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EP0122475A2 - Heating installation - Google Patents

Heating installation Download PDF

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Publication number
EP0122475A2
EP0122475A2 EP84102841A EP84102841A EP0122475A2 EP 0122475 A2 EP0122475 A2 EP 0122475A2 EP 84102841 A EP84102841 A EP 84102841A EP 84102841 A EP84102841 A EP 84102841A EP 0122475 A2 EP0122475 A2 EP 0122475A2
Authority
EP
European Patent Office
Prior art keywords
water
heating
hot water
heat generator
heating system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP84102841A
Other languages
German (de)
French (fr)
Other versions
EP0122475B1 (en
EP0122475A3 (en
Inventor
Heinz Prof. Dr.-Ing. Bach
Gunther Dipl.-Ing. Claus
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Forschungsgesellschaft Heizung- Lueftung- Klimatechnik Stuttgart Mbh
Original Assignee
Forschungsgesellschaft Heizung- Lueftung- Klimatechnik Stuttgart Mbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Forschungsgesellschaft Heizung- Lueftung- Klimatechnik Stuttgart Mbh filed Critical Forschungsgesellschaft Heizung- Lueftung- Klimatechnik Stuttgart Mbh
Priority to AT84102841T priority Critical patent/ATE44410T1/en
Publication of EP0122475A2 publication Critical patent/EP0122475A2/en
Publication of EP0122475A3 publication Critical patent/EP0122475A3/en
Application granted granted Critical
Publication of EP0122475B1 publication Critical patent/EP0122475B1/en
Expired legal-status Critical Current

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Classifications

    • 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
    • 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
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/002—Central heating systems using heat accumulated in storage masses water heating system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/263—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body with a dry-wall combustion chamber

