circle required for a maximum outdoor burner power gas flow rate can be adjusted. At the one end, which overlaps the valve gas outlet to the inner circle only in an angular position above the angular position for setting the maximum internal burner output opening width is to be provided at least until the end that the gas flow rate to the inner circle always at least that for a maximum Internal burner power required gas flow rate corresponds.

It is also conceivable a rotor disk with a plurality of openings, which may be formed, for example, in two parts or in several parts. The openings can also be formed in stages and without a transition region. However, the rotor disk must be designed such that a suitable combination of the adjustable gas flow rate to the inner circle and the adjustable gas flow rate to the outer circle is provided for each defined angular position according to the aforementioned embodiments. In this case, the rotor disk is preferably designed so that starting with increasing angular position from the closed position, the adjustable total burner power preferably increases steadily or in stages.

In a development of the invention, the rotor disk valve has two rotation stops. These each limit the possible angle of rotation or the angular position of the rotor disk in one direction of rotation and thus define a permissible angle of rotation range of the rotor disk. The rotation stops are positioned so that a gas supply to the outer circuit can only be set if the valve gas outlet to the inner circuit is open. The rotation stops are preferably designed as mechanical stop elements, for example as pins. The rotor disk has in particular in at least part of its circumference in the radial direction an outwardly projecting outer contour, so that the rotational stop results from the mechanical interaction of a stop element with the specially designed outer contour of the rotor disk.

In a further embodiment of the invention, the two-circuit burner system has a gas inlet for connecting a gas supply and additionally at least one electronically controllable shut-off valve, which is advantageously arranged between the gas inlet of the two-circuit burner system and the valve gas inlet of the modulation valve. Preferably, the shut-off valve is a solenoid valve. In a particularly preferred embodiment, the two-circuit burner system on two shut-off valves, in particular two in series shut-off valves. If a gas cooking appliance has one or more additional gas burners in addition to the two-circuit burner system, it is particularly advantageous to branch the gas feed line for supplying the further gas burners between the two shut-off valves connected in series so that the gas supply to all gas burners of the gas cooking appliance is closed by the first shut-off valve can be.

In a particularly preferred embodiment, the modulation valve and at least one shut-off valve form a structural unit. Preferably, all valves of the two-circuit burner system are combined to form a structural unit. In a further embodiment, the two-circuit burner system has an electronically controllable ignition device and a Überzündbrücke, preferably a mechanical Überzündbrücke. The ignition device is arranged on the inner circle burner and the Überzündbrücke between the inner circle burner and the outer circle burner. The Überzündbrücke is arranged so that the outer circle burner can be ignited by means of the inner circle burner and the Überzündbrücke when the inner circle burner is burning and the gas supply to the outer circle is opened. In particular, the electronically controllable ignition device is the only ignition device of the two-circuit burner system. This arrangement of the ignition device in conjunction with the Überzündbrücke only a single ignition device for the dual-circuit burner system is required and not for each burner a separate.

In a development of the invention, the two-circuit burner system has a flame sensor, which is arranged in the flame region of the inner-circle burner. It is advantageous if the flame sensor can also detect flames in the area of the over-ignition bridge between the burners. In this case, the flame sensor is preferably the only flame sensor of the two-circuit burner system. In a preferred embodiment, the flame sensor is a thermocouple or an ionization electrode and in particular can be evaluated electronically by the control unit.

In a development of the invention, the two-circuit burner system has an electrode, which is also designed as an ignition device and as a flame sensor. In this case, the electrode is arranged in the flame region of the inner-circle burner. This is advantageous because only one common electrode is needed, which saves space and reduces costs. In a particularly advantageous embodiment, the electrode is the only electrode of the two-circuit burner system.

In a preferred embodiment, the modulation valve, at least one shut-off valve and / or the ignition device of the electronically controlled two-circuit burner system be controlled by the control unit. In this case, the control unit preferably receives at least one signal from the operating device with the set nominal total burner output and in particular additionally at least one signal from a flame sensor with information about the flame state.

A method is provided for controlling a target total burner power of an aforementioned electronically-controlled, dual-circuit burner system in a range of total burner power from zero to a maximum total burner power. According to the invention, a nominal total burner output greater than zero is set by opening the gas supply to the modulation valve, opening at least the valve gas outlet to the inner circuit as a function of the nominal total burner output set by the user or the set power requirement by means of the modulation valve. a defined gas flow rate to the inner circle and the outer circle is set and ignited according to the set target total burner power at least the inner-ring burner. According to the invention, a nominal total burner output of zero is set by blocking the gas supply to the inner circle and to the outer circle.

