EP1710512B1 - Method of operating a heating installation comprising a mixer - Google Patents

Method of operating a heating installation comprising a mixer Download PDF

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Publication number
EP1710512B1
EP1710512B1 EP06101245A EP06101245A EP1710512B1 EP 1710512 B1 EP1710512 B1 EP 1710512B1 EP 06101245 A EP06101245 A EP 06101245A EP 06101245 A EP06101245 A EP 06101245A EP 1710512 B1 EP1710512 B1 EP 1710512B1
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EP
European Patent Office
Prior art keywords
mixer
pump
heat
transfer medium
heat transfer
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EP06101245A
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German (de)
French (fr)
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EP1710512A3 (en
EP1710512A2 (en
Inventor
Gerhard Pertiller
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Siemens AG Oesterreich
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Siemens AG Oesterreich
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F24D19/1015—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves
    • F24D19/1024—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves a multiple way valve
    • F24D19/1033—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves a multiple way valve motor operated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F24D19/1015—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves
    • F24D19/1021—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves a by pass valve

Definitions

  • the invention relates to a method for operating a heating system in which a heat transfer medium is pumped with at least one pump from a heat source via a flow to at least one heat consumer and a return back to the heat source and at least one mixer, the flow temperature by admixture of heat transfer medium is regulated from the return. Furthermore, the invention relates to an arrangement for carrying out the method.
  • Heating systems with central heat generators and heat distribution by means of heat transfer medium to heat consumers are well known. As a rule, buildings are heated with such heating systems.
  • the heat generators are ovens, heat pumps, solar systems or other facilities in which heat is provided.
  • a heated by the heat source heat transfer medium can either circulate directly in the heating circuit or collected in a memory. It is also a renewed heat transfer via a heat exchanger or a four-way mixing valve possible, so that there is a separate heating circuit and a separate heat generator circuit.
  • the heat transfer medium is usually water, optionally mixed with additives to prevent deposits and corrosion in the pipe network.
  • the heated heat transfer medium is transported via a flow to the heat consumers.
  • heat consumers such as radiators, heat exchangers for hot water or heating hoses in foot or wall heaters
  • heat is dissipated to the rooms to be heated or the surfaces to be heated.
  • the cooled Heat transfer medium flows back via a return to the heat source.
  • Flow and return consisting of a line system with facilities for state detection and modification of the heat transfer medium (pumps, control and measuring units, etc.).
  • a natural circulation can be used as a result of the differences in weight between heated and cooled heat transfer medium.
  • the natural circulation is only conditionally controllable, which is why a pump is used according to the prior art for the circulation of the heat transfer medium.
  • the temperature of the heat transfer medium in the flow through the position of a mixer e.g. a three-way mixing valve or a four-way mixing valve, determined.
  • a mixer e.g. a three-way mixing valve or a four-way mixing valve
  • the pump and the mixer are designed for the maximum heating capacity of the heating system.
  • the pump is usually differential pressure controlled and the mixer flow temperature controlled. With decreasing output of heating power with less open heat consumers, the flow rates of the heat transfer medium through the pump and mixer drop. This has for larger heating systems, eg central heated residential buildings, with the result that the pump and mixer must be usable over a wide operating range. For example, only heat exchanger for hot water treatment as a heat consumer can be present in summer operation, pump and mixer then work only with a fraction of the maximum flow rate of the heat transfer medium. It often comes to an undesirable oscillation of the flow temperature, since with low flow rates of the heat transfer medium no optimal mixing operations are possible.
  • a control for heating systems by means of a pump with variable delivery rate for the circulation of a carrier liquid is also in the DE 26 13 297 described.
  • a smaller auxiliary mixer and a smaller auxiliary pump are arranged parallel to a main mixer and a main pump for heating systems which have a high maximum heating capacity with a large operating range.
  • Additional mixer and additional pump are designed for the low flow rates of the heat transfer medium, in which the main pump and main mixer no longer satisfactory mixing process. But even with this solution, it can come in operating areas with further reduction of the flow rates to a swing of the flow temperature.
  • the invention is therefore based on the object to provide a comparison with the prior art improved heating system with mixer.
  • the advantage lies in avoiding the oscillation of the flow temperature in all operating conditions and is due to the arrangement of a reflux bypass, at least a mixer and the at least one pump bridges and over which each supply line of the at least one mixer, a portion of the heat transfer medium is supplied. In that section of the flow, which is located between the connections of the reflux bypass, then the flow rates of the heat transfer medium through the open heat consumers and the return flow bypass. For the pumps and mixers in this section of the flow, it is thus possible to set a minimum flow rate at which the flow temperature does not yet oscillate.
  • An advantageous embodiment of the invention provides that for the at least one mixer a design-dependent minimum flow rate is set, wherein when approaching this with a valve in the return flow bypass, the flow is increased so far that the minimum flow rate in the at least one mixer does not fall below becomes.