Definitions

  • the invention relates to a heating system with a heat generator and a heating water circuit of the type specified in the preamble of claim 1 and a method for their operation.
  • the heat capacity of the water in the boiler is required in order to bring about an adjustment between the burner output and the much smaller power requirement of the system.
  • the known boilers therefore have a water content of at least 35 liters in small systems and 100 liters and more in larger systems.
  • a relatively large heat capacity is also required to obtain reasonably long burner runtimes with as few on and off operations as possible during the day.
  • the boiler cools down as a result of the chimney draft during burner shutdown.
  • the resulting cooling losses are greater the greater the heat capacity of the boiler.
  • the amount of water cannot be reduced arbitrarily, as this leads to shorter and shorter burner runtimes and thus to more frequent switching on and off and to greater fluctuations in the flow temperature.
  • the unfavorable combustion processes in the ignition phase, the soot to - lead and pollutant formation receive greater weight in shorter burner running times.
  • lower flue gas temperatures are reached on average, resulting in faster chimney corrosion. To avoid this, inappropriately high burner outputs are set for the boiler, which in turn leads to increased losses and shorter burner runtimes.
  • the invention is therefore based on the object of developing a heating system in which the fluctuations in the heating flow temperature can be kept within narrow limits and the heat generator of which can be operated largely independently of the consumer power with relatively long runtimes and few switch-on processes.
  • Another object of the invention is to provide an advantageous method for operating such a heating system.
  • the invention is based once on the knowledge known per se that a high heat capacity in the area of the heat generator is required for smooth operation of the system with long runtimes and few switch-on processes of the heat generator.
  • the heat generator as such must not be oversized in terms of its heat capacity, so that excessive cooling losses do not occur and the optimum operating state is quickly reached in the course of the start-up phase.
  • a heat generator with a relatively small storage capacity is combined in a suitable manner with a buffer store with a high storage capacity separated from it: the heated water emerging at the heat generator is distributed proportionally according to the outlet temperature to a charging branch containing the buffer storage and a bypass branch directly returned to the inlet point of the heat generator, whereby cold water displaced by the bypass branch is mixed with cold water from the buffer storage and / or the heating water circuit and the heating water circuit with hot water from the storage tank is fed.
  • the water emerging from the heat generator is first completely circulated through the bypass branch until a predetermined outlet temperature is reached.
  • the water in the heat generator can be displaced from the buffer tank by hot water at the start of a heating cycle. Accordingly, at the end of a heating cycle, the water in the heat generator can be displaced from the buffer storage by cold water in order to keep the cooling losses during standstill as low as possible.
  • the buffer store is designed as a stratified store, in which a temperature course which is monotonously decreasing in layers is maintained from the hot water inlet located above to the cold water outlet located below.
  • the charging process is controlled by two temperature sensors, which are arranged at a vertical distance from each other in the upper and lower part of the buffer memory.
  • the buffer store is gradually filled with hot water via the hot water inlet from top to bottom while the cold water is displaced through the cold water outlet.
  • the buffer store preferably has a multiple, expediently five to ten times the water content of the heat generator.
  • a boiler is preferably used as the heat generator, the water content of which is less than 35 liters, preferably between 15 and 20 liters.
  • a combustion chamber open on one side towards the front surface of the boiler is provided for a gas or oil blowing burner.
  • the front surface is at least partially water-cooled and carries guide plates designed as heat-conducting ribs for deflecting the combustion gases emerging from the combustion chamber into an annular space which surrounds the combustion chamber and is water-cooled on its outer surface and which opens into an exhaust manifold having a water-cooled secondary heating surface.
  • the baffles in the area of the front surface are spirally curved to improve the heat transfer.
  • the water-cooled outer surface of the annular space has helically wound baffles for the combustion gases designed as heat-conducting ribs.
  • the heat generator as a water-cooled heat pump which can be operated using the buffer store according to the invention and the bypass line according to the invention independently of the instantaneous power requirement under constant condition conditions which are optimally adapted to the design parameters of the heat pump.
  • the heating systems shown schematically as a circuit diagram in FIGS. 1 and 2 contain a heat generator 10, a buffer store 12 and a consumer circuit 16, 18 connected to the heat generator 10 and the buffer store 12 via a three-way mixer 14.
  • the heat generator 10 is acted upon at its water inlet 20 by a charging pump 22 with the water to be heated.
  • the heated water exits from the heat generator 10 at the hot water outlet 24 and from there passes via the charging line 26 and the hot water inlet 30 arranged in the upper region of the storage container 28 into the buffer store 12.
  • the cold water outlet 32 of the buffer store 12 arranged in the lower region of the storage container 28 is located via the line 34 and the charge pump 22 with the water inlet 20 of the heat generator 10 in connection.
  • a bypass line 36 is branched off at point 35, which bypasses buffer memory 12 is returned directly via the charge pump 22 to the water inlet 20 of the heat generator 10.
  • the bypass line 36 is branched off at a point 38 in the hot water area of the buffer store 12 and is returned to the water inlet 20 of the heat generator 10 via the charge pump 22.
  • the ratio of the flow rates through the buffer memory 12 containing loading branch 26 and the B ypasstechnisch 36 is adjusted by means of the temperature sensor 39 in accordance with the area of the hot water outlet 24 of the heat generator 10 measured water temperature.
  • This setting can be made using various means, of which three preferred variants are shown in FIGS. 1, 1a and 1b.
  • thermostatic water valve 40 in the charging line 26, which can be controlled via the temperature sensor 39.
  • the water valve 40 At the beginning of a heating cycle, as long as the water temperature at the hot water outlet 24 of the heat generator 10 is still low, the water valve 40 is closed, so that the water emerging from the heat generator 10 is first completely circulated via the bypass line 36.
  • the thermostatic valve 40 opens, so that part of the hot water reaches the hot water inlet 30 of the buffer storage 12, while the residual flow is still directly returned via the bypass line 36 to the water inlet 20 of the heat generator 10.
  • cold water from the buffer store 12 and / or the heating return 16 is now added to the bypass flow at the mixing point B.
  • the distribution of the hot water flow to the charging line 26 and the bypass line 36 takes place with the aid of a distribution valve 42, which can be adjusted via a servomotor 44 in accordance with the water temperature measured at the temperature sensor 39.
  • the setting range of the distribution valve 42 is larger than that of the thermostatic valve 40 according to FIG. 1, since here the bypass flow can also be controlled until it is completely switched off.
  • optimal dimensioning of the heating system during the heating phase of the bypass stream is at least 50%, eizwasserstroms preferably more than 80% of the circulated through the heat generator 10 H.
  • a mixing valve 46 is provided at the mixing point B, which is used instead of the thermostatic valve 40 according to FIG. 1 or the distribution valve 42 according to FIG.
  • the mixing valve 46 is controlled via an actuator 48 in accordance with the temperature measured with the temperature sensor 39 at the hot water outlet 24. Otherwise, the same operating states can be set as with the distribution valve 42.
  • the distribution valve 42 according to FIG. La and the mixing valve 46 according to FIG. 1b can also be controlled externally independently of the temperature sensor 38 and thus to optimize the switch-on and switch-off phase of a heating cycle in the Use as described below:
  • the cooled heat generator 10 for example a boiler, must be brought to its operating temperature as briefly as possible. in order to avoid condensation phenomena that could lead to corrosion.
  • the heating-up time can be shortened noticeably if the cooled water in the heat generator 10 is displaced from the buffer storage 12 by hot water before the start of the heat supply, for example before the ignition of a burner flame, and the heat generator 10 is thereby brought to operating temperature, at least in the water-carrying region.
  • the flow paths required for this can in principle be set via the distribution valve 42 or the mixing valve 46. In the arrangement shown in FIG. 1, however, the flow direction in the charging circuit and thus the pumping direction of the charging pump 22 must be reversed.
  • the bypass 36 is branched off from the hot water area of the buffer store 12, so that hot water is removed from the buffer store 12 at the branch point 38 and fed to the water inlet 20 of the heat generator 10 in the pumping direction can be.
  • the mixing that occurs during the start-up phase in the upper region of the buffer store 12 with the water displaced from the heat generator can be accepted, since this mixed water is displaced downward in the buffer store 12 during the subsequent charging process.
  • the buffer store 12 is a so-called stratified store, the hot water inlets and outlets 30, 50 of which are arranged on the top and the cold water outlets and inlets 32, 52 of which are arranged on the underside of a heat-insulated storage tank 28.
  • the highest possible temperature difference of the system is maintained between the upper and lower part of the buffer store 12.
  • In the intermediate area there is a monotonically decreasing temperature profile with a more or less steep temperature gradient between the hot water zone and the cold water zone.
  • a discharge line 54 is connected to a hot water outlet 50 of the storage tank 28, via which the heating flow 16 of the consumer circuit can be acted on with hot water.
  • the temperature at the heating flow 16 is set via the three-way mixer 14, the hot water connection 56 of which is connected to the discharge line 54 and the cold water connection 58 of which is connected to the heating return 18 and which is controlled via a servomotor 60 e.g. is adjustable in accordance with the measured outside temperatures.
  • the heating return 18 is also with the cold water inlet 52 of the buffer memory 12 and thus over the Mixing point B is also connected to the water inlet 20 of the heat generator 10.
  • the charging process is regulated by two temperature sensors 62, 64, which are arranged at a vertical distance from one another in the upper and lower part of the buffer store 12. As soon as the temperature reported by the upper temperature sensor 62 falls below a preset value, a heating cycle with charging is triggered via the controller 66. In the course of the heating cycle, the buffer store 12 is gradually filled with hot water from top to bottom via the hot water inlet 30, while the cold water is displaced from the buffer store via the cold water outlet 32. The charging process is continued until the temperature at the lower temperature sensor 64 exceeds a predetermined value and the controller 66 ends the positioning process by switching off the heat generator 10.
  • hot water can also be continuously removed via the discharge line 54 and supplied to the consumer.
  • a corresponding part of the cold water arriving at the heating return 18 is mixed with the cold water displaced from the buffer store 12 and fed to the mixing point B of the charging circuit.
  • the cold water from the heating return 18 only reaches the cold water inlet 52 of the buffer store, so that the hot water is gradually displaced from the buffer store 12 via the discharge line 54 until a new heating cycle is initiated .
  • the heat generator 10 can be, for example, a boiler 70 which, due to the presence of a additional buffer memory 12 only requires a relatively small water content.
  • a preferred embodiment of such a boiler 70 is shown in a vertical section.
  • the boiler contains a combustion chamber 74 which is open on one side towards the front plate 72 and into which the burner tube 78 of an oil or gas blower burner can be inserted through an opening 76 in the front plate 72.
  • the combustion gases generated in the burner flame 80 (arrows 82) are reversed to the front in the combustion chamber and reach the opening 84 and the spirally curved baffles 86 in the region of the front plate 72 radially outward, from there via the annular space 88 to the Exhaust collector 90 and the outlet port 92 to be directed.
  • Both the front plate 72 and the jacket 93 surrounding the annular space 88 and the exhaust manifold 90 are water-cooled.
  • the water inlet 20 and the hot water outlet 24 of the boiler 70 are located at mutually opposite points of the water jacket 92, 94 in the area of a tubular collector 102, 104 connected to the water jacket 92, 94 via passage openings 100.
  • the curved baffles 86 are designed as heat conduction ribs, which improve the heat transfer to the water-cooled front plate 72 and ensure a largely uniform temperature distribution.
  • guide plates 106 designed as heat conduction ribs, which are helically wound to increase the flow path and improve the heat transfer.
  • the exhaust manifold 90 is also provided with ribs 108 on its water-cooled secondary heating surface 94 and has one in accordance with the volume reduction of the combustion gases in the flow direction decreasing flow cross-section.
  • the inner dead space of the exhaust manifold 90 is filled with a displacement body 110.
  • the cylindrical part containing the combustion chamber 74 and the exhaust manifold 90 are detachably connected to one another at a flange connection 112.
  • the connection of the water jacket 92, 94 of these two parts can be produced within the flange connection 112 or with the aid of connecting pipes.
  • the boiler 70, the buffer store 12 and the three-way mixer 14 for connecting the heating flow and return 16, 18 are expediently arranged in a common, thermally insulated housing.
  • a boiler with a water content of approx. 15 to 25 liters is sufficient to supply a detached house, while the buffer storage should have a content of approx. 100 to 200 liters. Even with larger heating systems that require a higher burner output, the boiler content will hardly have to be more than 35 liters.
  • a water heater (not shown) can also be provided inside or outside the thermally insulated housing, the water content of which can be heated via an additional heating water circuit fed by the buffer store 12.
  • the heat generator 10 can also be designed as a water-cooled heat pump. With the help of Control mechanisms described using a buffer memory 12 and a bypass line 36, such a heat pump can be operated regardless of the current power requirement under constant operating conditions optimally adapted to the design parameters of the heat pump.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)
  • Control And Other Processes For Unpacking Of Materials (AREA)
  • Polarising Elements (AREA)
  • Heating, Cooling, Or Curing Plastics Or The Like In General (AREA)
  • Percussion Or Vibration Massage (AREA)
  • Housings, Intake/Discharge, And Installation Of Fluid Heaters (AREA)