It should be noted that if the dual-circuit burner system has an electronically controllable ignition device that it is activated at the latest when the gas supply is opened. This means that the gas supply is opened for safety reasons only when the ignition device has already been activated. The ignition device is designed so that it is ready for ignition after a certain time, for example by means of a clocked spark or an annealing electrode.

Preferably, only the inner ring burner is ignited for small outputs, especially when the power requirement is less than or equal to the maximum inner burner power, while the valve gas outlet remains closed to the outer circuit. If the power requirement is above the maximum internal burner power, In addition, the outer circle burner is ignited, so that the desired target total burner power can be achieved.

In one embodiment of the invention, the gas supply to the inner circuit and the outer circuit is blocked and thus set a total target burner output of zero by the modulation valve is completely closed, or by means of at least one shut-off valve, the gas supply to the valve gas inlet of the modulation valve and thus to Inner circle and locked to the outer circle. Alternatively, the gas supply to the valve gas inlet of the modulation valve can also be blocked by means of at least one shut-off valve and at the same time the modulation valve can be completely closed, which is particularly advantageous. The complete closed position of the modulation valve is adjusted by closing the valve gas outlets to the inner circle and the outer circle. If the two-circuit burner system has two shut-off valves connected in series one behind the other, without the gas supply line branching between them to supply additional gas burners, preferably both are closed. In this way, a high level of security with regard to a shut-off to avoid unwanted gas leakage is possible.

In a further development of the invention, a nominal total burner output in a lower power range is set above a stable internal burner output and below a maximum internal burner output by a defined gas flow rate to the inner circuit corresponding to the desired nominal total burner power or temporarily corresponding to a predefined Ignition power is set and the inner circle burner is ignited. The valve gas outlet to the outer circuit remains permanently closed during this time. The stable internal burner output is the smallest internal burner output for which stable flame operation of the internal circuit burner is possible. Only in a stable operating condition above a stable operating burner performance, a stable flame can form and there is no risk that the flame goes out even with small fluctuations in the supplied gas flow rate or low interference from the outside. Below this stable burner power can be a burner Do not burn with a stable flame, as even small fluctuations in the gas supply can lead to an irregular flame formation or to extinguishment of the flame. A burner should therefore preferably be operated at least with its operationally stable burner power or above it.

In a further development of the invention, a setpoint total burner output is set in an upper power range above the maximum inner burner output, above an operationally stable outer burner output and below a maximum total burner output, by a defined gas flow rate to the inner circuit corresponding to the maximum inner burner output is set and for the outer circle a defined gas flow rate is set according to the required in addition to the maximum indoor burner power outdoor burner power. The inner circle burner is ignited and this ignites the outer circle burner by means of a Überzündbrücke. In this case, the stable external burner power is the smallest external burner power, for a stable flame operation of the outer circle burner is possible. The additionally required external burner output is the external burner output, which results from the difference between the user-set nominal total burner output or power requirement and the maximum internal burner output. So the power that the inner circle burner lacks to reach the performance requirement of the user.

In a further development of the invention, a nominal total burner output in the lowest power range of the two-circuit burner system is set below the operationally stable internal burner output by operating the internal-circuit burner in a cycle. For this purpose, the inner circle burner is switched on and off alternately. When switched on, it preferably burns with the operationally stable internal burner output. The clocking takes place by the gas supply to the inner circle and to the outer circle is cyclically locked and opened and is ignited in each cycle of the inner circle burner means of the ignition device again. For igniting the ignition device is controlled by the control unit accordingly.

By clocking the inner circle burner can be operated for a set target total burner capacity below the stable operating internal burner power with a stable operating internal burner power. However, in order to set the desired, set nominal total burner output or the corresponding amount of energy, the inner circuit burner is alternately switched on and off accordingly.

In a further development of the invention, a nominal total burner output in the lowermost power range of the outer circuit burner above the maximum inner burner output is set with an additionally required outer burner output below the operationally stable outer burner output by the inner circle burner having its maximum inner burner output. Burner power burns in continuous operation and the outer circuit burner is operated clocking. For the cyclic operation of the outer circle burner this is alternately switched on and off. In the switched-on state, the outer-circle burner preferably burns with the stable outer burner output.

In a further development of the invention for controlling an aforementioned two-circuit burner system with at least one electronically controllable shut-off valve, which is controlled by the control unit, controls the control unit to start the operation of the two-circuit burner system, the shut-off valve and opens this and thus the gas supply to the valve Gas input of the modulation valve, if a nominal total burner output is set above zero.

In a further development of the invention for controlling an aforementioned two-circuit burner system with at least one electronically controllable shut-off valve and an electronic ignition device, the modulation valve, the shut-off valve and the ignition device for starting the operation of the two-circuit burner system, when a target total burner power is set greater than zero is so controlled by the control unit that the gas supply is opened at least to the inner circle and the inner-circle burner is ignited.