  • the heating system can then be operated up to the flow rate through the heat consumer, in which no oscillation of the flow occurs, with closed valve in the return flow bypass. Only when the flow rate approaches the lower limit of the optimized mixer operating range, the valve is opened so that there is always a set minimum flow rate. This optimizes the power consumption of the pump for the entire operating range.
  • the valve is advantageously arranged in the region of the reflux bypass, which is not formed as branches to the mixer ports, so that the entire reflux amount of the heat transfer medium flows through the valve.
  • the non-return valve may be, for example, check valves or check valves, which allow only one direction of flow and thereby have a low flow resistance in the flow direction.
  • the flow rate over the speed of the at least one pump In order to detect the approach to the minimum flow rate in the at least one mixer, it is recommended that the flow rate over the speed of the at least one pump to measure, if it is a centrifugal pump with flow proportional speed.
  • the heat transfer medium is then performed when approaching a minimum speed of the main pump only by means of additional pump on the smaller additional mixer or open the valve in the return flow bypass.
  • additional elements for flow rate measurement can be omitted.
  • heating scheme shown is starting from a heat source 1 via a flow 2 by a mixer 4 and a pump 5, the heated heat transfer medium to heat consumers 8 moves.
  • the heat source 1 may be a heat generator (eg, oven, heat pump, solar element, thermal source, etc.), a memory or a heat transfer device (heat exchanger, four-way mixing valve).
  • the mixer 4 which is shown here as a three-way mixing valve with servomotor M, the heated heat transfer medium, a portion of the cooled heat transfer medium from the return 3 is added.
  • a pump 5 is usually a centrifugal circulation pump used, the flow rate is proportional to the speed.
  • the mixing ratio between the heated and cooled heat transfer medium is determined, resulting in the flow temperature T results, with the heat transfer medium reaches the heat consumers 8 and with a thermometer. 6 is detected.
  • the mixer 4 is regulated so that the flow temperature T follows the setpoint temperature specification.
  • the difference between the pressure in the flow 2 and in the return 4 is detected by a pressure gauge 7.
  • the pump 5 operates with a differential pressure control with constant differential pressure specification. This results in the dependence of the flow rate through the pump 5 on the number of flowed through heat consumer 8, which are usually divided into parallel zones. The fewer zone valves are opened, the lower the flow rate through the pump must be set so that the pressure drop in the heat consumers 8 remains constant. From a design-related minimum flow rate of the mixer 4, it may then come to unwanted oscillation of the flow temperature T.
  • FIG. 2 is that in FIG. 1 Scheme shown extended to the inventive arrangement of a reflux bypass 10, with which prevents the flow rate of the heat transfer medium through the mixer 4 and the pump 5 drops below a minimum value at which it comes to oscillation of the flow temperature T. It is advantageous if the flow rate is detected by the speed of the designed as a centrifugal circulation pump 5.
  • the reflux bypass 10 branches off after the thermometer 6 and leads to a valve 11, with which the flow rate through the reflux bypass 10 is controlled. Behind the valve 11 is a branching and continuation to the two connection points with the inflow lines of the mixer 4.
  • the valve 11 is for example a solenoid valve or a tap, which is controlled by a servomotor M.
  • non-return valve 12 In all lines that open into the inlet lines of the mixer 4, non-return valve 12 are arranged to prevent erroneous circulation.
  • FIG. 3 the scheme of a heating system according to the invention with two mixers 4 and 14 and two pumps 5 and 13 is shown for large residential buildings.
  • the line branch with the main pump 5 and the main mixer 4 a line branch with a smaller auxiliary pump 5 and an additional mixer 4 is connected in parallel.
  • a backflow bypass 10 with a valve 11 is again arranged.
  • the flow temperature T is detected, which serves as an actual variable for the temperature control of the mixer 4 and 14.
  • the pressure drop in the heat consumers 8 corresponding differential pressure Ap between the pressure in the flow 2 and the pressure in the return 3 is detected again via a pressure gauge 7.
  • the differential pressure ⁇ p is the actual variable for the differential pressure control of the pumps 5 and 13.
  • both pumps 5 and 13 are in operation.
  • the speed in the main pump 5 is lowered. This happens until the minimum flow rate for the main mixer 4 is reached.
  • the heat transfer medium is only passed through the smaller additional mixer 14 by the main pump 5 is no longer and the auxiliary pump 13 is operated.
  • the speed of the auxiliary pump 13 is further reduced until the minimum flow rate of the auxiliary mixer 14 is reached.
  • the valve 11 is opened in the return flow bypass and generates an additional circulation through the auxiliary mixer 14 and the auxiliary pump 13.

Abstract

The method involves having a heat distribution medium pumped via a mixer (4) by a heat source (1) over a flow (2) to a heat consumer (8) and over a return (3) back to the heat source. The mixer has an inlet temperature (T) regulated by the mixture of the heat distribution medium from the return. Each inlet of the heat distribution medium has a return flow bypass (10), bridging over the mixer with a pump (5) supplied.

Description

Die Erfindung betrifft ein Verfahren zum Betreiben einer Heizanlage, bei der ein Wärmeträgermedium mit wenigstens einer Pumpe von einer Wärmequelle über einen Vorlauf zu wenigstens einem Wärmeverbraucher und über einen Rücklauf zurück zur Wärmequelle gepumpt wird und bei der mit wenigstens einem Mischer die Vorlauftemperatur durch Beimischung von Wärmeträgermedium aus dem Rücklauf geregelt wird. Des Weiteren betrifft die Erfindung eine Anordnung zur Durchführung des Verfahrens.The invention relates to a method for operating a heating system in which a heat transfer medium is pumped with at least one pump from a heat source via a flow to at least one heat consumer and a return back to the heat source and at least one mixer, the flow temperature by admixture of heat transfer medium is regulated from the return. Furthermore, the invention relates to an arrangement for carrying out the method.