Abstract

1. Heating installation with a heating boiler (10, 70) having a water inlet (20) and a hot water outlet ; with at least one hot water circuit which can be connected via a heating flow section (16) and a heating return section (18) to the heating boiler (10), if appropriate by way of a mixing device (14) ; with a buffer reservoir (12) having a hot water inlet (30) which can be connected to the hot water (24) of the heating boiler (10) to form a charging circuit and further having a cold water outlet (32) which can be connected to the water inlet (20) ; with a bypass pipe (36) which branches off from the charging circuit and can be connected to the water inlet (20) of the heating boiler (10), and which branches from a point (35, 38) situated before the hot water inlet (30) of the buffer reservoir (12) or in the hot water portion of the buffer reservoir (12) ; with a charging pump (22) arranged in the charging circuit before the bifurcation (35, 38) or behind the junction (B) of the bypass pipe (36), the heating flow section (16) of the hot water circuit being connectable via a take-off pipe (54) to a hot water outlet (50) of the buffer reservoir (12), while the heating return section (18) is connectable to the water inlet (20) of the heating boiler and/or to a cold water inlet (52) of the buffer reservoir, characterized in that the heating boiler (10, 70) has a combustion chamber (74) which opens on one side towards a front panel (72), said front panel (72) having an opening (76) for a burner pipe (78), pointing into the combustion chamber, of a gas or oil ventilator burner, in that the front panel (72) is water-cooled and bears baffle plates (86) in the form of heat-conducting fins to divert the combustion gases (82) exiting from the combustion chamber (74) into an annular space (88) surrounding the combustion chamber and water-cooled on its outer surface, and in that the annular space (88) opens into a flue gas collector (90) having a water-cooled top-up generator surface (94).

Description

Die Erfindung betrifft eine Heizanlage mit einem Wärmeerzeuger und einem Heizwasserkreislauf der im Oberbegriff des Anspruchs l angegebenen Gattung sowie ein Verfahren zu deren Betrieb.The invention relates to a heating system with a heat generator and a heating water circuit of the type specified in the preamble of claim 1 and a method for their operation.

Bei bekannten Heizanlagen mit einem Heizkessel als Wärmeerzeuger wird die Wärmekapazität des im Heizkessel befindlichen Wassers benötigt, um eine Anpassung zwischen der Brennerleistung und dem wesentlich kleineren Leistungsbedarf der Anlage herbeizuführen. Die bekannten Heizkessel besitzen deshalb einen Wasserinhalt von mindestens 35 Liter bei Kleinanlagen und von 100 Liter und mehr bei größeren Anlagen. Eine relativ große Wärmekapazität ist auch erforderlich um vernünftig lange Brennerlaufzeiten mit möglichst wenigen Ein- und Ausschaltvorgängen im Tagesverlauf zu erhalten.In known heating systems with a boiler as the heat generator, the heat capacity of the water in the boiler is required in order to bring about an adjustment between the burner output and the much smaller power requirement of the system. The known boilers therefore have a water content of at least 35 liters in small systems and 100 liters and more in larger systems. A relatively large heat capacity is also required to obtain reasonably long burner runtimes with as few on and off operations as possible during the day.

Andererseits findet während des Brennerstillstands eine Auskühlung des Kessels infolge Schornsteinzugs statt. Die dadurch bedingten Auskühlungsverluste sind um so größer, je größer die Wärmekapazität des Kessels ist. Die Wassermenge kann jedoch nicht beliebig reduziert werden, da dies zu immer kürzeren Brennerlaufzeiten und damit zu häufigeren Ein- und Ausschaltvorgängen und zu stärkeren Schwankungen in der Vorlauftemperatur führt. Die ungünstigen Verbrennungsvorgänge in der Zündphase, die zu Ruß- und Schadstoffbildung führen, erhalten bei kürzeren Brennerlaufzeiten ein größeres Gewicht. Außerdem werden im Mittel niedrigere Abgastemperaturen erreicht mit der Folge einer rascheren Schornsteinkorrosion. Um dies zu vermeiden, werden häufig für den Kessel unangemessen hohe Brennerleistungen eingestellt, die wiederum zu erhöhten Verlusten und zu kürzeren Brennerlaufzeiten führen.On the other hand, the boiler cools down as a result of the chimney draft during burner shutdown. The resulting cooling losses are greater the greater the heat capacity of the boiler. However, the amount of water cannot be reduced arbitrarily, as this leads to shorter and shorter burner runtimes and thus to more frequent switching on and off and to greater fluctuations in the flow temperature. The unfavorable combustion processes in the ignition phase, the soot to - lead and pollutant formation, receive greater weight in shorter burner running times. In addition, lower flue gas temperatures are reached on average, resulting in faster chimney corrosion. To avoid this, inappropriately high burner outputs are set for the boiler, which in turn leads to increased losses and shorter burner runtimes.