In a preferred embodiment of the invention for controlling an aforementioned two-circuit burner system with a flame sensor and at least one electronically controlled by the control unit shut-off valve, the control unit controls the shut-off valve and closes this when the flame sensor detects a flame failure or faulty flame operation or if the set target Total burner power is zero. In this way, the gas supply is closed as soon as the flame operation is faulty or there is a flame failure or power requirement no longer exists or the inner circuit is switched off for clocking. In this case, the control unit receives at least one corresponding signal about the flame condition from the flame sensor.

The gas supply to the inner circle and to the outer circle can also be blocked via the modulation valve, however, the dynamics of the shut-off valve is higher. This means that the gas supply via the shut-off valve can be closed faster than by means of the modulation valve. Therefore, it is advantageous for safety reasons to block the gas supply by means of at least one shut-off valve in the event of a flame failure. For methods with automatic reignition, it has proven to be particularly advantageous to lock the gas supply in a flame failure exclusively through the shut-off valve and, if necessary, to control the modulation valve so that a predefined ignition position is set or one for the ignition of the inner circle burner sufficient gas flow rate to initiate the re-ignition as soon as possible. Preferably, in the off state or upon detection of a continued burning of a flame after switching off all valves of the dual-circuit burner system, including the modulation valve, closed.

In a further development of the invention for controlling an aforementioned two-circuit burner system with at least one electronically controllable shut-off valve, the gas supply to the inner circuit is cyclically locked and opened for clocking the inner circle burner by the control unit cyclically activates the shut-off valve for opening and closing and by means of the modulation valve a sufficient for the ignition of the inner circle burner gas flow rate is set to the inner circle. Meanwhile, the valve gas outlet to the outer circuit is permanently closed.

In a further development of the invention for controlling an aforementioned dual-circuit burner system with an electronically controllable ignition device with a Überzündbrücke the cyclic operation of the outer-circle burner by the gas supply to the outer circuit is cyclically locked and opened while the gas supply to the inner circuit remains open. The gas supply and thus the set gas flow rate to the inner circuit is preferably constant and the inner-circle burner burns in continuous operation, in particular with a constant internal burner power. After each opening of the gas supply to the outer circuit of the outer circle burner is ignited by means of the inner circle burner and the Überzündbrücke. When the gas supply to the outer circuit burner is closed, the outer circuit burner flame goes out while the inner circuit burner continues to burn. The flame sensor located on the inner circuit does not detect a flame failure, leaving the shut-off valve open. If the gas supply to the outer circuit is reopened, the outer-ring burner is ignited again by means of the burning inner-circle burner through the over-ignition bridge.

In a preferred embodiment of the method for controlling an aforementioned two-circuit burner system with an electronically controllable ignition device for clocking the outer circle burner, the gas supply to the outer circuit is cyclically locked and opened by the control unit controls the modulation valve so that the gas supply to the outer circuit cyclically open and is closed, while the set gas flow rate to the inner circuit preferably remains constant and corresponds to the gas flow rate for the maximum internal burner power. In an advantageous embodiment, when the gas supply to the outer circuit is opened, the gas flow rate to be set to the outer circuit is set in each case slightly above the actually required gas flow rate. To make sure the outer circle burner also really ignites and the gas supply is sufficient, the modulation valve is quasi "overdriven".

Brief description of the drawings

Fig. 1

ein erfindungsgemäßes Zweikreis-Brennersystem,

Fig. 2

ein Diagramm zur Darstellung der Leistungsbereiche eines erfindungsgemäßen Zweikreis-Brennersystems mit einer GesamtBrennerleistung von Null bis zu einer maximalen Gesamt-Brennerleistung,

Fig. 3

eine Ansicht in Gasflussrichtung auf eine Rotorscheibe eines Modulationsventils eines erfindungsgemäßen Zweikreis-Brennersystems in einer Winkelposition mit maximaler Gaszufuhr zum Innenkreis und zum Außenkreis und damit mit maximal eingestellter Gesamt-Brennerleistung

Fig. 4

eine Ansicht auf die Rotorscheibe gemäß Fig. 3 in einer Winkelposition mit eingestellter maximaler Innen-Brennerleistung und einer teilweise geöffneten Gaszufuhr zum Außenkreis,

Fig. 5

eine Ansicht auf die Rotorscheibe gemäß Fig. 3 und 4 in einer Winkelposition mit eingestellter maximaler Innen-Brennerleistung und geschlossener Gaszufuhr zum Außenkreis,

Fig. 6

eine Ansicht auf die Rotorscheibe gemäß Fig. 3, 4, und 5 in einer Winkelposition mit einer nur teilweise geöffneten Gaszufuhr zur Einstellung einer Innen-Brennerleistung unterhalb der maximalen Innen-Brennerleistung und

Fig. 7

eine Ansicht auf die Rotorscheibe gemäß Fig. 3, 4, 5 und 6 in der vollständigen Geschlossenstellung des Modulationsventils.