Heizanlagen mit zentralen Wärmeerzeugern und Wärmeverteilung mittels Wärmeträgermedium zu Wärmeverbrauchern sind allgemein bekannt. In der Regel werden mit derartigen Heizanlagen Gebäude beheizt. Die Wärmeerzeuger sind dabei Öfen, Wärmepumpen, Solaranlagen oder sonstige Einrichtungen, in denen Wärme zur Verfügung gestellt wird. Ein vom Wärmeerzeuger erwärmtes Wärmeträgermedium kann entweder direkt im Heizkreislauf zirkulieren oder in einem Speicher gesammelt werden. Es ist auch ein neuerlicher Wärmeübergang über einen Wärmetauscher oder ein Vierwegmischventil möglich, so dass ein eigener Heizkreislauf und ein eigener Wärmeerzeugerkreislauf vorliegen. Das Wärmeträgermedium ist in der Regel Wasser, gegebenenfalls mit Additiven zur Vermeidung von Ablagerungen und Korrosion im Leitungsnetz versetzt.Heating systems with central heat generators and heat distribution by means of heat transfer medium to heat consumers are well known. As a rule, buildings are heated with such heating systems. The heat generators are ovens, heat pumps, solar systems or other facilities in which heat is provided. A heated by the heat source heat transfer medium can either circulate directly in the heating circuit or collected in a memory. It is also a renewed heat transfer via a heat exchanger or a four-way mixing valve possible, so that there is a separate heating circuit and a separate heat generator circuit. The heat transfer medium is usually water, optionally mixed with additives to prevent deposits and corrosion in the pipe network.

Ausgehend von einer Wärmequelle (Wärmeerzeuger, Pufferspeicher, Wärmetauscher, Vierwegemischventil) wird das erwärmte Wärmeträgermedium über einen Vorlauf zu den Wärmeverbrauchern transportiert. In den Wärmeverbrauchern, beispielsweise Heizkörper, Wärmetauscher zur Warmwasseraufbereitung oder Heizschläuche bei Fuß- oder Wandheizungen, erfolgt eine Wärmeabgabe an die zu beheizenden Räume bzw. die zu beheizenden Flächen. Das abgekühlte Wärmträgermedium fließt über einem Rücklauf zur Wärmequelle zurück. Vorlauf und Rücklauf bestehend dabei aus einem Leitungssystem mit Einrichtungen zur Zustandserfassung und -änderung des Wärmeträgermediums (Pumpen, Steuer- und Messeinheiten etc.). Wenn die Wärmequelle auf einem niedrigeren Höhenniveau wie die Wärmeverbraucher angeordnet ist, kann eine natürliche Zirkulation als Resultat der Gewichtsunterschiede zwischen erwärmten und abgekühlten Wärmeträgermedium genutzt werden. Allerdings ist die natürliche Zirkulation nur bedingt steuerbar, weshalb nach dem Stand der Technik zur Zirkulation des Wärmeträgermediums eine Pumpe eingesetzt wird.Starting from a heat source (heat generator, buffer storage, heat exchanger, four-way mixing valve), the heated heat transfer medium is transported via a flow to the heat consumers. In the heat consumers, such as radiators, heat exchangers for hot water or heating hoses in foot or wall heaters, heat is dissipated to the rooms to be heated or the surfaces to be heated. The cooled Heat transfer medium flows back via a return to the heat source. Flow and return consisting of a line system with facilities for state detection and modification of the heat transfer medium (pumps, control and measuring units, etc.). If the heat source is located at a lower level than the heat consumers, a natural circulation can be used as a result of the differences in weight between heated and cooled heat transfer medium. However, the natural circulation is only conditionally controllable, which is why a pump is used according to the prior art for the circulation of the heat transfer medium.

Bei bekannten, einfach ausgestalteten Heizanlagen, wird die Temperatur des Wärmeträgermediums im Vorlauf durch die Stellung eines Mischers, z.B. eines Dreiweg-Mischventils oder eines Vierweg-Mischventils, bestimmt. Dabei wird das von der Wärmequelle kommende Wärmeträgermedium durch Mischung mit Wärmeträgermedium aus dem Rücklauf auf eine gewünschte Temperatur gebracht.In known, simply designed heating systems, the temperature of the heat transfer medium in the flow through the position of a mixer, e.g. a three-way mixing valve or a four-way mixing valve, determined. In this case, the coming from the heat source heat transfer medium is brought by mixing with heat transfer medium from the return to a desired temperature.

In der EP 0 001 615 A1 ist beispielsweise ein derartige Heizungsanlage beschrieben, wobei im Vorlauf ein Temperaturfühler angebracht ist, über den die Zumischmenge des Wärmeträgermediums aus der Rücklauf geregelt wird.In the EP 0 001 615 A1 For example, such a heating system is described, wherein in the flow a temperature sensor is mounted, via which the mixing amount of the heat transfer medium from the return is controlled.