Der Erfindung liegt daher die Aufgabe zugrunde, eine Heizanlage zu entwickeln, bei der die Schwankungen in der Heizungsvorlauftemperatur in engen Grenzen gehalten werden können und deren Wärmeerzeuger weitgehend unabhängig von der Verbraucherleistung mit relativ langen Laufzeiten und wenigen Einschaltvorgängen betrieben werden kann. Eine weitere Erfindungsaufgabe besteht darin, ein vorteilhaftes Verfahren zum Betrieb einer solchen Heizanlage anzugeben.The invention is therefore based on the object of developing a heating system in which the fluctuations in the heating flow temperature can be kept within narrow limits and the heat generator of which can be operated largely independently of the consumer power with relatively long runtimes and few switch-on processes. Another object of the invention is to provide an advantageous method for operating such a heating system.

Zur Lösung dieser Aufgabe werden die in den Patentansprüchen 1 und 20 angegebenen Merkmalskombinationen vorgeschlagen. Weitere vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen.To achieve this object, the combinations of features specified in claims 1 and 20 are proposed. Further advantageous refinements and developments of the invention result from the subclaims.

Die Erfindung geht einmal von der an sich bekannten Erkenntnis aus, daß für einen gleichmäßigen Betrieb der Anlage mit langen Laufzeiten und wenigen Einschaltvorgängen des Wärmeerzeugers eine hohe Wärmekapazität im Bereich des Wärmeerzeugers erforderlich ist. Andererseits wurde erkannt, daß der Wärmeerzeuger als solcher in seiner Wärmekapazität nicht überdimensioniert werden darf, damit keine zu großenAuskühlverluste auftreten und der optimale Betriebszustand im Verlauf der Anfahrphase rasch erreicht wird. Mit den erfindungsgemäßen Vorkehrungen wird diesen an sich gegensätzlichen Anforderungen dadurch Rechnung getragen, daß ein Wärmeerzeuger mit relativ geringer Speicherkapazität mit einem von diesem getrennten Pufferspeicher mit hoher Speicherkapazität in geeigneter Weise kombiniert wird: Das am Wärmeerzeuger austretende aufgeheizte Wasser wird nach Maßgabe der Austrittstemperatur anteilmäßig auf einen den Pufferspeicher enthaltenden Ladezweig und einen zur Einläßstelle des Wärmeerzeugers unmittelbar zurückgeführten Bypasszweig verteilt, wobei dem durch den Bypasszweig zurückgeleiteten Wasser verdrängtes Kaltwasser aus dem Pufferspeicher und/oder dem Heizwasserkreislauf beigemischt wird und der Heizwasserkreislauf mit Heißwasser aus dem Pufferspeicher gespeist wird.The invention is based once on the knowledge known per se that a high heat capacity in the area of the heat generator is required for smooth operation of the system with long runtimes and few switch-on processes of the heat generator. On the other hand, it was recognized that the heat generator as such must not be oversized in terms of its heat capacity, so that excessive cooling losses do not occur and the optimum operating state is quickly reached in the course of the start-up phase. With the precautions according to the invention, these mutually contradictory requirements are taken into account in that a heat generator with a relatively small storage capacity is combined in a suitable manner with a buffer store with a high storage capacity separated from it: the heated water emerging at the heat generator is distributed proportionally according to the outlet temperature to a charging branch containing the buffer storage and a bypass branch directly returned to the inlet point of the heat generator, whereby cold water displaced by the bypass branch is mixed with cold water from the buffer storage and / or the heating water circuit and the heating water circuit with hot water from the storage tank is fed.

Zu Beginn eines Heizzyklus wird das aus dem Wärmeerzeuger austretende Wasser zunächst vollständig über den Bypasszweig umgewälzt, bis eine vorgegebene Austrittstemperatur erreicht ist. Um die optimalen Betriebstemperaturen des Wärmeerzeugers möglichst rasch zu erreichen, kann zu Beginn eines Heizzyklus das im Wärmeerzeuger befindliche Wasser durch Heißwasser aus dem Pufferspeicher verdrängt werden. Entsprechend kann am Ende eines Heizzyklus das im Wärmeerzeuger befindliche Wasser durch Kaltwasser aus dem Pufferspeicher verdrängt werden, um die Auskühlverluste während des Stillstands so klein wie möglich zu halten.At the beginning of a heating cycle, the water emerging from the heat generator is first completely circulated through the bypass branch until a predetermined outlet temperature is reached. In order to reach the optimal operating temperatures of the heat generator as quickly as possible, the water in the heat generator can be displaced from the buffer tank by hot water at the start of a heating cycle. Accordingly, at the end of a heating cycle, the water in the heat generator can be displaced from the buffer storage by cold water in order to keep the cooling losses during standstill as low as possible.

Gemäß einer bevorzugten Ausgestaltung der Erfindung ist der Pufferspeicher als Schichtspeicher ausgebildet, in welchem von dem oben befindlichen Heißwassereinlaß zum unten befindlichen Kaltwasserauslaß ein schichtweise monoton abnehmender Temperaturverlauf aufrechterhalten wird. Der Ladevorgang wird über zwei Temperaturfühler geregelt, die in senkrechtem Abstand voneinander im oberen bzw. unteren Teil des Pufferspeichers angeordnet sind. Im Verlauf eines solchen Ladevorgangs wird der Pufferspeicher allmählich über den Heißwassereinlaß von oben nach unten mit Heißwasser gefüllt, während das Kaltwasser über den Kaltwasserauslaß verdrängt wird. Der Pufferspeicher weist vorzugsweise ein Mehrfaches, zweckmäßig das Fünf- bis Zehnfache des Wasserinhalts des Wärmeerzeugers auf.According to a preferred embodiment of the invention, the buffer store is designed as a stratified store, in which a temperature course which is monotonously decreasing in layers is maintained from the hot water inlet located above to the cold water outlet located below. The charging process is controlled by two temperature sensors, which are arranged at a vertical distance from each other in the upper and lower part of the buffer memory. In the course of such a loading process, the buffer store is gradually filled with hot water via the hot water inlet from top to bottom while the cold water is displaced through the cold water outlet. The buffer store preferably has a multiple, expediently five to ten times the water content of the heat generator.