Embodiments of the invention are shown schematically in the drawings and are explained in more detail below. The embodiments shown in the individual figures have some features that are not shown in all embodiments shown or not all embodiments shown have. In the drawings show:

Fig. 1

a two-circuit burner system according to the invention,

Fig. 2

3 is a diagram showing the power ranges of a two-circuit burner system according to the invention with a total burner power of zero up to a maximum total burner power,

Fig. 3

a view in the gas flow direction of a rotor disk of a modulation valve of a dual-circuit burner system according to the invention in an angular position with maximum gas supply to the inner circle and the outer circle and thus with a maximum set total burner power

Fig. 4

a view of the rotor disk according to Fig. 3 in an angular position with set maximum internal burner power and a partially open gas supply to the outer circuit,

Fig. 5

a view of the rotor disk according to 3 and 4 in an angular position with set maximum internal burner power and closed gas supply to the outer circuit,

Fig. 6

a view of the rotor disk according to Fig. 3, 4 , and 5 in an angular position with a partially open gas supply for setting an internal burner power below the maximum internal burner power and

Fig. 7

a view of the rotor disk according to Fig. 3, 4 . 5 and 6 in the full closed position of the modulation valve.

Detailed description of the embodiments

Fig. 1 shows a schematic representation of an exemplary, inventive dual-circuit burner system 10. The figure shows in detail a two-circuit burner 13 with an outer circle burner 40 and an inner circle burner 36. In this embodiment, the inner circle burner 36 is an electronically controllable ignition device 32nd arranged with a Überzündbrücke 38. The ignition device 32 may be, for example, an ignition electrode for electric spark ignition or a glow starter. Furthermore, a flame sensor 34 is arranged in the flame region of the inner circle burner 36. The embodiment shown has two separate components for the ignition device 32 and the flame sensor 34 for better understanding. However, it is particularly advantageous to provide only a single, common electrode, which is designed both as an ignition device 32 and as a flame sensor 34. The ignition device 32 and the flame sensor 34 are connected to an electronic control unit 26. Via an operating device 11, the electronic control unit 26 receives a nominal total burner power and thus a power requirement for the dual-circuit burner 13. Furthermore, the dual-circuit burner system 10 has a gas inlet 12 for connecting a gas supply 14 with a gas supply V. The gas supply to the inner-circle burner 36 via an inner-circuit gas supply line 44 and the gas supply to the outer-circle burner 40 by means of an outer-circuit gas supply line 42. The inner-circle burner 36 and the inner gas supply 44th are hereinafter referred to collectively as inner circle. The outer circle burner 40 and the outer circle gas supply line 42 are referred to as outer circle accordingly. A defined gas flow rate to the inner circle and the outer circle is adjusted by means of a modulation valve 50. This modulation valve 50 has a servomotor 22 for driving an actuator 52. The actuator 52 is a rotor disk in a rotor disk valve as a modulation valve 50. However, if the actuator 52 is a rotor disk, its axis of rotation is parallel to the gas flow direction within the modulation valve and not as in FIG Fig. 1 for the sake of simplicity, only schematically shown transversely thereto.

Furthermore, the modulation valve 50 has a common valve gas inlet 18 and a valve gas outlet 46 to the inner circle and a valve gas outlet 48 to the outer circle. The modulation valve 50 or the associated servomotor 22 of the modulation valve 50 is controlled by the electronic control unit 26. Between the valve gas inlet 18 of the modulation valve 50 and the gas inlet 12 of the dual-circuit burner system 10, a shut-off valve 16 is arranged in the gas flow direction. The shut-off valve 16 is electronically controllable in this embodiment and is controlled by the control unit 26. Preferably, generally at least one shut-off valve is combined with the modulation valve to form a structural unit. In this embodiment, only one shut-off valve between the gas inlet 12 and the modulation valve 50 is arranged. In an advantageous embodiment, two shut-off valves are connected in series in this area, wherein in a particularly preferred embodiment of the gas supply line between the two shut-off valves gas supply lines may be diverted to supply additional gas burner.