Auch zur Erzeugung von Warmwasser sind Anlagen bekannt, bei denen die Wassertemperatur des Brauchwassers durch Zumischung von Frischwasser geregelt wird, wie beispielsweise in der DE 101 22 475 A1 und der DE 202 17 305 U1 offenbart.Also for the production of hot water systems are known in which the water temperature of the service water is regulated by admixing fresh water, such as in the DE 101 22 475 A1 and the DE 202 17 305 U1 disclosed.

Die Pumpe und der Mischer sind für die maximale Heizleistung der Heizanlage ausgelegt. Dabei wird die Pumpe in der Regel differenzdruckgeregelt und der Mischer vorlauftemperaturgeregelt. Mit sinkender Heizleistungsabgabe bei weniger geöffneten Wärmeverbrauchern sinken dabei die Durchflussmengen des Wärmeträgermediums durch Pumpe und Mischer. Das hat bei größeren Heizanlagen, z.B. bei zentral beheizten Wohnhausanlagen, zur Folge, dass Pumpe und Mischer über einen großen Betriebsbereich hinweg einsetzbar sein müssen. Beispielsweise können im Sommerbetrieb nur Wärmetauscher zur Warmwasseraufbereitung als Wärmeverbraucher vorhanden sein, Pumpe und Mischer arbeiten dann nur mit einem Bruchteil der maximalen Durchflussmenge des Wärmeträgermediums. Dabei kommt es oft zu einem unerwünschten Pendeln der Vorlauftemperatur, da mit geringen Durchflussmengen des Wärmeträgermediums keine optimalen Mischvorgänge mehr möglich sind.The pump and the mixer are designed for the maximum heating capacity of the heating system. The pump is usually differential pressure controlled and the mixer flow temperature controlled. With decreasing output of heating power with less open heat consumers, the flow rates of the heat transfer medium through the pump and mixer drop. This has for larger heating systems, eg central heated residential buildings, with the result that the pump and mixer must be usable over a wide operating range. For example, only heat exchanger for hot water treatment as a heat consumer can be present in summer operation, pump and mixer then work only with a fraction of the maximum flow rate of the heat transfer medium. It often comes to an undesirable oscillation of the flow temperature, since with low flow rates of the heat transfer medium no optimal mixing operations are possible.

Bei Heizungsanlegen mit Mischer bewirkt auch eine steigende Außentemperatur, dass die Zumischmenge aus dem Rückfluss abnimmt. Für diesen Fall ist in der DE 23 58 754 A1 ein Verfahren und eine Steuerung einer Heizungsanlage beschrieben, bei der die Leistung der Umwälzpumpe in Abhängigkeit von der Temperaturdifferenz zwischen Vorlauf und Rücklauf gesteuert wird.When heating with mixer also causes an increasing outside temperature, that the admixed amount decreases from the reflux. For this case is in the DE 23 58 754 A1 a method and a control of a heating system described in which the performance of the circulating pump is controlled in dependence on the temperature difference between flow and return.

Eine Steuerung für Heizungsanlagen mittels einer Pumpe mit variierbarer Fördermenge für die Zirkulation einer Trägerflüssigkeit ist auch in der DE 26 13 297 beschrieben.A control for heating systems by means of a pump with variable delivery rate for the circulation of a carrier liquid is also in the DE 26 13 297 described.

Nach dem Stand der Technik werden für Heizanlagen, die eine hohe maximale Heizleistung bei gleichzeitig großem Betriebsbereich aufweisen, parallel zu einem Hauptmischer und einer Hauptpumpe ein kleinerer Zusatzmischer und eine kleinere Zusatzpumpe angeordnet. Zusatzmischer und Zusatzpumpe sind dabei für die niedrigen Durchsatzmengen des Wärmeträgermediums ausgelegt, bei denen Hauptpumpe und Hauptmischer keinen zufrieden stellenden Mischvorgang mehr liefern. Aber auch bei dieser Lösung kann es in Betriebsbereichen mit weiterer Verringerung der Durchsatzmengen zu einem Pendeln der Vorlauftemperatur kommen.According to the state of the art, a smaller auxiliary mixer and a smaller auxiliary pump are arranged parallel to a main mixer and a main pump for heating systems which have a high maximum heating capacity with a large operating range. Additional mixer and additional pump are designed for the low flow rates of the heat transfer medium, in which the main pump and main mixer no longer satisfactory mixing process. But even with this solution, it can come in operating areas with further reduction of the flow rates to a swing of the flow temperature.

Der Erfindung liegt daher die Aufgabe zugrunde, eine gegenüber dem Stand der Technik verbesserte Heizanlage mit Mischer anzugeben.The invention is therefore based on the object to provide a comparison with the prior art improved heating system with mixer.