Als Wärmeerzeuger wird bevorzugt ein Heizkessel verwendet, dessen Wasserinhalt weniger als 35 Liter, vorzugsweise zwischen 15 und 20 Liter beträgt. Vorteilhafterweise ist eine zur Frontfläche des Heizkessels hin einseitig offene Brennkammer für einen Gas- oder Ölgebläsebrenner vorgesehen. Die Frontfläche ist zumindest teilweise wassergekühlt und trägt als Wärmeleitungsrippen ausgebildete Leitbleche zur Umlenkung der aus der Brennkammer austretenden Verbrennungsgase in einen die Brennkammer umgebenden, an seiner Außenfläche wassergekühlten Ringraum, der in einen eine wassergekühlte Nachschaltheizfläche aufweisenden Abgassammler mündet. Die Leitbleche im Bereich der Frontfläche sind zur Verbesserung des Wärmeübergangs spiralförmig gekrümmt. Aus dem gleichen Grund weist die wassergekühlte Außenfläche des Ringraumes schraubenförmig gewundene, als Wärmeleitungsrippen ausgebildete Leitbleche für die Verbrennungsgase auf.A boiler is preferably used as the heat generator, the water content of which is less than 35 liters, preferably between 15 and 20 liters. Advantageously, a combustion chamber open on one side towards the front surface of the boiler is provided for a gas or oil blowing burner. The front surface is at least partially water-cooled and carries guide plates designed as heat-conducting ribs for deflecting the combustion gases emerging from the combustion chamber into an annular space which surrounds the combustion chamber and is water-cooled on its outer surface and which opens into an exhaust manifold having a water-cooled secondary heating surface. The baffles in the area of the front surface are spirally curved to improve the heat transfer. For the same reason, the water-cooled outer surface of the annular space has helically wound baffles for the combustion gases designed as heat-conducting ribs.

Grundsätzlich ist es auch möglich, den Wärmeerzeuger als wassergekühlte Wärmepumpe auszubilden, die unter Verwendung des erfindungsgemäßen Pufferspeichers und der erfindungsgemäßen Bypassleitung unabhängig von der augenblicklichen Leistungsanforderung unter konstanten, an die Auslegungsparameter der Wärmepumpe optimal angepaßten Zustandsbedingungen betrieben werden kann.In principle, it is also possible to design the heat generator as a water-cooled heat pump which can be operated using the buffer store according to the invention and the bypass line according to the invention independently of the instantaneous power requirement under constant condition conditions which are optimally adapted to the design parameters of the heat pump.

Im folgenden wird die Erfindung anhand der Zeichnung näher erläutert. Es zeigen:

  • Fig. 1 eine Schaltskizze eines an eine Heizanlage anschließbaren Wärmeerzeugers mit Puffer- speicher und Thermostatventil im Ladekreislauf;
  • Fig. la den Ausschnitt A der Fig. l mit einem Verteilventil im Ladekreislauf;
  • Fig. lb den Ausschnitt B der Fig. 1 mit einem Misch-ventil im Ladekreislauf;
  • Fig. 2 eine Schaltskizze eines abgewandelten Ausführungsbeispiels eines an eine Heizanlage anschließbaren Wärmeerzeugers mit Pufferspeicher und aus dem Pufferspeicher abgezweigtem Bypass sowie Mischventil im Ladekreislauf;
  • Fig. 3 einen Längsschnitt durch einen als Heizkessel ausgebildeten Wärmeerzeuger.
The invention is explained in more detail below with reference to the drawing. Show it:
  • 1 shows a circuit diagram of a heat generator with a buffer store and a thermostatic valve in the charging circuit that can be connected to a heating system;
  • Fig. La section A of Figure 1 with a distribution valve in the charging circuit.
  • Fig. Lb the section B of Figure 1 with a mixing valve in the charging circuit.
  • 2 shows a circuit diagram of a modified exemplary embodiment of a heat generator which can be connected to a heating system and has a buffer store and a bypass branched off from the buffer store, as well as a mixing valve in the charging circuit;
  • Fig. 3 shows a longitudinal section through a heat generator designed as a boiler.

Die in Fig. 1 und 2 schematisch als Schaltbild dargestellten Heizanlagen enthalten einen Wärmeerzeuger 10, einen Pufferspeicher 12 und einen über einen Dreiwegemischer 14 an den Wärmeerzeuger 10 und den Pufferspeicher 12 angeschlossenen Verbraucherkreis 16,18. Der Wärmeerzeuger 10 wird an seinem Wassereinlaß 20 über eine Ladepumpe 22 mit dem aufzuheizenden Wasser beaufschlagt. Das aufgeheizte Wasser tritt am Heißwasserauslaß 24 aus dem Wärmeerzeuger 10 aus und gelangt von dort über die Ladeleitung 26 und den im oberen Bereich des Speicherbehälters 28 angeordneten Heißwassereinlaß 30 in den Pufferspeicher 12. Der im unteren Bereich des Speicherbehälters 28 angeordnete Kaltwasserauslaß 32 des Pufferspeichers 12 steht über die Leitung 34 und die Ladepumpe 22 mit dem Wassereinlaß 20 des Wärmeerzeugers 10 in Verbindung. Bei dem in Fig. 1 gezeigten Ausführungsbeispiel ist an der Stelle 35 eine Bypassleitung 36 abgezweigt, die unter Umgehung des Pufferspeichers 12 unmittelbar über die Ladepumpe 22 zum Wassereinlaß 20 des Wärmeerzeugers 10 zurückgeführt ist. Bei dem in Fig. 2 gezeigten Ausführungsbeispiel ist die Bypassleitung 36 an einer Stelle 38 im Heißwasserbereich des Pufferspeichers 12 abgezweigt und über die Ladepumpe 22 zum Wassereinlaß 20 des Wärmeerzeugers 10 zurückgeführt.The heating systems shown schematically as a circuit diagram in FIGS. 1 and 2 contain a heat generator 10, a buffer store 12 and a consumer circuit 16, 18 connected to the heat generator 10 and the buffer store 12 via a three-way mixer 14. The heat generator 10 is acted upon at its water inlet 20 by a charging pump 22 with the water to be heated. The heated water exits from the heat generator 10 at the hot water outlet 24 and from there passes via the charging line 26 and the hot water inlet 30 arranged in the upper region of the storage container 28 into the buffer store 12. The cold water outlet 32 of the buffer store 12 arranged in the lower region of the storage container 28 is located via the line 34 and the charge pump 22 with the water inlet 20 of the heat generator 10 in connection. In the exemplary embodiment shown in FIG. 1, a bypass line 36 is branched off at point 35, which bypasses buffer memory 12 is returned directly via the charge pump 22 to the water inlet 20 of the heat generator 10. In the exemplary embodiment shown in FIG. 2, the bypass line 36 is branched off at a point 38 in the hot water area of the buffer store 12 and is returned to the water inlet 20 of the heat generator 10 via the charge pump 22.

