EP0356690B1 - Fuel-fired heat producer - Google Patents

Fuel-fired heat producer Download PDF

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Publication number
EP0356690B1
EP0356690B1 EP89113385A EP89113385A EP0356690B1 EP 0356690 B1 EP0356690 B1 EP 0356690B1 EP 89113385 A EP89113385 A EP 89113385A EP 89113385 A EP89113385 A EP 89113385A EP 0356690 B1 EP0356690 B1 EP 0356690B1
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EP
European Patent Office
Prior art keywords
duct
fuel
flow
line
burner
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP89113385A
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German (de)
French (fr)
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EP0356690A1 (en
Inventor
Karl Dungs
Alfred Sinner
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Karl Dungs GmbH and Co KG
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Karl Dungs GmbH and Co KG
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Priority to AT89113385T priority Critical patent/ATE89657T1/en
Publication of EP0356690A1 publication Critical patent/EP0356690A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/04—Regulating fuel supply conjointly with air supply and with draught
    • F23N1/045—Regulating fuel supply conjointly with air supply and with draught using electrical or electromechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2225/00—Measuring
    • F23N2225/08—Measuring temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2225/00—Measuring
    • F23N2225/08—Measuring temperature
    • F23N2225/20—Measuring temperature entrant temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2233/00—Ventilators
    • F23N2233/02—Ventilators in stacks
    • F23N2233/04—Ventilators in stacks with variable speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/18—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel

Definitions

  • the invention relates to a fuel-fired heat generator with a burner, which has an inlet line for supplying a fuel / air mixture and an outlet line for discharging the exhaust gases, with a main line connected to the inlet line, in which a flow sensor is arranged, with a first fuel line, introduces a fixed-size fuel flow that determines the minimum heating output into the area of the main and inlet lines between the flow sensor and the burner, with at least one secondary line that supplies an air flow that is proportional to its cross-section to the inlet line, with a second fuel line that surrounds the inlet line Area a second fuel flow introduces, which is in the same ratio to the fuel flow of fixed size as the cross section of the branch line to the cross section of the main line, with a fan determining the size of the air flow flowing through the lines and with a delivery rate of the fan depending on the output signal of the main line arranged flow sensor controlling control device.
  • Such a heat generator is known from DE-A-37 00 084. It enables the burner to be operated in a very simple manner with flows of the fuel / air mixture of very different strengths while maintaining the optimum fuel / air ratio. Nevertheless, the controllability of such a heat generator is subject to strict limits because the outflow speed of the fuel / air mixture does not allow for a large variation. If the outflow rate exceeds the ignition rate of the fuel / air mixture, the flame breaks off. If, on the other hand, the outflow speed becomes too low, the flame moves too close to the burner and the burner is inadmissibly overheated due to the reduced cooling capacity due to the reduced flow speed.
  • the invention has for its object to develop a fuel-fired heat generator of the type described in such a way that the heating output can be varied to a much greater extent than in the known heat generators.
  • outlet line and the inlet line are connected to one another by a return line provided with a valve, via which a flow of the exhaust gas that decreases with increasing size can be mixed with the fuel / air mixture flow.
  • the volume of the fuel / air mixture is increased and thereby the outflow speed is increased without the fuel portion of the mixture and thus its heat content being increased or the ratio of fuel to air volume, which is important for optimal combustion, being changed.
  • the ignition speed of the mixture is reduced by the addition of exhaust gases, so that a reduction in the throughput compared to conventionally operated burners is also possible.
  • the double effect of increasing the throughput with a constant calorific value and reducing the ignition speed makes it possible to operate conventional burners far below the minimum power required previously, thereby considerably expanding their control range.
  • a particular advantage of this measure is that it does not require any complicated measures to regulate the composition of the fuel / Lusft mixture or the burner behavior, but the advantages of the known heat generator are retained in full.
  • a valve arrangement which enables the heat generator according to DE-A-37 00 084 to be designed in a particularly simple manner.
  • a similar arrangement can also be used successfully with the heat generator designed according to the invention.
  • a preferred embodiment of the invention provides that the secondary line, the second fuel line and the return line open side by side in the inlet line and the mouths of the three lines a common slide is assigned, which can optionally be brought into a position which simultaneously releases or covers the two mouths of the secondary line and the second fuel line, in which it covers or releases the mouth of the return line in the reverse manner.
  • valve arrangement When using such a valve arrangement, there is no need to install separate valves in the return line, the secondary line and the second fuel line and, if necessary, to connect them to a common drive.
  • special fittings such as T-pieces or the like need not be provided in order to bring the various lines together, since the valve arrangement according to the invention fulfills both the functions of the shut-off valves and the line mergers. Therefore, such a valve arrangement significantly simplifies the structure and reduces the space requirement of fuel-fired heat generators of the type described.
  • valve arrangement enables that in a further embodiment of the invention the orifices of the secondary line, the fuel line and also the return line have cross sections which are proportional to one another and the slide can be able to be brought into intermediate positions in which it releases or covers corresponding portions of the orifice cross sections.
  • outlets of the secondary line and the return line have a rectangular Cross-section, the throughputs of the secondary line and the return line are exactly proportional to the travel of the slide or inversely proportional.
  • either the mouth of the associated fuel line can also have a rectangular cross section, or all holes can have the same diameter when using holes.
  • the main line, the secondary line and the return line open into the inlet line in the region of a chamber having an arcuate wall section and the slide is designed as a rotary slide valve.
  • Rotary slide valve arrangements are particularly easy to manufacture and allow simple storage and also particularly simple drive of the slide valve.
  • the chamber can be formed in a particularly simple manner completely by a cylindrical pot open at one end, in the jacket of which, in addition to the secondary line, the return line also opens, while the inlet line leading to the burner of the heat generator connects to the open end of the pot.
  • the bottom of the chamber also permits the bearing of a shaft which is sealed off from the bottom and to which the slide is fastened inside the chamber and whose end penetrating the bottom is connected to a drive motor.
  • the heat generator shown in the drawing has a burner 1, to which a gas / air mixture is supplied via an inlet line 2.
  • the burner 1 is located within a boiler housing 3, which also encloses the heat exchanger 4 of a heating system.
  • the boiler housing 3 is provided with an outlet line 5 for the exhaust gases, in which there is a fan 7 driven by a motor 6.
  • the inlet line 2 connects the burner 1 to a main line 21, which leads to an air inlet opening 8.
  • a temperature sensor 9 and a flow sensor 10 also protrude into the main line 21.
  • the output signals of these sensors 9, 10 are fed to a control device 11.
  • a first fuel line 13 opens into the main line 21 and supplies gas to the main line as fuel.
  • a gas pressure regulator 14 is located in the fuel line 13 in the flow direction of the gas, so that the main line 21 is supplied with the gas at a predetermined pressure and therefore also as a current of a predetermined strength.
  • a precisely defined one belongs to the given gas flow Airflow.
  • the supply of the correct air flow is monitored by the flow sensor 10, the output signal of which is characteristic of the flow speed of the air in the main line 21.
  • the control device 11 controls depending on the output signals of the temperature sensor 9 and the flow sensor 10, the speed of the motor 6 used to drive the blower 7 in such a way that the flow rate required for supplying the correct amount of air prevails in the main line 21. This ensures in a very simple way that optimal combustion conditions are present for the gas supplied to the burner 1.
  • the main line 21 is connected in parallel to a secondary line 22 which, like the main line 21, opens into the inlet line 2. Similar to the main line 21, the secondary line 22 also has an open end serving as an air inlet opening, and a second fuel line 23 is assigned to it, which branches off from the first fuel line 13 opening into the main line 21. A shut-off valve 24 is located in this second fuel line 23. A shut-off valve 25 is also located in the secondary line 21. The shut-off valves 24 and 25 are connected to a common servomotor 26 which, if necessary, causes the shut-off valves 24, 25 to open and close together .
  • the check valves 24, 25, schematically shown in FIG. 1, for the secondary line 21 and the associated fuel line 23 are integrated into a valve arrangement which has a cylindrical pot 31, in the jacket 32 of which the Air inlet opening 8 leading section 2 of the main line and the secondary line 21 open.
  • both lines have the same rectangular cross-section in the exemplary embodiment shown and are arranged parallel to one another in such a way that they abut one side 27 and 28, respectively.
  • the leading to the burner 1 section 2 'of the main line connects to the open end of the pot 31.
  • the section 2 'of the main line opposite end of the pot 31 is provided with a bottom 33 into which an annular channel 34 is incorporated.
  • the bottom 33 consists of two disk-shaped parts 35, 36, of which the upper part 36 has a groove forming the annular channel 34 on its side facing the lower part 35.
  • the lower disc-shaped part 35 is provided with a screw connection for the gas line 13, so that the gas line 13 opens into the annular channel 34.
  • This ring channel 34 communicates with the interior of the pot 31 via bores 37 and 38, of which the bore 37 is arranged in front of the mouth of section 2 of the main line and has a diameter such that the amount of gas entering the pot via this bore 37 corresponds to the minimum output of the burner, to which the amount of air flowing through the main line 2, 2 'is set by means of the sensors 9, 10.
  • the bores 38 are arranged within the sector 39 delimited by dash-dotted lines in FIG. 2, which is defined by the mouth 40 of the secondary line 21 in the jacket 32 of the pot 31, and next to one another on a circular arc 41, likewise indicated by dash-dotted lines.
  • the bores 38 in their entirety form the fuel line 23 assigned to the secondary line 21.
  • the overall cross section of these bores 38 is so dimensioned that the amount of gas supplied through these holes to the pot 31 to the amount of air supplied via the secondary line 21 is in the same ratio as the amount of gas supplied via the bore 37 to the amount of air supplied through section 2 of the main line.
  • the amount of gas supplied over the entirety of the bores 38 and the amount of air supplied via the secondary line 21 can be dimensioned such that the maximum output of the burner 1 is achieved together with the fuel / air mixture always carried by the main line 2, 2 ' .
  • the section 2 of the main line and the secondary line 21 leading to the air inlet opening 8 have the same cross section, so that the entirety of the bores 38 has the same cross section as the bore 37 and the heating power of the burner 1 is doubled by switching on the secondary line 21 can be.
  • a rotary slide valve 51 serves as shut-off valves 24, 25 for the secondary line 21 and the associated gas line 23, which is fastened on the inner end of a shaft 52 which is rotatably mounted in the base 33 and is sealed against the base in a manner not shown is.
  • This rotary slide valve has at its end a plate 53 which is circular in cross-section and which, in a first end position shown, covers the mouth 40 of the secondary line 21 and thus blocks the secondary line 21.
  • the rotary slide 51 In its section connecting the plate 53 to the shaft 52, the rotary slide 51 has a bore 54 perpendicular to the bottom 33 of the pot, in which a stamp-like insert 55 is mounted displaceably and is loaded by a helical compression spring 56 arranged in the bore 54, so that the latter Insert with the outer surface of his head 57 abuts the bottom 33.
  • the diameter The head 57 is dimensioned such that it completely covers the holes 38 arranged on the circular arc 41 when the plate 53 covers the mouth 40 of the secondary line 21.
  • the rotary valve 51 By pivoting the rotary valve 51 by an angle which is substantially equal to the angle of the sector 39 defined by the mouth 40 of the secondary line 21, the rotary valve 51 can be brought into a second end position, not shown in the drawing, in which the plate 53 the mouth 40 and also the head 57 of the insert 55 clear all the bores 38. If the rotary slide valve occupies a position lying between these two end positions, the mouth 40 of the secondary line 21 is only partially released.
  • the use of tubes with a rectangular cross section has the result that the mouth 40 of the secondary line also has a rectangular cross section and the released section of the secondary line is exactly proportional to the swivel angle of the rotary valve.
  • the use of a number of bores 38 as the mouth of the fuel line assigned to the secondary line 21 ensures that the amount of gas supplied is proportional to the number of bores released and thus in turn to the swivel angle of the rotary valve. It is advisable to gradually adjust the rotary valve so that one additional hole is completely released or covered. If a completely constant change in the heating output is desired, the row of holes could be replaced by a corresponding slot. It would also be possible to partially cover a larger bore similar to the mouth of the secondary line, in which case such a bore would correspond to a circular mouth of the secondary line. With regard to a linear dependency of the power change on the angle of rotation, however, the described embodiment preferred with a rectangular mouth of the secondary line and a correspondingly designed mouth of the associated fuel line.
  • the drive motor 26 for the rotary valve 51 which corresponds to the two shut-off valves 24, 25 according to FIG. 1, is fastened to the base 33 of the pot 31 by means of a holder 61 such that the output shaft 62 of the motor with the rotary valve 51 supporting shaft 52 is aligned and can be connected to this shaft by a plug-in coupling 63.
  • the motor 26 can be a stepping motor, but it can also be a continuously running motor with appropriate control, which preferably has a strong reduction, since the rotary valve 51 may only be adjusted at a relatively low speed. Since the air throughput is determined by the delivery capacity of the blower 7, the change in the line cross sections and thus the fuel supply must not take place faster than the speed at which the blower 7 can react to the changed air requirement.
  • the invention is not restricted to the exemplary embodiment shown, but deviations from it are possible without leaving the scope of the invention.
  • the cylindrical shape of the pot is only important for the pivoting range of the rotary valve, so that even when using a rotary valve, the chamber formed by the pot is also different Can have a cross-sectional shape as long as only the secondary line opens into a cylindrical wall section and there is sufficient space for the rotary valve to pivot away.
  • a linearly movable slide valve can also be used and that it is possible to provide the mouths of the air and gas lines in the same wall section.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Gas Burners (AREA)

Abstract

A heat producer has, in addition to a main pipe (21) which guides a fuel/air mixture of controlled composition, a secondary pipe (22), which can be switched on and off alternatively, with an associated fuel pipe (23). The variation range from minimum to maximum heating output, which is limited by the performance in service of the burner, is to be increased. The outlet pipe (5) and the inlet pipe (2) of the heat producer are interconnected by means of a return pipe (71) which is provided with a valve (72) and via which a flow of exhaust gas, which decreases with an increase in the size of the flow of fuel/air mixture which is supplied to the burner (1), can be added to the latter flow. As a result of this, the minimum output of the burner (1) is greatly reduced because by adding the exhaust air the outflow rate at the burner is increased and at the same time the ignition rate of the fuel/air mixture is reduced, so that stable relationships are maintained at the burner even with a very small flame. <IMAGE>