Erfindungsgemäß wird diese Aufgabe gelöst durch ein Verfahren nach Patentanspruch 1 und eine Heizanlage zur Durchführung des Verfahrens nach Patentanspruch 5. Der Vorteil liegt dabei in der Vermeidung des Pendelns der Vorlauftemperatur in allen Betriebszuständen und begründet sich in der Anordnung eines Rückfluss-Bypasses, der den zumindest einen Mischer und die zumindest eine Pumpe überbrückt und über den jeder Zuleitung des zumindest einen Mischers ein Teil des Wärmeträgermediums zugeführt wird. In jenem Abschnitt des Vorlaufs, der zwischen den Anschlüssen des Rückfluss-Bypasses liegt, addieren sich dann die Durchflussmengen des Wärmeträgermediums durch die geöffneten Wärmeverbraucher und den Rückfluss-Bypass. Für die in diesem Abschnitt des Vorlaufs liegenden Pumpen und Mischer kann somit eine Mindestdurchflussmenge eingestellt werden, bei der noch kein Pendeln der Vorlauftemperatur auftritt.This object is achieved by a method according to claim 1 and a heating system for carrying out the method according to claim 5. The advantage lies in avoiding the oscillation of the flow temperature in all operating conditions and is due to the arrangement of a reflux bypass, at least a mixer and the at least one pump bridges and over which each supply line of the at least one mixer, a portion of the heat transfer medium is supplied. In that section of the flow, which is located between the connections of the reflux bypass, then the flow rates of the heat transfer medium through the open heat consumers and the return flow bypass. For the pumps and mixers in this section of the flow, it is thus possible to set a minimum flow rate at which the flow temperature does not yet oscillate.

Daraus ergibt sich die Möglichkeit, bei Heizanlagen mit hoher maximaler Heizleistung und vielen nur zeitweise offenen Wärmeverbrauchen kostengünstige Mischeinrichtungen einzusetzen, die einen schmalen optimierten Betriebsbereich aufweisen.This results in the possibility of heating systems with high maximum heat output and many only temporarily open heat consuming inexpensive mixing equipment use, which have a narrow optimized operating range.

Eine vorteilhafte Ausprägung der Erfindung sieht vor, dass für den zumindest einen Mischer eine bauartabhängige Mindestdurchflussmenge festgelegt wird, wobei bei einer Annäherung an diese mit einem Ventil im Rückfluss-Bypass der Durchfluss so weit erhöht wird, dass die Mindestdurchflussmenge in dem zumindest einen Mischer nicht unterschritten wird. Die Heizanlage kann dann bis zu der Durchflussmenge durch die Wärmeverbraucher, bei dem noch kein Pendeln des Vorlaufs auftritt, mit geschlossenem Ventil im Rückfluss-Bypass betrieben werden. Erst wenn sich die Durchflussmenge der unteren Grenze des optimierten Mischerbetriebsbereichs nähert, wird das Ventil geöffnet, so dass immer eine eingestellte minimale Durchflussmenge vorhanden ist. Damit wird die Leistungsaufnahme der Pumpe für den gesamten Betriebsbereich optimiert.
Das Ventil ist dabei vorteilhaft in dem Bereich des Rückfluss-Bypass angeordnet, der nicht als Abzweigungen zu den Mischeranschlüssen ausgebildet ist, so dass die gesamte Rückflussmenge des Wärmeträgermediums durch das Ventil strömt.An advantageous embodiment of the invention provides that for the at least one mixer a design-dependent minimum flow rate is set, wherein when approaching this with a valve in the return flow bypass, the flow is increased so far that the minimum flow rate in the at least one mixer does not fall below becomes. The heating system can then be operated up to the flow rate through the heat consumer, in which no oscillation of the flow occurs, with closed valve in the return flow bypass. Only when the flow rate approaches the lower limit of the optimized mixer operating range, the valve is opened so that there is always a set minimum flow rate. This optimizes the power consumption of the pump for the entire operating range.
The valve is advantageously arranged in the region of the reflux bypass, which is not formed as branches to the mixer ports, so that the entire reflux amount of the heat transfer medium flows through the valve.

Von Vorteil ergibt sich weiters, wenn vor allen Leitungszusammenführungspunkten im Leitungsnetz Rückflussverhinderer angeordnet werden um Fehlzirkulationen zu verhindern. Dadurch wird der Wirkungsgrad der Anlage verbessert, weil so ein Maximum der im Wärmeträgermedium gespeicherten Wärme an die Wärmeverbraucher gelangt. Die Rückflussverhinderer können beispielsweise Rückschlagventile oder Rückschlagklappen sein, die nur eine Flussrichtung zulassen und dabei in Flussrichtung einen geringen Strömungswiderstand aufweisen.It is also advantageous if return flow inhibitors are arranged in front of all line junction points in the line network in order to prevent incorrect circulation. As a result, the efficiency of the system is improved, because as a maximum of the heat stored in the heat transfer medium reaches the heat consumer. The non-return valve may be, for example, check valves or check valves, which allow only one direction of flow and thereby have a low flow resistance in the flow direction.

Um die Annäherung an die Mindestdurchflussmenge in dem zumindest einen Mischer zu erfassen, empfiehlt es sich, die Durchflussmenge über die Drehzahl der zumindest einen Pumpe zu messen, wenn es sich dabei um eine Kreiselpumpe mit durchflussproportionaler Drehzahl handelt. Das Wärmeträgermedium wird dann bei Annäherung an eine Mindestdrehzahl der Hauptpumpe nur mehr mittels Zusatzpumpe über den kleineren Zusatzmischer geführt oder das Ventil im Rückfluss-Bypass geöffnet. Damit können zusätzliche Elemente zur Durchflussmengenmessung entfallen.In order to detect the approach to the minimum flow rate in the at least one mixer, it is recommended that the flow rate over the speed of the at least one pump to measure, if it is a centrifugal pump with flow proportional speed. The heat transfer medium is then performed when approaching a minimum speed of the main pump only by means of additional pump on the smaller additional mixer or open the valve in the return flow bypass. Thus, additional elements for flow rate measurement can be omitted.