Das Verhältnis der Durchflußmengen durch den den Pufferspeicher 12 enthaltenden Ladezweig 26 und die Bypassleitung 36 wird über den Temperaturfühler 39 nach Maßgabe der im Bereich des Heißwasserauslasses 24 des Wärmeerzeugers 10 gemessenen Wassertemperatur eingestellt. Diese Einstellung kann mit verschiedenen Mitteln erfolgen, von denen in den Figuren 1,la und lb drei bevorzugte Varianten aufgezeigt sind.The ratio of the flow rates through the buffer memory 12 containing loading branch 26 and the B ypassleitung 36 is adjusted by means of the temperature sensor 39 in accordance with the area of the hot water outlet 24 of the heat generator 10 measured water temperature. This setting can be made using various means, of which three preferred variants are shown in FIGS. 1, 1a and 1b.

Bei der in Fig. 1 dargestellten Regelvariante befindet sich in der Ladeleitung 26 ein thermostatisches Wasserventil 40, das über den Temperaturfühler 39 ansteuerbar ist. Zu Beginn eines Heizzyklus, solange die Wassertemperatur am Heißwasserauslaß 24 des Wärmeerzeugers 10 noch niedrig ist, ist das Wasserventil 40 geschlossen, so daß das aus dem Wärmeerzeuger 10 austretende Wasser zunächst vollständig über die Bypassleitung 36 umgewälzt wird. Sobald die Austrittstemperatur einen vorgegebenen Wert erreicht, öffnet das Thermostatventil 40, so daß ein Teil des Heißwassers zum Heißwassereinlaß 30 des Pufferspeichers 12 gelangt, während der Reststrom nach wie vor über die Bypassleitung 36 unmittelbar zum Wassereinlaß 20 des Wärmeerzeugers 10 zurückgeführt wird. Im gleichen Maße, wie Heißwasser zum Pufferspeicher 12 gelangt, wird nun jedoch an der Mischstelle B Kaltwasser aus dem Pufferspeicher 12 und/oder dem Heizungsrücklauf 16 dem Bypassstrom beigemischt.In the control variant shown in FIG. 1, there is a thermostatic water valve 40 in the charging line 26, which can be controlled via the temperature sensor 39. At the beginning of a heating cycle, as long as the water temperature at the hot water outlet 24 of the heat generator 10 is still low, the water valve 40 is closed, so that the water emerging from the heat generator 10 is first completely circulated via the bypass line 36. As soon as the outlet temperature reaches a predetermined value, the thermostatic valve 40 opens, so that part of the hot water reaches the hot water inlet 30 of the buffer storage 12, while the residual flow is still directly returned via the bypass line 36 to the water inlet 20 of the heat generator 10. To the same extent as hot water arrives at the buffer store 12, cold water from the buffer store 12 and / or the heating return 16 is now added to the bypass flow at the mixing point B.

Bei der in Fig. la gezeigten Regelvariante erfolgt die Aufteilung des Heißwasserstromes auf die Ladeleitung 26 und die Bypassleitung 36 mit Hilfe eines Verteilventils 42, das nach Maßgabe der am Temperaturfühler 39 gemessenen Wassertemperatur über einen Stellmotor 44 einstellbar ist. Der Einstellbereich des Verteilventils 42 ist größer als der des Thermostatventils 40 nach Fig. 1, da hier auch der Bypassstrom bis zur vollständigen Abschaltung gesteuert werden kann. Bei optimaler Dimensionierung der Heizanlage beträgt während der Heizphase der Bypassstrom mindestens 50%, vorzugsweise mehr als 80% des durch den Wärmeerzeuger 10 umgewälzten Heizwasserstroms.In the control variant shown in FIG. 1 a, the distribution of the hot water flow to the charging line 26 and the bypass line 36 takes place with the aid of a distribution valve 42, which can be adjusted via a servomotor 44 in accordance with the water temperature measured at the temperature sensor 39. The setting range of the distribution valve 42 is larger than that of the thermostatic valve 40 according to FIG. 1, since here the bypass flow can also be controlled until it is completely switched off. With optimal dimensioning of the heating system during the heating phase of the bypass stream is at least 50%, eizwasserstroms preferably more than 80% of the circulated through the heat generator 10 H.

Als dritte Regelvariante ist gemäß Fig. lb an der Mischstelle B ein Mischventil 46 vorgesehen, das anstelle des Thermostatventils 40 nach Fig. 1 oder des Verteilventils 42 nach Fig. la verwendet wird. Das Mischventil 46 wird über einen Stellmotor 48 nach Maßgabe der mit dem Temperaturfühler 39 am Heißwasserauslaß 24 gemessenen Temperatur gesteuert. Im übrigen lassen sich damit die gleichen Betriebszustände wie mit dem Verteilventil 42 einstellen.As a third control variant, according to FIG. 1b, a mixing valve 46 is provided at the mixing point B, which is used instead of the thermostatic valve 40 according to FIG. 1 or the distribution valve 42 according to FIG. The mixing valve 46 is controlled via an actuator 48 in accordance with the temperature measured with the temperature sensor 39 at the hot water outlet 24. Otherwise, the same operating states can be set as with the distribution valve 42.