If a setpoint total burner output greater than zero is set on the operating device 11, the control unit 26 receives a corresponding power requirement and opens the shut-off valve 16 and thus the gas supply to the modulation valve 50. Furthermore, the modulation valve 50 is also actuated by the control unit 26 and by means of the servomotor 22, the actuator 52 is driven. By means of the actuator 52, a defined gas flow rate to the inner circle and a defined gas flow rate to the outer circuit is set or depending on the height of the power demand only a defined gas flow rate to the inner circuit while the gas supply to the outer circuit remains closed. The setting of a defined gas flow rate to the inner or outer circle takes place by the corresponding valve gas outlet 46 or 48 of the modulation valve 50 is opened correspondingly wide by the actuator 52. If the gas supply to the inner circuit is opened, the ignition device 32 at the inner circle burner 36 is controlled by the control unit 26 and ignites the inner circle burner 36. By means of the Überzündbrücke 38 takes place at an open gas supply to the outer circle automatically the ignition of the outer circle burner 40 when the inner-circle burner 36 is burning.

Fig. 2 shows a diagram illustrating the individual power ranges of a dual-circuit burner system according to the invention with a total burner power from zero to a maximum total burner power. Shown is the total burner power P _total over a defined gas flow rate V, which is supplied to the two-circuit burner system. Here, the defined gas flow rate V is the sum of the inner flow supplied gas flow rate V _inside and the outer circle supplied gas flow rate V _outside . When the gas supply is closed, the total burner output P is _total = 0. For stable operation of the internal- _circuit burner 36, a minimum _{gas flow} rate V _{internally stable is} required, which corresponds to an associated internal _{burner output} of P inside- _stable . With increasing gas flow rate to the inner circle up to the maximum gas flow rate V _{innen_max of} the inner circle, the power of the inner circle burner 36 continuously increases up to its maximum internal burner power P _{innen_max} . If the required nominal total burner power is greater than the maximum internal burner power P _{innen_max} , the additional power requirement is ensured by the outer circuit burner 40. The outer _circuit burner 40 also requires a _{Mindestgasdurchflussmenge} V _{außen_stabil} for a stable flame operation. Preferably, it is avoided by a corresponding control of the modulation valve to adjust such gas flow rates, the would result in unstable flame operation of the inner circle burner or the outer circle burner. From an outside burner power P _{outside_stabil} increases with increasing gas supply to the outer circle, the external burner power also continuously up to the maximum outdoor burner power P _{außen_max} . The sum of the maximum internal burner power P _{innen_max} and the maximum external burner power P _{außen_max} gives the maximum total burner power P _{total_max} .

In Fig. 3 is for a modulation valve 50, which is designed as a rotor disk valve, a view in the gas flow direction on a rotor disk 60 of a modulation valve 50 of a dual-circuit burner system 10 according to the invention shown in an angular position 72a with maximum gas supply to the inner circle and the outer circle and thus with maximum set total burner power , The angular position 72a of the rotor disk 60 corresponds to a set gas flow rate for the maximum total burner power P _{total_max} . The figure shows a valve gas outlet to the inner circle 46 and a valve gas outlet 48 to the outer circle. The rotor disk 60 has an opening 64, which is arranged in the circumferential direction oblong, partially encircling and formed in this embodiment silverfish-shaped. The opening 64 has at its one end a region 55 with a constant, large opening width and at its other end a region 54 with a constant small opening width. The rotor disk 60 is rotatably mounted on a drive shaft 62, wherein it is non-rotatably connected to the drive shaft 62, which is not shown here. The drive shaft 62 corresponds to the output shaft of the servomotor 22 of the modulation valve 50. In an alternative embodiment, not shown here, the rotor disc, instead of rotation on a drive shaft, also rotatably mounted on a fixed axis and by a pinion with the aid of a on the outer edge of the rotor disk incorporated gear rim are driven. At this point will be on the aforementioned DE 10 2009 047 914 A1 the same applicant. In the figure, the rotor disk 60 is further shown with an outwardly projecting in an area 56 outer contour, which cooperates with a rotation stop 58. This rotation stop 58 is in this embodiment designed as a stop element, for example in the form of a positioning pin to which the protruding outer contour 56 of the rotor disk 60 abuts in its end position. In this embodiment, the position of the rotation stop 58 is selected so that the rotation stop in this direction of rotation in the setting of the maximum total burner power P _samtj-max , as shown in this figure, is achieved. Furthermore, a further rotation stop 66 is present, which is designed analogously to the rotation stop 58 and is positioned so that a defined closed position of the modulation valve 50 and the rotor disk valve can be adjusted. For the in Fig. 3 shown angular position 72a of the rotor disk 60 results in a defined opening cross section 69a to the inner circle and a defined opening cross section 71a to the outer circle, the gas flow rate to the inner circle or the outer circle is maximum, so that with this angular position, the maximum total burner power P _{total_max is} set.