Ausführungsbeispiele der Erfindung werden anhand von Figuren näher erläutert. Es zeigen beispielhaft:

Fig. 1:
eine schematische Darstellung einer Heizanlage mit Mischer nach dem Stand der Technik
Fig. 2:
eine schematische Darstellung einer erfindungsgemäßen Heizanlage mit einer Pumpe und einem Mischer
Fig. 3:
eine schematische Darstellung einer erfindungsgemäßen Heizanlage mit zwei Pumpen und zwei Mischern
Embodiments of the invention will be explained in more detail with reference to figures. They show by way of example:
Fig. 1:
a schematic representation of a heating system with mixer according to the prior art
Fig. 2:
a schematic representation of a heating system according to the invention with a pump and a mixer
3:
a schematic representation of a heating system according to the invention with two pumps and two mixers

In dem in Figur 1 dargestellten Heizungsschema wird ausgehend von einer Wärmequelle 1 über einem Vorlauf 2 durch einen Mischer 4 und eine Pumpe 5 das erwärmte Wärmeträgermedium zu Wärmeverbrauchern 8 bewegt. Die Wärmequelle 1 kann dabei ein Wärmeerzeuger (z.B. Ofen, Wärmepumpe, Solarelement, Thermalquelle etc.), ein Speicher oder eine Wärmeübergabeeinrichtung (Wärmetauscher, Vierwegemischventil) sein. Im Mischer 4, der hier als Dreiwegmischventil mit Stellmotor M dargestellt ist, wird dem erwärmten Wärmeträgermedium ein Teil des abgekühlten Wärmeträgermediums aus dem Rücklauf 3 zugemischt. Als Pumpe 5 kommt in der Regel eine Kreiselumwälzpumpe zum Einsatz, deren Fördermenge proportional zur Drehzahl ist.In the in FIG. 1 heating scheme shown is starting from a heat source 1 via a flow 2 by a mixer 4 and a pump 5, the heated heat transfer medium to heat consumers 8 moves. The heat source 1 may be a heat generator (eg, oven, heat pump, solar element, thermal source, etc.), a memory or a heat transfer device (heat exchanger, four-way mixing valve). In the mixer 4, which is shown here as a three-way mixing valve with servomotor M, the heated heat transfer medium, a portion of the cooled heat transfer medium from the return 3 is added. As a pump 5 is usually a centrifugal circulation pump used, the flow rate is proportional to the speed.

Durch die Stellung des Stellmotors M des Mischers 4 wird das Mischverhältnis zwischen erwärmtem und abgekühltem Wärmeträgermedium bestimmt, woraus sich die Vorlauftemperatur T ergibt, mit der das Wärmeträgermedium zu den Wärmeverbrauchern 8 gelangt und die mit einem Thermometer 6 erfasst wird. Der Mischer 4 wird dabei so geregelt, dass die Vorlauftemperatur T der Solltemperaturvorgabe nachfolgt.By the position of the servomotor M of the mixer 4, the mixing ratio between the heated and cooled heat transfer medium is determined, resulting in the flow temperature T results, with the heat transfer medium reaches the heat consumers 8 and with a thermometer. 6 is detected. The mixer 4 is regulated so that the flow temperature T follows the setpoint temperature specification.

Die Differenz zwischen dem Druck im Vorlauf 2 und im Rücklauf 4 wird über ein Manometer 7 erfasst. Die Pumpe 5 arbeitet dabei mit einer Differenzdruckregelung mit konstanter Differenzdruckvorgabe. Daraus ergibt sich die Abhängigkeit der Durchflussmenge durch die Pumpe 5 von der Anzahl durchströmter Wärmeverbraucher 8, wobei diese meist in parallel geschaltete Zonen aufgeteilt sind. Je weniger Zonenventile geöffnet sind, desto geringer muss dann die Durchflussmenge durch die Pumpe eingestellt werden, damit der Druckabfall in den Wärmeverbrauchern 8 konstant bleibt. Ab einer bauartbedingten Mindestdurchflussmenge des Mischers 4 kann es dann zum unerwünschten Pendeln der Vorlauftemperatur T kommen.The difference between the pressure in the flow 2 and in the return 4 is detected by a pressure gauge 7. The pump 5 operates with a differential pressure control with constant differential pressure specification. This results in the dependence of the flow rate through the pump 5 on the number of flowed through heat consumer 8, which are usually divided into parallel zones. The fewer zone valves are opened, the lower the flow rate through the pump must be set so that the pressure drop in the heat consumers 8 remains constant. From a design-related minimum flow rate of the mixer 4, it may then come to unwanted oscillation of the flow temperature T.