Im Gegensatz zu dem Thermostatventil 40 nach Fig. 1 lassen sich das Verteilventil 42 nach Fig. la und das Mischventil 46 nach Fig. lb auch noch unabhängig von dem Temperaturfühler 38 extern ansteuern und damit zu einer Optimierung der Einschalt- und Abschaltphase eines Heizzyklus in der nachstehend beschriebenen Weise verwenden:In contrast to the thermostatic valve 40 according to FIG. 1, the distribution valve 42 according to FIG. La and the mixing valve 46 according to FIG. 1b can also be controlled externally independently of the temperature sensor 38 and thus to optimize the switch-on and switch-off phase of a heating cycle in the Use as described below:

Zu Beginn eines Heizzyklus muß der ausgekühlte Wärmeerzeuger 10, beispielsweise ein Heizkessel, möglichst kurzzeitig auf seine Betriebstemperatur gebracht werden, um korrisionsgefährdende Kondensationserscheinungen zu vermeiden. Die Aufheizzeit kann merklich verkürzt werden, wenn das im Wärmeerzeuger 10 befindliche abgekühlte Wasser vor Beginn der Wärmezufuhr, also beispielsweise vor der Zündung einer Brennerflamme, durch Heißwasser aus dem Pufferspeicher 12 verdrängt und der Wärmeerzeuger 10 dadurch zumindest im wasserführenden Bereich etwa auf Betriebstemperatur gebracht wird. Die hierfür erforderlichen Strömungswege können grundsätzlich über das Verteilventil 42 oder das Mischventil 46 eingestellt werden. Bei der in Fig. 1 gezeigten Anordnung muß dazu allerdings die Strömungsrichtung im Ladekreislauf und damit die Pumprichtung der Ladepumpe 22 umgekehrt werden.At the beginning of a heating cycle, the cooled heat generator 10, for example a boiler, must be brought to its operating temperature as briefly as possible. in order to avoid condensation phenomena that could lead to corrosion. The heating-up time can be shortened noticeably if the cooled water in the heat generator 10 is displaced from the buffer storage 12 by hot water before the start of the heat supply, for example before the ignition of a burner flame, and the heat generator 10 is thereby brought to operating temperature, at least in the water-carrying region. The flow paths required for this can in principle be set via the distribution valve 42 or the mixing valve 46. In the arrangement shown in FIG. 1, however, the flow direction in the charging circuit and thus the pumping direction of the charging pump 22 must be reversed.

Um eine Strömungsumkehr zu vermeiden, ist bei der in Fig. 2 gezeigten Anordnung der Bypass 36 aus dem Heißwasserbereich des Pufferspeichers 12 abgezweigt, so daß an der Abzweigstelle 38 Heißwasser aus dem Puffer- speicher 12 entnommen und in Pumprichtung dem Wassereinlaß 20 des Wärmeerzeugers 10 zugeleitet werden kann. Die während der Anfahrphase dabei im oberen Bereich des Pufferspeichers 12 auftretende Durchmischung mit dem aus dem Wärmeerzeuger verdrängten Wasser kann in Kauf genommen werden, da dieses Mischwasser beim anschließenden Ladevorgang im Pufferspeicher 12 nach unten verdrängt wird.In order to avoid a reversal of the flow, in the arrangement shown in FIG. 2 the bypass 36 is branched off from the hot water area of the buffer store 12, so that hot water is removed from the buffer store 12 at the branch point 38 and fed to the water inlet 20 of the heat generator 10 in the pumping direction can be. The mixing that occurs during the start-up phase in the upper region of the buffer store 12 with the water displaced from the heat generator can be accepted, since this mixed water is displaced downward in the buffer store 12 during the subsequent charging process.

Am Ende eines Heizzyklus ist im Wärmeerzeuger 12 je nach dessen Wärmekapazität noch eine erhebliche Wärmemenge gespeichert, die der Heizanlage als sogenannte Auskühlverluste verloren gehen kann, wenn keine zusätzlichen Vorkehrungen getroffen werden. Bei der hier beschriebenen Anlage können diese Verluste dadurch vermieden werden, daß am Ende eines jeden Heizzyklus das Wasser im Ladekreislauf noch eine Zeitlang umgewälzt wird, bis das im Wärmeerzeuger 10 befindliche Wasser durch Kaltwasser aus dem Pufferspeicher 12 verdrängt ist. Auch die hierfür erforderlichen Strömungswege können über das Verteilventil 40 oder das Mischventil 46 gegebenenfalls über eine externe Regelung eingestellt werden.At the end of a heating cycle, depending on its heat capacity, a considerable amount of heat is still stored in the heat generator 12, which the heating system can lose as so-called cooling losses if no additional precautions are taken. In the system described here, these losses can ver be avoided that at the end of each heating cycle, the water in the charging circuit is circulated for a while until the water in the heat generator 10 is displaced by cold water from the buffer store 12. The flow paths required for this can also be set via the distribution valve 40 or the mixing valve 46, if necessary via an external control.

Der Pufferspeicher 12 ist ein sogenannter Schichtspeicher, dessen Heißwasserein- und -auslässe 30,50 an der Oberseite und dessen Kaltwasseraus- und -einlässe 32,52 an der Unterseite eines wärmeisolierten Speicherbehälters 28 angeordnet sind. Zwischen dem oberen und unteren Teil des Pufferspeichers 12 wird die höchstmögliche Temperaturdifferenz der Anlage aufrechterhalten. Im Zwischenbereich stellt sich ein schichtweise monoton abnehmender Temperaturverlauf mit einem mehr oder weniger steilen Temperaturgradienten zwischen der Heißwasserzone und der Kaltwasserzone ein.The buffer store 12 is a so-called stratified store, the hot water inlets and outlets 30, 50 of which are arranged on the top and the cold water outlets and inlets 32, 52 of which are arranged on the underside of a heat-insulated storage tank 28. The highest possible temperature difference of the system is maintained between the upper and lower part of the buffer store 12. In the intermediate area there is a monotonically decreasing temperature profile with a more or less steep temperature gradient between the hot water zone and the cold water zone.