Description

Die Erfindung betrifft einen brennstoffbefeuerten Wärmeerzeuger mit einem Brenner, der eine Einlaßleitung zum Zuführen eines Brennstoff/Luft-Gemisches und eine Auslaßleitung zum Abführen der Abgase aufweist, mit einer an die Einlaßleitung angeschlossenen Hauptleitung, in der ein Strömunsgsensor angeordnet ist, mit einer ersten Brennstoffleitung, die in den zwischen Strömungssensor und Brenner gelegenen Bereich von Haupt- und Einlaßleitung einen die minimale Heizleistung bestimmenden Brennstoffstrom fester Größe einführt, mit mindestens einer Nebenleitung, die der Einlaßleitung einen ihrem Querschnitt proportionalen Luftstrom zuführt, mit einer zweiten Brennstoffleitung, die in einen die Einlaßleitung umfassenden Bereich einen zweiten Brennstoffstrom einführt, der in dem gleichen Verhältnis zu dem Brennstoffstrom fester Größe steht wie der Querschnitt der Nebenleitung zum Querschnitt der Hauptleitung, mit einem die Größe des die Leitungen durchfließenden Luftstromes bestimmenden Gebläse und mit einer die Förderleistung des Gebläses in Abhängigkeit von dem Ausgangssignal des in der Hauptleitung angeordneten Strömungssensors steuernden Regeleinrichtung.The invention relates to a fuel-fired heat generator with a burner, which has an inlet line for supplying a fuel / air mixture and an outlet line for discharging the exhaust gases, with a main line connected to the inlet line, in which a flow sensor is arranged, with a first fuel line, introduces a fixed-size fuel flow that determines the minimum heating output into the area of the main and inlet lines between the flow sensor and the burner, with at least one secondary line that supplies an air flow that is proportional to its cross-section to the inlet line, with a second fuel line that surrounds the inlet line Area a second fuel flow introduces, which is in the same ratio to the fuel flow of fixed size as the cross section of the branch line to the cross section of the main line, with a fan determining the size of the air flow flowing through the lines and with a delivery rate of the fan depending on the output signal of the main line arranged flow sensor controlling control device.

Ein solcher Wärmeerzeuger ist aus der DE-A-37 00 084 bekannt. Er ermöglicht auf sehr einfache Weise das Betreiben des Brenners mit sehr unterschiedlich starken Strömen des Brennstoff/Luft-Gemisches unter Einhaltung des optimalen Brennstoff/Luft-Verhältnisses. Trotzdem sind der Regelbarkeit eines solchen Wärmeerzeugers enge Grenzen gesetzt, weil die Ausströmgeschwindigkeit des Brennstoff/Luft-Gemisches keine starke Variation zuläßt. Wenn die Ausströmgeschwindigkeit die Zündgeschwindigkeit des Brennstoff/Luft-Gemisches überschreitet, kommt es zu einem Abreißen der Flamme. Wird dagegen die Ausströmgeschwindigkeit zu klein, rückt die Flamme zu nahe an den Brenner heran und es kommt wegen der gleichzeitig aufgrund der verminderten Strömungsgeschwindigkeit verminderten Kühlleistung zu einer unzulässigen Überhitzung des Brenners.Such a heat generator is known from DE-A-37 00 084. It enables the burner to be operated in a very simple manner with flows of the fuel / air mixture of very different strengths while maintaining the optimum fuel / air ratio. Nevertheless, the controllability of such a heat generator is subject to strict limits because the outflow speed of the fuel / air mixture does not allow for a large variation. If the outflow rate exceeds the ignition rate of the fuel / air mixture, the flame breaks off. If, on the other hand, the outflow speed becomes too low, the flame moves too close to the burner and the burner is inadmissibly overheated due to the reduced cooling capacity due to the reduced flow speed.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, einen brennstoffbefeuerten Wärmeerzeuger der eingangs beschriebenen Art derart weiterzubilden, daß die Heizleistung in sehr viel stärkerem Maße variierbar ist als bei den bekannten Wärmeerzeugern.In contrast, the invention has for its object to develop a fuel-fired heat generator of the type described in such a way that the heating output can be varied to a much greater extent than in the known heat generators.

Diese Aufgabe wird nach der Erfindung dadurch gelöst, daß die Auslaßleitung und die Einlaßleitung durch eine mit einem Ventil versehene Rückführleitung miteinander verbunden sind, über die dem Brennstoff/Luft-Gemischstrom eine mit Zunahme seiner Größe abnehmender Strom des Abgases zumischbar ist.This object is achieved according to the invention in that the outlet line and the inlet line are connected to one another by a return line provided with a valve, via which a flow of the exhaust gas that decreases with increasing size can be mixed with the fuel / air mixture flow.

Durch Zumischen von Abgasen wird das Volumen des Brennstoff/Luft-Gemisches vergrößert und dadurch die Ausströmgeschwindigkeit erhöht, ohne daß der Brennstoff-Anteil des Gemisches und damit dessen Wärmeinhalt erhöht oder das für eine optimale Verbrennung wichtige Verhältnis von Brennstoff- zu Luftvolumen verändert würde. Gleichzeitig vermindert sich durch das Beimischen von Abgasen die Zündgeschwindigkeit des Gemisches, so daß auch noch eine Verminderung des Durchsatzes gegenüber herkömmlich betriebenen Brennern möglich ist. Der doppelte Effekt der Erhöhung des Durchsatzes bei gleichbleibendem Heizwert und der Verminderung der Zündgeschwindigkeit macht es möglich, Brenner üblicher Bauart weit unterhalb der bisher erforderlichen Mindestleistung zu betreiben und dadurch ihren Regelbereich erheblich auszudehnen.
Ein besonderer Vorteil dieser Maßnahme besteht darin, daß sie keine komplizierten Maßnahmen zur Regelung der Zusammensetzung des Brennstoff/Lusft-Gemisches oder auch des Brennerverhaltens erfordert, sondern die Vorteile des bekannten Wärmeerzeugers voll erhalten bleiben.By adding exhaust gases, the volume of the fuel / air mixture is increased and thereby the outflow speed is increased without the fuel portion of the mixture and thus its heat content being increased or the ratio of fuel to air volume, which is important for optimal combustion, being changed. At the same time, the ignition speed of the mixture is reduced by the addition of exhaust gases, so that a reduction in the throughput compared to conventionally operated burners is also possible. The double effect of increasing the throughput with a constant calorific value and reducing the ignition speed makes it possible to operate conventional burners far below the minimum power required previously, thereby considerably expanding their control range.
A particular advantage of this measure is that it does not require any complicated measures to regulate the composition of the fuel / Lusft mixture or the burner behavior, but the advantages of the known heat generator are retained in full.

In der deutschen Patentanmeldung DE-A-37 08 573, deren Inhalt als Stand der Technik gilt, ist eine Ventilanordnung beschrieben, die eine besonders einfache Ausbildung des Wärmeerzeugers nach der DE-A-37 00 084 ermöglicht. Eine ähnliche Anordnung läßt sich auch bei dem erfindungsgemäß ausgebildeten Wärmeerzeuger mit Erfolg anwenden. Demgemäß sieht eine bevorzugte Ausgestaltung der Erfindung vor, daß die Nebenleitung, die zweite Brennstoffleitung und die Rückführleitung nebeneinander in die Einlaßleitung münden und den Mündungen der drei Leitungen ein gemeinsamer Schieber zugeordnet ist, der wahlweise in eine die beiden Mündungen der Nebenleitung und der zweiten Brennstoffleitung gleichzeitig freigebende oder abdeckende Stellung bringbar ist, in der er die Mündung der Rückführleitung in umgekehrter Weise abdeckt oder freigibt.In the German patent application DE-A-37 08 573, the content of which is considered to be prior art, a valve arrangement is described which enables the heat generator according to DE-A-37 00 084 to be designed in a particularly simple manner. A similar arrangement can also be used successfully with the heat generator designed according to the invention. Accordingly, a preferred embodiment of the invention provides that the secondary line, the second fuel line and the return line open side by side in the inlet line and the mouths of the three lines a common slide is assigned, which can optionally be brought into a position which simultaneously releases or covers the two mouths of the secondary line and the second fuel line, in which it covers or releases the mouth of the return line in the reverse manner.