Fig. 4 shows a view of the rotor disk 60 according to Fig. 3 in an angular position 72b with a set maximum internal burner power and a partially open gas supply to the outer circuit. In this case, the opening 64 of the rotor disk 60 overlaps with the valve gas outlet 46 to the inner circle such that a defined opening cross-section 69b and thus a defined gas flow rate to the inner circle adjusts, which corresponds to a maximum internal burner power. Although in Fig. 4 the defined opening cross section to the inner circle 69b is significantly smaller than in Fig. 3 , the maximum internal burner output is still set. With increasing gas flow rate, the associated burner power can be increased up to a maximum burner output. If the maximum burner output is reached, however, a further increase in the gas flow rate no longer leads to a further increase in the burner output, since the associated gas outlet nozzles of the burner limit an outflow of gas upwards. This means that a further increase in the gas flow rate to the inner circle or outer circle above the corresponding maximum burner power does not lead to a further increase in the internal or external burner power, if the maximum gas outlet volume at the inner circle or outer circle burner already is reached. This also applies to the in Fig. 4 shown angular position 72b. With the setting of a defined opening cross section 69b to the inner circle, the maximum possible gas supply V _{innen_max} is already reached. If the gas supply is further increased, the internal burner power does not increase further, since the design of the gas outlet nozzles on the inner-circle burner 36, the maximum gas outlet amount is limited. In Fig. 4 is further shown that the opening 64 forms with the valve gas outlet 48 by overlapping a defined opening cross-section 71b to the outer circle and thus partially opens the gas supply to the outer circle and adjusts a defined gas flow rate to the outer circle. The outer circuit is operated at this setting with an external burner power between a _stable operating outdoor burner power P _{au-ßen_stabil} and the maximum outdoor burner power P _{außen_max} .

In Fig. 5 is a view of the rotor disk 60 according to 3 and 4 shown in an angular position 72c with set maximum internal burner power P _{innen_max} and closed gas supply to the outer circle. The angular position 72c is shown, which corresponds to a total burner output Ptot below the maximum internal burner power P _{inside_max} . The opening 64 of the rotor disk 60 forms with the valve gas outlet 46 to the inner circle a defined opening cross section 69 c and thus sets a defined gas flow rate to the inner circle. This gas supply to the outer circuit is closed. The closed region of the rotor disk 60 completely covers the valve gas outlet 48 to the outer circle.

In Fig. 6 is a view of the rotor disk 60 according to Fig. 3, 4 , and 5 shown with an angular position 72d with a partially open gas supply for adjusting an internal burner power below the maximum internal burner power P _{innen_max} . In this case, this angular position corresponds to 72d an internal burner power at the lowest limit, namely the smallest internal burner power P _{innen_stabil} at a stable flame operation is possible. The defined opening cross-section 69d is here again significantly smaller than in Fig. 5 , The gas supply to the outer circuit is still closed.

In Fig. 7 a view of the rotor disk 60 according to Fig. 3, 4 . 5 and 6 shown in the full closed position of the modulation valve 50. In this case, the rotor disk 60 is shown in the angular position 72e. The protruding outer contour 56 abuts the rotation stop 66. The closed region of the rotor disk 60 completely covers both valve gas outlets 46 and 48 to the inner circle and to the outer circle. The gas supply is completely closed. The opening 64 of the rotor disk 60 does not overlap with the valve gas outlets 46 and 48. The gas supply to the inner circle and to the outer circle is respectively closed.

Claims (14)

1. Two-ring burner system (10) for a gas hob, comprising:

   - an operator control device (11) for setting a target total burner capacity,

   - a controllable rotor disc valve (50) with a setting range,

   - an inner ring, wherein the inner ring has an inner ring gas supply line (44) and an inner ring burner (36) with a maximum inner burner capacity (P_{innen_max}) and the inner ring gas supply line (44) leads from the rotor disc valve (50) to the inner ring burner (36) in the gas flow direction,

   - with an outer ring, wherein the outer ring has an outer ring gas supply line (42) and an outer ring burner (40) with a maximum outer burner capacity (P_{außen_max}), wherein the outer ring burner (40) is arranged outside the inner ring burner (36) surrounding the latter and the outer ring gas supply line (42) leads from the rotor disc valve (50) to the outer ring burner (40) in the gas flow direction,

   - a control unit (26), wherein the control unit (26) is configured to control at least the rotor disc valve (50),

   wherein the rotor disc valve (50) includes:

   - a valve gas inlet (18),

   - at least one valve gas outlet (46) to the inner ring,

   - at least one valve gas outlet (48) to the outer ring,

   - a motor-driven rotor disc (52, 60) for setting a gas flow volume (V_innen) to the inner ring, and thereby for controlling the inner burner capacity (P_innen) and for setting a gas flow volume (V_außen) to the outer ring, and thereby for controlling the outer burner capacity (P_außen), and