In Figur 2 ist das in Figur 1 dargestellte Schema um die erfindungsgemäße Anordnung eines Rückfluss-Bypasses 10 erweitert, mit dem verhindert wird, dass die Durchflussmenge des Wärmeträgermediums durch den Mischer 4 und die Pumpe 5 unter einen Mindestwert abfällt, bei dem es zum Pendeln der Vorlauftemperatur T kommt. Dabei ist es günstig, wenn die Durchflussmenge über die Drehzahl der als Kreiselumwälzpumpe ausgebildeten Pumpe 5 erfasst wird.In FIG. 2 is that in FIG. 1 Scheme shown extended to the inventive arrangement of a reflux bypass 10, with which prevents the flow rate of the heat transfer medium through the mixer 4 and the pump 5 drops below a minimum value at which it comes to oscillation of the flow temperature T. It is advantageous if the flow rate is detected by the speed of the designed as a centrifugal circulation pump 5.

Der Rückfluss-Bypass 10 zweigt nach dem Thermometer 6 ab und führt zu einem Ventil 11, mit dem die Durchflussmenge durch den Rückfluss-Bypass 10 gesteuert wird. Hinter dem Ventil 11 erfolgt eine Aufzweigung und Weiterführung zu den beiden Verbindungspunkten mit den Zuflussleitungen des Mischers 4. Das Ventil 11 ist beispielsweise ein Magnetventil oder ein Hahn, der über einen Stellmotor M gesteuert wird.The reflux bypass 10 branches off after the thermometer 6 and leads to a valve 11, with which the flow rate through the reflux bypass 10 is controlled. Behind the valve 11 is a branching and continuation to the two connection points with the inflow lines of the mixer 4. The valve 11 is for example a solenoid valve or a tap, which is controlled by a servomotor M.

In allen Leitungen, die in die Zuflussleitungen des Mischers 4 münden, sind Rückflussverhinderer 12 angeordnet, um Fehlzirkulationen zu verhindern.In all lines that open into the inlet lines of the mixer 4, non-return valve 12 are arranged to prevent erroneous circulation.

In Figur 3 ist das Schema einer erfindungsgemäßen Heizanlage mit zwei Mischern 4 und 14 und zwei Pumpen 5 und 13 für große Wohnhausanlagen dargestellt. Dabei ist dem Leitungszweig mit der Hauptpumpe 5 und dem Hauptmischer 4 ein Leitungszweig mit einer kleineren Zusatzpumpe 5 und einem Zusatzmischer 4 parallel geschaltet. Die beiden Leitungszweige überbrückend ist wieder ein Rückfluss-Bypass 10 mit einem Ventil 11 angeordnet. Über ein den Pumpen 5 und 13 nachgeschaltetes Thermometer 6 wird die Vorlauftemperatur T erfasst, die als Istgröße für die Temperaturregelung der Mischer 4 und 14 dient.In FIG. 3 the scheme of a heating system according to the invention with two mixers 4 and 14 and two pumps 5 and 13 is shown for large residential buildings. In this case, the line branch with the main pump 5 and the main mixer 4, a line branch with a smaller auxiliary pump 5 and an additional mixer 4 is connected in parallel. Bridging over the two line branches, a backflow bypass 10 with a valve 11 is again arranged. About a pump 5 and 13 downstream thermometer 6, the flow temperature T is detected, which serves as an actual variable for the temperature control of the mixer 4 and 14.

Der dem Druckabfall in den Wärmeverbrauchern 8 entsprechende Differenzdruck Δp zwischen dem Druck im Vorlauf 2 und dem Druck im Rücklauf 3 wird wieder über ein Manometer 7 erfasst. Der Differenzdruck Δp ist dabei die Istgröße für die Differenzdruckregelung der Pumpen 5 und 13. Beim Vollbetrieb mit maximaler Heizleistung sind dann beide Pumpen 5 und 13 in Betrieb. Mit abnehmender Heizleistung und damit sinkender Durchflussmenge wird die Drehzahl in der Hauptpumpe 5 gesenkt. Das geschieht so lange, bis für den Hauptmischer 4 die Minimaldurchflussmenge erreicht wird. Dann wird das Wärmeträgermedium nur mehr über den kleineren Zusatzmischer 14 geleitet, indem die Hauptpumpe 5 nicht mehr und die Zusatzpumpe 13 weiter betrieben wird. Bei weiterer Absenkung der Heizleistung und damit der Durchflussmenge durch die Wärmeverbraucher 8 wird die Drehzahl der Zusatzpumpe 13 weiter reduziert, bis die Mindestdurchflussmenge des Zusatzmischers 14 erreicht wird. Dann wird das Ventil 11 im Rückfluss-Bypass geöffnet und eine zusätzliche Zirkulation durch den Zusatzmischer 14 und die Zusatzpumpe 13 erzeugt.The pressure drop in the heat consumers 8 corresponding differential pressure Ap between the pressure in the flow 2 and the pressure in the return 3 is detected again via a pressure gauge 7. The differential pressure Δp is the actual variable for the differential pressure control of the pumps 5 and 13. During full operation with maximum heating power then both pumps 5 and 13 are in operation. With decreasing heating power and thus decreasing flow rate, the speed in the main pump 5 is lowered. This happens until the minimum flow rate for the main mixer 4 is reached. Then, the heat transfer medium is only passed through the smaller additional mixer 14 by the main pump 5 is no longer and the auxiliary pump 13 is operated. Upon further reduction of the heating power and thus the flow rate through the heat consumer 8, the speed of the auxiliary pump 13 is further reduced until the minimum flow rate of the auxiliary mixer 14 is reached. Then, the valve 11 is opened in the return flow bypass and generates an additional circulation through the auxiliary mixer 14 and the auxiliary pump 13.