Bei Anwendung einer solche Ventilanordnung entfällt die Notwendigkeit, in die Rückführleitung, die Nebenleitung und die zweite Brennstoffleitung gesonderte Ventile einzubauen und ggf. mit einem gemeinsamen Antrieb zu verbinden. Außerdem müssen nicht besondere Armaturen wie T-Stücke o. dgl. vorgesehen werden, um die verschiedenen Leitungen zusammenzuführen, da die erfindungsgemäße Ventilanordnung sowohl die Funktionen der Absperrventile als auch der Leitungs-Zusammenführungen erfüllt. Daher wird durch eine solche Ventilanordnung eine bedeutende Vereinfachung des Aufbaus und eine Verminderung des Platzbedarfes von brennstoffbefeuerten Wärmeerzeugern der beschriebenen Art erzielt.When using such a valve arrangement, there is no need to install separate valves in the return line, the secondary line and the second fuel line and, if necessary, to connect them to a common drive. In addition, special fittings such as T-pieces or the like need not be provided in order to bring the various lines together, since the valve arrangement according to the invention fulfills both the functions of the shut-off valves and the line mergers. Therefore, such a valve arrangement significantly simplifies the structure and reduces the space requirement of fuel-fired heat generators of the type described.

Die Anwendung einer solchen Ventilanordnung ist dann von besonderem Vorteil, wenn nicht nur eine sprunghafte Erhöhung der Heizleistung durch vollständiges Zuschalten der Nebenleitung und der zweiten Brennstoffleitung mit entsprechender vollständiger Sperrung der Rückführleitung gewünscht wird, sondern eine mehr oder weniger stetige Änderung der Heizleistung, weil es die Ventilanordnung ermöglicht, daß in weiterer Ausgestaltung der Erfindung die Mündungen der Nebenleitung, der Brennstoffleitung und auch der Rückführleitung zueinander proportionale Querschnitte haben und der Schieber in Zwischenstellungen bringbar sein kann, in denen er einander entsprechende Anteile der Mündungsquerschnitte freigibt bzw. abdeckt. Haben die Mündungen der Nebenleitung und der Rückführleitung einen rechteckigen Querschnitt, so sind die Durchsätze der Nebenleitung und der Rückführleitung dem Stellweg des Schiebers genau proportional bzw. umgekehrt proportional. Dabei kann dann entweder die Mündung der zugeordneten Brennstoffleitung ebenfalls einen rechteckigen Querschnitt haben oder es können bei der Verwendung von Bohrungen alle Bohrungen den gleichen Durchmesser haben.The use of such a valve arrangement is particularly advantageous if not only a sudden increase in heating power by completely switching on the secondary line and the second fuel line with a corresponding complete blocking of the return line is desired, but a more or less constant change in the heating power because it is the Valve arrangement enables that in a further embodiment of the invention the orifices of the secondary line, the fuel line and also the return line have cross sections which are proportional to one another and the slide can be able to be brought into intermediate positions in which it releases or covers corresponding portions of the orifice cross sections. Do the outlets of the secondary line and the return line have a rectangular Cross-section, the throughputs of the secondary line and the return line are exactly proportional to the travel of the slide or inversely proportional. In this case, either the mouth of the associated fuel line can also have a rectangular cross section, or all holes can have the same diameter when using holes.

Für den mechanischen Aufbau der Ventilanordnung eines solchen Wärmeerzeugers ist es von besonderem Vorteil, wenn die Hauptleitung, die Nebenleitung und die Rückführleitung im Bereich einer kreisbogenförmigen Wandabschnitt aufweisenden Kammer in die Einlaßleitung münden und der Schieber als Drehschieber ausgebildet ist. Drehschieberanordnungen sind besonders leicht herstellbar und gestatten eine einfache Lagerung sowie auch einen besonders einfachen Antrieb des Schiebers. Dabei kann die Kammer in besonders einfacher Weise vollständig von einem zylindrischen, an einem Ende offenen Topf gebildet werden, in dessen Mantel außer der Nebenleitung auch die Rückführleitung mündet, während die zum Brenner des Wärmeerzeugers führende Einlaßleitung sich an das offene Ende des Topfes anschließt. Bei dieser Ausführungsform der Erfindung gestattet der Boden der Kammer zugleich das Lagern einer gegenüber dem Boden abgedichteten Welle, an der im Inneren der Kammer der Schieber befestigt ist und deren den Boden durchdringendes Ende mit einem Antriebsmotor verbunden ist.For the mechanical construction of the valve arrangement of such a heat generator, it is particularly advantageous if the main line, the secondary line and the return line open into the inlet line in the region of a chamber having an arcuate wall section and the slide is designed as a rotary slide valve. Rotary slide valve arrangements are particularly easy to manufacture and allow simple storage and also particularly simple drive of the slide valve. The chamber can be formed in a particularly simple manner completely by a cylindrical pot open at one end, in the jacket of which, in addition to the secondary line, the return line also opens, while the inlet line leading to the burner of the heat generator connects to the open end of the pot. In this embodiment of the invention, the bottom of the chamber also permits the bearing of a shaft which is sealed off from the bottom and to which the slide is fastened inside the chamber and whose end penetrating the bottom is connected to a drive motor.

Die Erfindung wird im folgenden anhand des in der Zeichnung dargestellten Ausführungsbeispieles näher beschrieben und erläutert. Die der Beschreibung und der Zeichnung zu entnehmenden Merkmale können bei anderen Ausführungsformen der Erfindung einzeln für sich oder zu mehreren in beliebiger Kombination Anwendung finden. Es zeigen

Fig. 1
eine schematische Darstellung eines Wärmeerzeugers nach der Erfindung in schematischer Darstellung,
Fig. 2
einen Schnitt längs der Linie II-II durch eine Ausführungsform der in Fig. 1 nur schematisch dargestellte Ventilanordnung des Wärmeerzeugers und
Fig. 3
einen Schnitt längs der Linie III-III durch die Ventilanordnung nach Fig. 2.
The invention is described and explained in more detail below with reference to the embodiment shown in the drawing. The features to be gathered from the description and the drawing can be used in other embodiments of the invention individually or in combination in any combination. Show it
Fig. 1
1 shows a schematic illustration of a heat generator according to the invention,
Fig. 2
a section along the line II-II through an embodiment of the valve arrangement of the heat generator shown only schematically in Fig. 1 and
Fig. 3
a section along the line III-III through the valve assembly of FIG. 2nd

Der in der Zeichnung dargestellte Wärmeerzeuger weist einen Brenner 1 auf, dem über eine Einlaßleitung 2 ein Gas/Luft-Gemisch zugeführt wird. Der Brenner 1 befindet sich innerhalb eines Kesselgehäuses 3, das auch den Wärmeaustauscher 4 einer Heizungsanlage umschließt. Das Kesselgehäuse 3 ist mit einem Auslaßleitung 5 für die Abgase versehen, in dem sich ein von einem Motor 6 angetriebenes Gebläse 7 befindet.The heat generator shown in the drawing has a burner 1, to which a gas / air mixture is supplied via an inlet line 2. The burner 1 is located within a boiler housing 3, which also encloses the heat exchanger 4 of a heating system. The boiler housing 3 is provided with an outlet line 5 for the exhaust gases, in which there is a fan 7 driven by a motor 6.