   - a controllable servomotor (22) having an output shaft (62) for direct or indirect driving of the rotor disc (52, 60),

   - the rotor disc valve (50) being the only valve of the two-ring burner system (10),

   - the rotor disc valve (50) including a single actuator as rotor disc (52, 60), wherein by means of the rotor disc valve (50), as a function of a set target total burner capacity and thereby as a function of a respective required defined gas flow volume (V_innen,V_außen) to the inner ring and the outer ring, a respective defined opening cross-section (69a to 69d, 71a to 71b) to the inner ring and to the outer ring can be set, wherein

   - the two-ring burner system (10) is configured such that by means of the rotor disc (52, 60) in a part of the setting range only an inner burner capacity (P_innen) is variable and therein an outer burner capacity (P_außen) is zero,

   - in another part of the setting range by means of said rotor disc (52, 60) only the outer burner capacity (P_außen) is variable and the inner burner capacity (P_innen) is maximum,

   - the rotor disc (60)

   - is rotatably mounted on the output shaft (62) in the rotor disc valve (50),

   - has one or more openings (64) for setting a defined gas flow volume (V_innen,V_außen) to the inner ring and to the outer ring,

   - is disposed upstream of the valve gas outlet (46) to the inner ring and upstream of the valve gas outlet (48) to the outer ring in the gas flow direction.
2. Two-ring burner system (10) according to claim 1, characterized in that the at least one opening (64) is configured such that, starting from the completely closed position with an increasing set target total burner capacity, a gas flow volume (V_außen) to the outer ring is settable only when the gas flow volume (V_innen) to the inner ring and the corresponding inner burner capacity (P_innen), respectively, exceeds a required minimum value, wherein preferably said minimum value is approximately 90 % to 100 % of the gas flow volume (V_{innen_max}) required for a maximum inner burner capacity (P_{innen_max}) and 90 % to 100 % of the maximum inner burner capacity (P_{innen_max}), respectively, in particular corresponding thereto.
3. Two-ring burner system (10) according to claim 1 or 2, characterized in that the opening cross-section of the valve gas outlet (46) of the rotor disc valve (50) to the inner ring is less or equal to the opening cross-section of the valve gas outlet (48) to the outer ring.
4. Two-ring burner system (10) according to claim 1 or 3, characterized in that at least one opening (64) of the rotor disc (60) is elongate and partially circumferential, preferably with a constant, small opening width (54) on one end and with a constant, great opening width (55) on the other end, wherein in particular a transition region connecting them is provided there between with an increasing opening width from the small opening width (54) to the great opening width (55).
5. Two-ring burner system (10) according to claim 4, characterized in that the opening (64) of the rotor disc (60) has an approximately silverfish-shaped outer contour in the circumferential direction and is configured such that, starting from the completely closed position, with an angular position (72e to 72a) of the rotor disc (60) varying increasingly

   - initially, the end with the small opening width (54) overlaps the valve gas outlet (46) to the inner ring and the closed region of the rotor disc (60) seals the valve gas outlet (48) to the outer ring,

   - that then, with a further varying angular position (72e to 72a) due to the increasing opening width, the opening cross-section (69d to 69a) to the inner ring and thereby also the gas flow volume (V_innen) to the inner ring increases, while the valve gas outlet (48) to the outer ring remains closed,

   - until the opening cross-section (69d to 69a) to the inner ring resulting from overlapping of the opening (64) of the rotor disc (60) with the valve gas outlet (46) is great enough that a defined gas flow volume (V_innen, V_{innen_max}) to the inner ring for a maximum inner burner capacity (P_{innen_max}) can be set, wherein the valve gas outlet (48) to the outer ring is still closed, and

   - that then, with an even further increasing angular position (72e to 72a), the transition region of the opening (64) of the rotor disc (60) overlaps the valve gas outlet (46) to the inner ring and the small opening width (54) overlaps the valve gas outlet (48) to the outer ring and thereby the valve gas outlet (48) to the outer ring is opened and a defined gas flow volume (V_außen) to the outer ring can be set, while a defined gas flow volume (V_innen, V_{innen_max}) to the inner ring for a maximum inner burner capacity (P_{innen_max}) remains settable,