Unmittelbar hinter den Pumpen 5 und 13 sind wieder Rückflussverhinderer 12 angeordnet, um eine Fehlzirkulation zu verhindern.Immediately behind the pumps 5 and 13 backflow preventer 12 are again arranged to prevent a Fehlzirkulation.

Claims (6)

  1. Method for operating a heating installation, with which a heat transfer medium is pumped using at least one pump (4) from a heat source (1) by way of an advance (2) to at least one heat consumer (8) and by way of a return (3) back to the heat source (1) and with which at least one mixer (4) is used to regulate the advance temperature (T) by mixing in heat transfer medium from the return (3),
    characterised in that some of the heat transfer medium is fed to each supply line of the at least one mixer by way of a return flow bypass (10) bridging the at least one mixer (4) and the at least one pump (5).
  2. Method according to claim 1, characterised in that a structure-dependent minimum throughflow quantity is determined for the at least one mixer (4) and when this is approached, a valve (11) in the return flow bypass (10) is used to increase the throughflow so that it does not fall below the minimum throughflow quantity in the at least one mixer (4).
  3. Method according to claims 1 to 2,
    characterised in that incorrect circulation is prevented by the arrangement of return flow check systems (12) upstream of all line merging points.
  4. Method according to claims 1 to 2,
    characterised in that the approaching of the minimum throughflow quantity is detected in the at least one mixer (4) by way of the speed of the at least one pump (5).
  5. Heating installation for implementing the method according to one of claims 1 to 4, characterised in that at least one pump (5) and at least one mixer (4) are disposed in the heating installation and a return flow bypass (10) bridging the at least one pump (5) and the at least one mixer (4) is provided and this return flow bypass is connected to each supply line of the at least one mixer.
  6. Heating installation according to claim 5,
    characterised in that a valve (11) is disposed in the return flow bypass (10) to determine the throughflow.
EP06101245A 2005-03-23 2006-02-03 Method of operating a heating installation comprising a mixer Not-in-force EP1710512B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT0049505A AT501299B8 (en) 2005-03-23 2005-03-23 METHOD FOR OPERATING A HEATING SYSTEM WITH MIXER

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EP1710512A2 EP1710512A2 (en) 2006-10-11
EP1710512A3 EP1710512A3 (en) 2008-07-23
EP1710512B1 true EP1710512B1 (en) 2010-03-31

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EP06101245A Not-in-force EP1710512B1 (en) 2005-03-23 2006-02-03 Method of operating a heating installation comprising a mixer

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EP (1) EP1710512B1 (en)
AT (2) AT501299B8 (en)
DE (1) DE502006006545D1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013001532B4 (en) 2013-01-29 2018-08-16 Ritter Energie- Und Umwelttechnik Gmbh & Co. Kg Solar return admixture for solar temperature limitation

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006054893A1 (en) * 2006-11-20 2008-05-21 Wilo Ag Compact heating installation
DE102012202375A1 (en) * 2012-02-16 2013-08-22 Rotex Heating Systems Gmbh Heating system and method for its operation
DE102017116079A1 (en) * 2017-07-18 2019-01-24 Eisenmann Se Supply circuit for a heat transfer medium for a consumer, industrial plant and method for operating such

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2358754A1 (en) * 1973-11-26 1975-05-28 Schumacher Josef Central heating plant output control - by altering flow, or bypass, of heat carrier in dependence on feed and return temp. difference
IT1036636B (en) * 1975-07-25 1979-10-30 Ve Ma Elettropompe Spa IMPROVEMENT IN THE MEANS FOR REGULATING THE TEMPERATURE OF ENVIRONMENTS PARTICULARLY FOR CIRCUS HEATING SYSTEMS FORCED FLUID LACING
DE2747969A1 (en) * 1977-10-26 1979-05-10 Braukmann Armaturen CONTROL DEVICE FOR A HEATING SYSTEM
DE3727442A1 (en) * 1987-08-17 1989-03-02 Gerhard Urban Method for producing hot water and apparatus for carrying out this method
DE10122475A1 (en) 2001-05-09 2002-11-14 Froeling Gmbh & Co Kessel Appb Improving circulation in drinking water heating systems involves circulating in distribution network and charging hot water storage device using common circulation pump for both processes
DE20217305U1 (en) 2002-11-09 2003-03-27 Dms Wasser Waermetechnik Gmbh Drinking water heating system maintains flow of disinfected water during periods of nil discharge

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013001532B4 (en) 2013-01-29 2018-08-16 Ritter Energie- Und Umwelttechnik Gmbh & Co. Kg Solar return admixture for solar temperature limitation

Also Published As

Publication number Publication date
EP1710512A3 (en) 2008-07-23
AT501299B8 (en) 2007-02-15
AT501299B1 (en) 2006-08-15
EP1710512A2 (en) 2006-10-11
ATE462936T1 (en) 2010-04-15
AT501299A4 (en) 2006-08-15
DE502006006545D1 (en) 2010-05-12

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