Die Einlaßleitung 2 verbindet den Brenner 1 mit einer Hauptleitung 21, die zu einer Lufteintrittsöffnung 8 führt. In die Hauptleitung 21 ragen weiterhin ein Temperatursensor 9 und ein Strömungssensor 10 hinein. Die Ausgangssignale dieser Sensoren 9, 10 werden einer Regeleinrichtung 11 zugeführt. Im Bereich zwischen den Sensoren 9, 10 und dem Brenner 1 mündet in die Hauptleitung 21 eine erste Brennstoffleitung 13, die der Hauptleitung als Brennstoff Gas zuführt. In der Brennstoffleitung 13 befinden sich in der Strömungsrichtung des Gases hintereinander ein Gasdruckregler 14, so daß der Hauptleitung 21 das Gas mit vorgegebenem Druck und daher auch als Strom mit vorgegebener Stärke zugeführt wird. Um optimale Verbrennungsverhältnisse zu haben, gehört zu dem vorgegebenen Gasstrom ein genau bestimmter Luftstrom. Die Zufuhr des richtigen Luftstromes wird durch den Strömungssensor 10 überwacht, dessen Ausgangssignal für die Strömungsgeschwindigkeit der Luft in der Hauptleitung 21 charakteristisch ist. Die Regeleinrichtung 11 steuert in Abhängigkeit von den Ausgangssignalen des Temperatursensors 9 und des Strömungssensors 10 die Drehzahl des zum Antrieb des Gebläses 7 dienenden Motors 6 in solcher Weise, daß in der Hauptleitung 21 die zur Zufuhr der richtigen Luftmenge erforderliche Strömungsgeschwindigkeit herrscht. Damit ist auf sehr einfache Weise gewährleistet, daß optimale Verbrennungsbedingungen für das dem Brenner 1 zugeführte Gas vorliegen.The inlet line 2 connects the burner 1 to a main line 21, which leads to an air inlet opening 8. A temperature sensor 9 and a flow sensor 10 also protrude into the main line 21. The output signals of these sensors 9, 10 are fed to a control device 11. In the area between the sensors 9, 10 and the burner 1, a first fuel line 13 opens into the main line 21 and supplies gas to the main line as fuel. A gas pressure regulator 14 is located in the fuel line 13 in the flow direction of the gas, so that the main line 21 is supplied with the gas at a predetermined pressure and therefore also as a current of a predetermined strength. In order to have optimal combustion conditions, a precisely defined one belongs to the given gas flow Airflow. The supply of the correct air flow is monitored by the flow sensor 10, the output signal of which is characteristic of the flow speed of the air in the main line 21. The control device 11 controls depending on the output signals of the temperature sensor 9 and the flow sensor 10, the speed of the motor 6 used to drive the blower 7 in such a way that the flow rate required for supplying the correct amount of air prevails in the main line 21. This ensures in a very simple way that optimal combustion conditions are present for the gas supplied to the burner 1.

Der Hauptleitung 21 ist eine Nebenleitung 22 parallel geschaltet, die ebenso wie die Hauptleitung 21 in die Einlaßleitung 2 mündet. Ähnlich wie die Hauptleitung 21 hat auch die Nebenleitung 22 ein als Lufteintrittsöffnung dienendes, offenes Ende, und es ist ihr eine zweite Brennstoffleitung 23 zugeordnet, die von der in die Hauptleitung 21 mündenden ersten Brennstoffleitung 13 abzweigt. In dieser zweiten Brennstoffleitung 23 befindet sich ein Absperrventil 24. Auch in der Nebenleitung 21 befindet sich ein Absperrventil 25. Die Absperrventile 24 und 25 sind mit einem gemeinsamen Stellmotor 26 verbunden, der bei Bedarf das gemeinsame Öffnen bzw. Schließen der Absperrventile 24, 25 bewirkt.The main line 21 is connected in parallel to a secondary line 22 which, like the main line 21, opens into the inlet line 2. Similar to the main line 21, the secondary line 22 also has an open end serving as an air inlet opening, and a second fuel line 23 is assigned to it, which branches off from the first fuel line 13 opening into the main line 21. A shut-off valve 24 is located in this second fuel line 23. A shut-off valve 25 is also located in the secondary line 21. The shut-off valves 24 and 25 are connected to a common servomotor 26 which, if necessary, causes the shut-off valves 24, 25 to open and close together .

Wie aus den Fig. 2 und 3 näher ersichtlich, sind die in Fig. 1 schematisch dargestellten Sperrventile 24, 25 für die Nebenleitung 21 und die zugeordnete Brennstoffleitung 23 in eine Ventilanordnung integriert, die einen zylindrischen Topf 31 aufweist, in dessen Mantel 32 der zur Lufteintrittsöffnung 8 führende Abschnitt 2 der Hauptleitung und die Nebenleitung 21 münden. Wie ersichtlich, haben beide Leitungen bei dem dargestellten Ausführungsbeispiel den gleichen rechteckigen Querschnitt und sind derart parallel zueinander angeordnet, daß sie mit einer Seite 27 bzw. 28 aneinander anliegen. Der zum Brenner 1 führende Abschnitt 2′ der Hauptleitung schließt an das offene Ende des Topfes 31 an.As can be seen from FIGS. 2 and 3 in more detail, the check valves 24, 25, schematically shown in FIG. 1, for the secondary line 21 and the associated fuel line 23 are integrated into a valve arrangement which has a cylindrical pot 31, in the jacket 32 of which the Air inlet opening 8 leading section 2 of the main line and the secondary line 21 open. As can be seen, both lines have the same rectangular cross-section in the exemplary embodiment shown and are arranged parallel to one another in such a way that they abut one side 27 and 28, respectively. The leading to the burner 1 section 2 'of the main line connects to the open end of the pot 31.

Das dem Abschnitt 2′ der Hauptleitung gegenüberliegende Ende des Topfes 31 ist mit einem Boden 33 versehen, in den ein Ringkanal 34 eingearbeitet ist. Zu diesem Zweck besteht der Boden 33 aus zwei scheibenförmigen Teilen 35, 36, von denen der obere Teil 36 an seiner dem unteren Teil 35 zugewandten Seite eine den Ringkanal 34 bildende Nut aufweist. Der untere scheibenförmige Teil 35 ist mit einem Schraubanschluß für die Gasleitung 13 versehen, so daß die Gasleitung 13 in den Ringkanal 34 mündet. Dieser Ringkanal 34 steht mit dem Innenraum des Topfes 31 über Bohrungen 37 und 38 in Verbindung, von denen die Bohrung 37 vor der Mündung des Abschnittes 2 der Hauptleitung angeordnet ist und einen solchen Durchmesser hat, daß die über diese Bohrung 37 in den Topf eintretende Gasmenge der Mindestleistung des Brenners entspricht, auf welche die die Hauptleitung 2, 2′ durchströmende Luftmenge mittels der Sensoren 9, 10 eingestellt wird.The section 2 'of the main line opposite end of the pot 31 is provided with a bottom 33 into which an annular channel 34 is incorporated. For this purpose, the bottom 33 consists of two disk-shaped parts 35, 36, of which the upper part 36 has a groove forming the annular channel 34 on its side facing the lower part 35. The lower disc-shaped part 35 is provided with a screw connection for the gas line 13, so that the gas line 13 opens into the annular channel 34. This ring channel 34 communicates with the interior of the pot 31 via bores 37 and 38, of which the bore 37 is arranged in front of the mouth of section 2 of the main line and has a diameter such that the amount of gas entering the pot via this bore 37 corresponds to the minimum output of the burner, to which the amount of air flowing through the main line 2, 2 'is set by means of the sensors 9, 10.