   - until the opening cross-section (71b to 71a) to the outer ring is great enough that a defined gas flow volume (V_außen,V_{außen_max}) to the outer ring for a maximum outer burner capacity (P_{außen_max}) and thereby the maximum total burner capacity (P_{gesamt_max}) can be set, while a defined gas flow volume (V_innen, V_{innen_max}) to the inner ring for a maximum inner burner capacity (P_{innen_max}) remains settable.
6. Two-ring burner system (10) according to any of claims 3 to 5, characterized in that the rotor disc valve has two rotating stops (58, 66), each limiting in a rotational direction the possible rotation angle of the rotor disc (60) and thereby define an allowable rotation angle range, wherein the rotating stops (58, 66) are positioned such that a gas supply to the outer ring is settable only when the valve gas outlet (46) to the inner ring is opened, wherein preferably the rotating stops (58, 66) are mechanical stop members and in particular the rotor disc (60) has an outwards protruding outer contour (56) at least in a part of its circumference in the radial direction.
7. Two-ring burner system (10) according to any of the preceding claims, characterized in that it includes an electronically controllable ignition device (32) and an overignition bridge (38), preferably a mechanical overignition bridge (38), wherein the ignition device (32) is arranged on the inner ring burner (36) and the overignition bridge (38) is arranged between the inner ring burner (36) and the outer ring burner (40) such that the outer ring burner (40) can be ignited by means of the inner ring burner (36) and the overignition bridge (38), when the inner ring burner (36) is burning and the gas supply to the outer ring is open, wherein in particular it is the only ignition device (32) of the two-ring burner system (10).
8. Two-ring burner system (10) according to any of the preceding claims, characterized in that it includes a flame sensor (34), wherein the flame sensor (34) is arranged in the flame zone of the inner ring burner (36), and preferably is the only flame sensor (34) of the two-ring burner system (10).
9. Method for controlling a target total burner capacity of a two-ring burner system (10) according to any of claims 1 to 8 in range from zero up to a maximum total burner capacity (P_{gesamt_max}), characterized in that a target total burner capacity greater zero is set by opening the gas supply to the rotor disc valve (50), as a function of the set target total burner capacity at least the valve gas outlet (46) to the inner ring is opened by means of the rotor disc valve (50), a defined gas flow volume (V_innen,V_außen) to the inner ring and to the outer ring is set and corresponding to the set target total burner capacity at least the inner ring burner (36) is ignited, and in that a target total burner capacity of zero is set by blocking the gas supply to the inner ring and to the outer ring.
10. Method according to claim 9 for controlling a two-ring burner system (10) using an electronically controllable ignition device (32) characterized in that, for setting a target total burner capacity in the lowest capacity range of the two-ring burner system (10) below a stable operation of the inner burner capacity (P_{innen_stabil}), the inner ring burner (36) is operated in a timed manner and for that purpose the gas supply to the inner ring is cyclically blocked and opened and in each cycle the inner ring burner (36) is reignited by means of the ignition device (32), wherein igniting is performed, by the control unit (26) correspondingly controlling the ignition device (32) and opening of the gas supply to the inner ring, such that the inner ring burner (36) is alternatingly turned on and off and in the turned-on condition preferably burns with the operation stable inner burner capacity (P_{innen_stabil}), while the gas supply to the outer ring remains closed.
11. Method according to claim 9, characterized in that a target total burner capacity above a maximum inner burner capacity (P_{innen_max}) with an additionally needed outer burner capacity (P_außen) below the operation stable outer burner capacity (P_{außen_stabil}) is set by operating the inner ring burner (36) with its maximum inner burner capacity (P_{innen_max}) in continuous operation and the outer ring burner (40) in a timed manner, wherein for that purpose the outer ring burner (40) is alternatingly turned on and off and in the turned-on condition preferably burns with the operation stable outer burner capacity (P_{außen_stabil}).
12. Method according to claim 10 for controlling a two-ring burner system (10) using an electronically controlled shut-off valve (16), characterized in that the gas supply to the inner ring is cyclically blocked and opened by the control unit (26) controlling the shut-off valve (16) cyclically for opening and closing the gas supply and by means of the rotor disc valve (50) a gas flow volume (V_innen) to the inner ring sufficient for igniting the inner ring burner (36) is set, while the valve gas outlet (48) to the outer ring remains permanently closed.
13. Method according to claim 11 for controlling a two-ring burner system (10) using an electronically controllable ignition device (32) and an overignition bridge (38), characterized in that the outer ring burner (40) is operated in a timed manner by cyclically blocking and opening the gas supply to the outer ring, while the gas supply to the inner ring remains permanently open, preferably constantly, wherein the inner ring burner (36) burns in continuous operation and after each opening of the gas supply to the outer ring the outer ring burner (40) is ignited by means of the inner ring burner (36) and the overignition bridge (38).
14. Method according to claim 13, characterized in that the gas supply to the outer ring is cyclically blocked and opened by the control unit (26) controlling the rotor disc valve (50) such that the gas supply to the outer ring is cyclically opened and closed, while the set gas flow volume (V_innen, V_{innen_max}) to the inner ring remains constant and corresponds to the maximum inner burner capacity (P_{innen_max}) such that the inner ring burner (36) burns with the maximum inner burner capacity (P_{innen_max}).

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