Die Bohrungen 38 sind innerhalb des in Fig. 2 durch strichpunktierte Linien begrenzten Sektors 39, der durch die Mündung 40 der Nebenleitung 21 im Mantel 32 des Topfes 31 definiert wird, und nebeneinander auf einem ebenfalls strichpunktiert angedeuteten Kreisbogen 41 angeordnet. Die Bohrungen 38 bilden in ihrer Gesamtheit die der Nebenleitung 21 zugeordnete Brennstoffleitung 23. Der Gesamtquerschnitt dieser Bohrungen 38 ist so bemessen, daß die über diese Bohrungen dem Topf 31 zugeführte Gasmenge zu der über die Nebenleitung 21 zugeführten Luftmenge in dem gleichen Verhältnis steht wie die über die Bohrung 37 zugeführte Gasmenge zu der durch den Abschnitt 2 der Hauptleitung zugeführten Luftmenge. Dabei können die über die Gesamtheit der Bohrungen 38 zugeführte Gasmenge und die über die Nebenleitung 21 zugeführte, entsprechende Luftmenge so bemessen sein, daß zusammen mit dem von der Hauptleitung 2, 2′ stets geführten Brennstoff/Luft-Gemisch die Maximalleistung des Brenners 1 erreicht wird. Bei dem dargestellten Ausführungsbeispiel haben der zur Lufteintrittsöffnung 8 führende Abschnitt 2 der Hauptleitung und die Nebenleitung 21 den gleichen Querschnitt, so daß auch die Gesamtheit der Bohrungen 38 den gleichen Querschnitt hat wie die Bohrung 37 und die Heizleistung des Brenners 1 durch Zuschalten der Nebenleitung 21 verdoppelt werden kann.The bores 38 are arranged within the sector 39 delimited by dash-dotted lines in FIG. 2, which is defined by the mouth 40 of the secondary line 21 in the jacket 32 of the pot 31, and next to one another on a circular arc 41, likewise indicated by dash-dotted lines. The bores 38 in their entirety form the fuel line 23 assigned to the secondary line 21. The overall cross section of these bores 38 is so dimensioned that the amount of gas supplied through these holes to the pot 31 to the amount of air supplied via the secondary line 21 is in the same ratio as the amount of gas supplied via the bore 37 to the amount of air supplied through section 2 of the main line. The amount of gas supplied over the entirety of the bores 38 and the amount of air supplied via the secondary line 21 can be dimensioned such that the maximum output of the burner 1 is achieved together with the fuel / air mixture always carried by the main line 2, 2 ' . In the illustrated embodiment, the section 2 of the main line and the secondary line 21 leading to the air inlet opening 8 have the same cross section, so that the entirety of the bores 38 has the same cross section as the bore 37 and the heating power of the burner 1 is doubled by switching on the secondary line 21 can be.

Als Absperrventile 24, 25 für die Nebenleitung 21 und die zugeordnete Gasleitung 23 dient bei dem dargestellten Ausführungsbeispiel der Ventilanordnung ein Drehschieber 51, der auf dem inneren Ende einer in dem Boden 33 drehbar gelagerten und in nicht näher dargestellter Weise gegenüber dem Boden abgedichteten Welle 52 befestigt ist. Dieser Drehschieber weist an seinem Ende eine im Querschnitt kreisbogenförmige Platte 53 auf, die in einer dargestellten ersten Endstellung die Mündung 40 der Nebenleitung 21 abdeckt und damit die Nebenleitung 21 absperrt. In seinem die Platte 53 mit der Welle 52 verbindenden Abschnitt weist der Drehschieber 51 eine zum Boden 33 des Topfes senkreche Bohrung 54 auf, in der ein stempelartiger Einsatz 55 verschiebbar gelagert und durch eine in der Bohrung 54 angeordnete Schraubendruckfeder 56 belastet ist, so daß dieser Einsatz mit der Außenfläche seines Kopfes 57 am Boden 33 anliegt. Der Durchmesser des Kopfes 57 ist so bemessen, daß er die auf dem Kreisbogen 41 angeordneten Bohrungen 38 vollständig abdeckt, wenn die Platte 53 die Mündung 40 der Nebenleitung 21 abdeckt. Durch Verschwenken des Drehschiebers 51 um einen Winkel, der im wesentlichen gleich dem Winkel des durch die Mündung 40 der Nebenleitung 21 definierten Sektors 39 gleich ist, kann der Drehschieber 51 in eine in der Zeichnung nicht dargestellte, zweite Endstellung gebracht werden, in welcher die Platte 53 die Mündung 40 und ebenso auch der Kopf 57 des Einsatzes 55 sämtliche Bohrungen 38 freigibt. Nimmt der Drehschieber eine zwischen diesen beiden Endstellungen liegende Stellung ein, wird die Mündung 40 der Nebenleitung 21 nur partiell freigegeben. Die Verwendung von Rohren mit rechteckigem Querschnitt hat zur Folge, daß auch die Mündung 40 der Nebenleitung einen rechteckigen Querschnitt hat und der freigegebene Abschnitt der Nebenleitung dem Schwenkwinkel des Drehschiebers genau proportional ist. Ebenso ist durch die Anwendung einer Anzahl von Bohrungen 38 als Mündung der der Nebenleitung 21 zugeordneten Brennstoffleitung gewährleistet, daß die zugeführte Gasmenge der Anzahl der freigegebenen Bohrungen und damit wiederum dem Schwenkwinkel des Drehschiebers proportional ist. Dabei ist es zweckmäßig, den Drehschieber schrittweise so zu verstellen, daß jeweils eine weitere Bohrung vollständig freigegeben oder abgedeckt wird. Wenn eine völlig stetige Veränderung der Heizleistung gewünscht wird, könnte die Reihe von Bohrungen durch einen entsprechenden Schlitz ersetzt werden. Ebenso wäre es möglich, eine größere Bohrung ähnlich wie die Mündung der Nebenleitung partiell abzudecken, wobei dann eine solche Bohrung einer kreisförmigen Mündung der Nebenleitung entsprechen würde. Im Hinblick auf eine lineare Abhängigkeit der Leistungsänderung vom Drehwinkel wird jedoch die beschriebene Ausführungsform mit einer rechteckigen Mündung der Nebenleitung und einer entsprechend gestalteten Mündung der zugeordneten Brennstoffleitung bevorzugt.In the illustrated embodiment of the valve arrangement, a rotary slide valve 51 serves as shut-off valves 24, 25 for the secondary line 21 and the associated gas line 23, which is fastened on the inner end of a shaft 52 which is rotatably mounted in the base 33 and is sealed against the base in a manner not shown is. This rotary slide valve has at its end a plate 53 which is circular in cross-section and which, in a first end position shown, covers the mouth 40 of the secondary line 21 and thus blocks the secondary line 21. In its section connecting the plate 53 to the shaft 52, the rotary slide 51 has a bore 54 perpendicular to the bottom 33 of the pot, in which a stamp-like insert 55 is mounted displaceably and is loaded by a helical compression spring 56 arranged in the bore 54, so that the latter Insert with the outer surface of his head 57 abuts the bottom 33. The diameter The head 57 is dimensioned such that it completely covers the holes 38 arranged on the circular arc 41 when the plate 53 covers the mouth 40 of the secondary line 21. By pivoting the rotary valve 51 by an angle which is substantially equal to the angle of the sector 39 defined by the mouth 40 of the secondary line 21, the rotary valve 51 can be brought into a second end position, not shown in the drawing, in which the plate 53 the mouth 40 and also the head 57 of the insert 55 clear all the bores 38. If the rotary slide valve occupies a position lying between these two end positions, the mouth 40 of the secondary line 21 is only partially released. The use of tubes with a rectangular cross section has the result that the mouth 40 of the secondary line also has a rectangular cross section and the released section of the secondary line is exactly proportional to the swivel angle of the rotary valve. Likewise, the use of a number of bores 38 as the mouth of the fuel line assigned to the secondary line 21 ensures that the amount of gas supplied is proportional to the number of bores released and thus in turn to the swivel angle of the rotary valve. It is advisable to gradually adjust the rotary valve so that one additional hole is completely released or covered. If a completely constant change in the heating output is desired, the row of holes could be replaced by a corresponding slot. It would also be possible to partially cover a larger bore similar to the mouth of the secondary line, in which case such a bore would correspond to a circular mouth of the secondary line. With regard to a linear dependency of the power change on the angle of rotation, however, the described embodiment preferred with a rectangular mouth of the secondary line and a correspondingly designed mouth of the associated fuel line.

Der besondere Vorteil der Erfindung besteht darin, daß durch die Verwendung eines gemeinsamen Schiebers zum Freigeben oder Absperren der Nebenleitung sowie der zugeordneten Brennstoffleitung keinerlei Probleme für den motorischen Antrieb der Ventilanordnung bestehen. Bei dem dargestellten Ausführungsbeispiel ist der Antriebsmotor 26 für den Drehschieber 51, der den beiden Absperrventilen 24, 25 nach Fig. 1 entspricht, mittels einer Halterung 61 an dem Boden 33 des Topfes 31 derart befestigt, daß die Abtriebswelle 62 des Motors mit der den Drehschieber 51 tragenden Welle 52 fluchtet und mit dieser Welle durch eine Steckkupplung 63 verbunden werden kann. Bei dem Motor 26 kann es sich um einen Schrittschaltmotor, aber auch um einen kontinuierlich laufenden Motor mit entsprechender Steuerung handeln, der vorzugsweise eine starke Untersetzung aufweist, da der Drehschieber 51 nur mit relativ geringer Geschwindigkeit verstellt werden darf. Da der Luftdurchsatz durch die Förderleistung des Gebläses 7 bestimmt wird, darf die Veränderung der Leitunsquerschnitte und damit der Brennstoffzufuhr nicht schneller erfolgen als mit der Geschwindigkeit, mit der das Gebläse 7 auf den veränderten Luftbedarf reagieren kann.The particular advantage of the invention is that by using a common slide to release or shut off the secondary line and the associated fuel line there are no problems for the motor drive of the valve arrangement. In the illustrated embodiment, the drive motor 26 for the rotary valve 51, which corresponds to the two shut-off valves 24, 25 according to FIG. 1, is fastened to the base 33 of the pot 31 by means of a holder 61 such that the output shaft 62 of the motor with the rotary valve 51 supporting shaft 52 is aligned and can be connected to this shaft by a plug-in coupling 63. The motor 26 can be a stepping motor, but it can also be a continuously running motor with appropriate control, which preferably has a strong reduction, since the rotary valve 51 may only be adjusted at a relatively low speed. Since the air throughput is determined by the delivery capacity of the blower 7, the change in the line cross sections and thus the fuel supply must not take place faster than the speed at which the blower 7 can react to the changed air requirement.

Es versteht sich, daß die Erfindung nicht auf das dargestellte Ausführungsbeispiel beschränkt ist, sondern Abweichungen davon möglich sind, ohne den Rahmen der Erfindung zu verlassen. So ist beispielsweise ohne weiteres ersichtlich, daß die zylindrische Form des Topfes nur für den Schwenkbereich des Drehschiebers von Bedeutung ist, so daß selbst bei Verwendung eines Drehschiebers die von dem Topf gebildete Kammer auch eine andere Querschnittsform haben kann, solange nur die Nebenleitung in einen zylindrischen Wandabschnitt mündet und ausreichend Raum zum Wegschwenken des Drehschiebers vorhanden ist. Weiterhin ist ersichtlich, daß anstelle eines Drehschiebers auch ein geradlinig beweglicher Schieber Verwendung finden kann und daß es möglich ist, die Mündungen der Luft- und der Gasleitung in dem gleichen Wandabschnitt vorzusehen. Dabei besteht sowohl die Möglichkeit, diese Mündungen mit ausreichendem Abstand in der Bewegungsrichtung des Schiebers hintereinander als auch an der gleichen Wand senkrecht zur Bewegungsrichtung des Schiebers nebeneinander anzuordnen. Es sei auch erwähnt, daß bei Wärmeerzeugern, die eine solche Ventilanordnung aufweisen, das Gebläse an einem für die Hauptleitung und die Nebenleitung gemeinsamen Lufteinlaß angeordnet sein könnte. Angesichts all dieser vielen Möglichkeiten wird jedoch die dargestellte Ausführungsform der Ventilanordnung wegen ihrer besonders einfachen und kompakten Bauweise als optimale Verwirklichung der Erfindung angesehen.It goes without saying that the invention is not restricted to the exemplary embodiment shown, but deviations from it are possible without leaving the scope of the invention. For example, it is readily apparent that the cylindrical shape of the pot is only important for the pivoting range of the rotary valve, so that even when using a rotary valve, the chamber formed by the pot is also different Can have a cross-sectional shape as long as only the secondary line opens into a cylindrical wall section and there is sufficient space for the rotary valve to pivot away. Furthermore, it can be seen that instead of a rotary slide valve, a linearly movable slide valve can also be used and that it is possible to provide the mouths of the air and gas lines in the same wall section. There is the possibility of arranging these orifices one behind the other at a sufficient distance in the direction of movement of the slide and also on the same wall perpendicular to the direction of movement of the slide. It should also be mentioned that in the case of heat generators which have such a valve arrangement, the fan could be arranged at an air inlet common to the main line and the secondary line. In view of all these many possibilities, however, the embodiment of the valve arrangement shown is regarded as the optimal implementation of the invention because of its particularly simple and compact design.

Claims (6)

  1. Fuel-fed heat producer with a burner (1) having an inlet duct (2) for the supply of a fuel/air mixture and an outlet duct (5) for the discharge of the burnt gases, with a main duct (21) for air which is connected to the inlet duct and in which a flow sensor is arranged, with a first fuel duct (13) which feeds into the area of the main duct and the inlet duct between the flow sensor and the burner a fuel flow of a fixed value determining the minimal heating power, with at least one side duct (22) for air which supplies the inlet duct with an air flow proportional to its cross-section, with a second fuel duct (23) which feeds into an area comprising the inlet duct a second fuel flow which has the same ratio to the fuel flow of the fixed value as the cross-section of the side duct to the cross-section of the main duct, with a fan (7) determining the value of the air flow flowing through the ducts and with a control unit (11) regulating the capacity of the fan dependent on the output signal of the flow sensor arranged in the main duct,
    characterized in that
    the outlet duct (5) and the inlet duct (2) are connected with one another by a return duct (71) provided with a valve (72), via said return duct a flow of the burnt gases decreasing as the fuel/air mixture flow increases can be mixed into the fuel/air mixture.
  2. Heat producer according to claim 1, characterized in that the side duct (22), the second fuel duct (23) and the return duct (71) end side-by-side into the inlet duct (2) and the muzzles (40, 38, 73) of the three ducts are related to a common slide valve (51) which can selectably be brought into a position which simultaneously releases or covers the two muzzles (40, 38) of the side duct (22) and of the second fuel duct (23), in said position it covers or releases the muzzle (73) of the return duct (71) in the reverse way.
  3. Heat producer according to claim 2, characterized in that the muzzles (46, 73) of the side duct (21) and of the return duct (71) have rectangular cross-section.
  4. Heat producer according to claim 2 or 3, characterized in that the main duct (21), the side duct (22) and the return duct (71) end into the inlet duct (2) in the area of a chamber (31) having a circular wall section (32) and the slide valve (51) is provided as a rotary slide.
  5. Heat producer according to claim 4, characterized in that the chamber (31) is formed by a cylindrical pot open on one end, in the shell (32) of said pot the return duct (71), apart from the side duct (21) also ends, whereas the inlet duct (2) leading to the burner (1) of the heat producer adjoins the open end of the pot.
  6. Heat producer according to claim 5, characterized in that the slide valve (51) is fastened to a shaft (52) which is supported in the bottom (33) of the chamber (31) and is sealed against the bottom, said shaft is linked with a driving motor (26) at the outside of the bottom (33).
EP89113385A 1988-09-01 1989-07-21 Fuel-fired heat producer Expired - Lifetime EP0356690B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89113385T ATE89657T1 (en) 1988-09-01 1989-07-21 FUEL-FIRED HEAT GENERATOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3829664A DE3829664C1 (en) 1988-09-01 1988-09-01
DE3829664 1988-09-01

Publications (2)

Publication Number Publication Date
EP0356690A1 EP0356690A1 (en) 1990-03-07
EP0356690B1 true EP0356690B1 (en) 1993-05-19

Family

ID=6362054

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89113385A Expired - Lifetime EP0356690B1 (en) 1988-09-01 1989-07-21 Fuel-fired heat producer

Country Status (3)

Country Link
EP (1) EP0356690B1 (en)
AT (1) ATE89657T1 (en)
DE (1) DE3829664C1 (en)

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US8839815B2 (en) 2011-12-15 2014-09-23 Honeywell International Inc. Gas valve with electronic cycle counter
US8899264B2 (en) 2011-12-15 2014-12-02 Honeywell International Inc. Gas valve with electronic proof of closure system
US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US9234661B2 (en) 2012-09-15 2016-01-12 Honeywell International Inc. Burner control system
US9557059B2 (en) 2011-12-15 2017-01-31 Honeywell International Inc Gas valve with communication link
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism
US10215291B2 (en) 2013-10-29 2019-02-26 Honeywell International Inc. Regulating device

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DE4120831A1 (en) * 1991-06-24 1993-01-07 Asea Brown Boveri Gas turbine combustion chamber operating method - involves by=passing part of air into pre-mixing zone at part-load operation
DE19502905C2 (en) * 1995-01-31 1997-12-18 Stiebel Eltron Gmbh & Co Kg Gas burner device with exhaust gas recirculation
DE19711140A1 (en) * 1997-03-18 1998-06-04 Bosch Gmbh Robert Method for operating burner with mixture of fuel and air
EP0908670B1 (en) * 1997-10-06 2004-07-28 Robert Bosch Gmbh Device for operating an atmospheric gas burner
DE19857239C2 (en) * 1998-12-11 2000-11-23 Honeywell Bv Control procedures for gas burners
DE19947565A1 (en) * 1999-10-02 2001-04-05 Ruhrgas Ag Two-fluid mixer for any gas or liquid combination, includes polygon tube plane with offset, inclined, parallel and divergent walls, complemented by jet slots and impact baffles, producing uniform mixture across entire cross section
DE19920113A1 (en) * 1999-05-03 2000-11-09 Kromschroeder Ag G Method and device for heating up a furnace zone containing contaminated waste gases with residual oxygen content applies hot gases generated by fuel combustion to the waste gases
EP1052365B1 (en) 1999-05-11 2004-12-29 Hunter Douglas Industries B.V. Operating mechanism for a venetian blind
US9835265B2 (en) 2011-12-15 2017-12-05 Honeywell International Inc. Valve with actuator diagnostics
US9851103B2 (en) 2011-12-15 2017-12-26 Honeywell International Inc. Gas valve with overpressure diagnostics
US9846440B2 (en) 2011-12-15 2017-12-19 Honeywell International Inc. Valve controller configured to estimate fuel comsumption
US10422531B2 (en) 2012-09-15 2019-09-24 Honeywell International Inc. System and approach for controlling a combustion chamber
US9841122B2 (en) 2014-09-09 2017-12-12 Honeywell International Inc. Gas valve with electronic valve proving system
US9645584B2 (en) 2014-09-17 2017-05-09 Honeywell International Inc. Gas valve with electronic health monitoring
US10503181B2 (en) 2016-01-13 2019-12-10 Honeywell International Inc. Pressure regulator
US10564062B2 (en) 2016-10-19 2020-02-18 Honeywell International Inc. Human-machine interface for gas valve
US11073281B2 (en) 2017-12-29 2021-07-27 Honeywell International Inc. Closed-loop programming and control of a combustion appliance
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DE685899C (en) * 1935-04-29 1939-12-28 Rateau Soc Control device for exhaust gas turbine fan for the combustion air of steam generators
DE3114866A1 (en) * 1981-04-13 1982-11-04 Honeywell B.V., Amsterdam GAS-FIRED WATER OR AIR HEATER
EP0109620A3 (en) * 1982-11-18 1985-06-26 Joh. Vaillant GmbH u. Co. Fuel heated heat source
DE3708573A1 (en) * 1987-03-17 1988-09-29 Dungs Karl Gmbh & Co VALVE ARRANGEMENT

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Publication number Priority date Publication date Assignee Title
US8839815B2 (en) 2011-12-15 2014-09-23 Honeywell International Inc. Gas valve with electronic cycle counter
US8899264B2 (en) 2011-12-15 2014-12-02 Honeywell International Inc. Gas valve with electronic proof of closure system
US8905063B2 (en) 2011-12-15 2014-12-09 Honeywell International Inc. Gas valve with fuel rate monitor
US8947242B2 (en) 2011-12-15 2015-02-03 Honeywell International Inc. Gas valve with valve leakage test
US9074770B2 (en) 2011-12-15 2015-07-07 Honeywell International Inc. Gas valve with electronic valve proving system
US9557059B2 (en) 2011-12-15 2017-01-31 Honeywell International Inc Gas valve with communication link
US9995486B2 (en) 2011-12-15 2018-06-12 Honeywell International Inc. Gas valve with high/low gas pressure detection
US9234661B2 (en) 2012-09-15 2016-01-12 Honeywell International Inc. Burner control system
US10215291B2 (en) 2013-10-29 2019-02-26 Honeywell International Inc. Regulating device
US10024439B2 (en) 2013-12-16 2018-07-17 Honeywell International Inc. Valve over-travel mechanism

Also Published As

Publication number Publication date
EP0356690A1 (en) 1990-03-07
ATE89657T1 (en) 1993-06-15
DE3829664C1 (en) 1990-01-18

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