Im oberen Bereich des Pufferspeichers 12 ist an einem Heißwasserauslaß 50 des Speicherbehälters 28 eine Entladeleitung 54 angeschlossen, über die der Heizungsvorlauf 16 des Verbraucherkreises mit Heißwasser beaufschlagbar ist. Die Temperatur am Heizungsvorlauf 16 wird über den Dreiwegemischer 14 eingestellt, dessen Heißwasseranschluß 56 mit der Entladeleitung 54 und dessen Kaltwasseranschluß 58 mit dem Heizungsrücklauf 18 verbunden und der über einen Stellmotor 60 z.B. nach Maßgabe der gemessenen Außentemperaturen einstellbar ist.In the upper area of the buffer store 12, a discharge line 54 is connected to a hot water outlet 50 of the storage tank 28, via which the heating flow 16 of the consumer circuit can be acted on with hot water. The temperature at the heating flow 16 is set via the three-way mixer 14, the hot water connection 56 of which is connected to the discharge line 54 and the cold water connection 58 of which is connected to the heating return 18 and which is controlled via a servomotor 60 e.g. is adjustable in accordance with the measured outside temperatures.

Der Heizungsrücklauf 18 ist außerdem mit dem Kaltwassereinlaß 52 des Pufferspeichers 12 und damit über die Mischstelle B auch mit dem Wassereinlaß 20 des Wärmeerzeugers 10 verbunden.The heating return 18 is also with the cold water inlet 52 of the buffer memory 12 and thus over the Mixing point B is also connected to the water inlet 20 of the heat generator 10.

Der Ladevorgang wird über zwei Temperaturfühler 62,64 geregelt, die in senkrechtem Abstand voneinander im oberen bzw. unteren Teil des Pufferspeichers 12 angeordnet sind. Sobald die vom oberen Temperaturfühler 62 gemeldete Temperatur einen Vorgabewert unterschreitet, wird über den Regler 66 ein Heizzyklus mit Ladevorgang ausgelöst. Im Verlauf des Heizzyklus wird der Puffer- speicher 12 allmählich über den Heißwassereinlaß 30 von oben nach unten mit Heißwasser gefüllt, während das Kaltwasser über den Kaltwasserauslaß 32 aus dem Pufferspeicher verdrängt wird. Der Ladevorgang wird so lange fortgesetzt, bis die Temperatur am unteren Temperaturfühler 64 einen vorgegebenen Wert übersteigt und der Regler 66 durch Abschalten des Wärmeerzeugers 10 den Lagevorgang beendet.The charging process is regulated by two temperature sensors 62, 64, which are arranged at a vertical distance from one another in the upper and lower part of the buffer store 12. As soon as the temperature reported by the upper temperature sensor 62 falls below a preset value, a heating cycle with charging is triggered via the controller 66. In the course of the heating cycle, the buffer store 12 is gradually filled with hot water from top to bottom via the hot water inlet 30, while the cold water is displaced from the buffer store via the cold water outlet 32. The charging process is continued until the temperature at the lower temperature sensor 64 exceeds a predetermined value and the controller 66 ends the positioning process by switching off the heat generator 10.

Während des Heizzyklus kann ständig auch Heißwasser über die Entladeleitung 54 entnommen und dem Verbraucher zugeführt werden. In diesem Falle wird ein entsprechender Teil des am Heizungsrücklauf 18 ankommenden Kaltwassers dem aus dem Pufferspeicher 12 verdrängten Kaltwasser zugemischt und der Mischstelle B des Ladekreislaufs zugeleitet. In der Zeit zwischen zwei Heizzyklen, in denen der Ladekreislauf abgestellt ist, gelangt das Kaltwasser aus dem Heizungsrücklauf 18 ausschließlich zum Kaltwassereinlass 52 des Pufferspeichers, so daß das Heißwasser allmählich über die Entladeleitung 54 aus dem Pufferspeicher 12 verdrängt wird, bis ein neuer Heizzyklus eingeleitet wird.During the heating cycle, hot water can also be continuously removed via the discharge line 54 and supplied to the consumer. In this case, a corresponding part of the cold water arriving at the heating return 18 is mixed with the cold water displaced from the buffer store 12 and fed to the mixing point B of the charging circuit. In the period between two heating cycles, in which the charging circuit is switched off, the cold water from the heating return 18 only reaches the cold water inlet 52 of the buffer store, so that the hot water is gradually displaced from the buffer store 12 via the discharge line 54 until a new heating cycle is initiated .

Der Wärmeerzeuger 10 kann beispielsweise ein Heizkessel 70 sein, der aufgrund des Vorhandenseins eines zusätzlichen Pufferspeichers 12 nur einen verhältnismäßig kleinen Wasserinhalt benötigt. In Fig. 3 ist ein bevorzugtes Ausführungsbeispiel eines solchen Heizkessels 70 in einem senkrechten Schnitt dargestellt.The heat generator 10 can be, for example, a boiler 70 which, due to the presence of a additional buffer memory 12 only requires a relatively small water content. In Fig. 3, a preferred embodiment of such a boiler 70 is shown in a vertical section.

Der Heizkessel enthält eine zur Frontplatte 72 hin einseitig offene Brennkammer 74, in die durch eine Öffnung 76 in der Frontplatte 72 hindurch das Brennerrohr 78 eines Öl- oder Gasgebläsebrenners einführbar ist. Die in der Brennerflamme 80 entstehenden Verbrennungsgase (Pfeile 82) werden in der Brennkammer zur Frontseite hin umgekehrt und gelangen dort über die Öffnung 84 und die spiralig gebogenen Leitbleche 86 im Bereich der Frontplatte 72 radial nach außen, um von dort über den Ringraum 88 zu dem Abgassammler 90 und dem Austrittsstutzen 92 geleitet zu werden. Sowohl die Frontplatte 72 als auch der den Ringraum 88 und den Abgassammler 90 umgebende Mantel 93 sind wassergekühlt. Der Wassereinlaß 20 und der Heißwasserauslaß 24 des Heizkessels 70 befinden sich an einander gegenüberliegenden Stellen des Wassermantels 92,94 im Bereich je eines über Durchtrittsöffnungen 100 mit dem Wassermantel 92,94 verbundenen rohrförmigen Sammlers 102,104. Die gekrümmten Leitbleche 86 sind als Wärmeleitungsrippen ausgebildet, die den Wärmeübergang zur wassergekühlten Frontplatte 72 verbessern und für eine weitgehend gleichmäßige Temperaturverteilung sorgen. Auch im Bereich des Ringraums 88 sind als Wärmeleitungsrippen ausgebildete Leitbleche 106 vorgesehen, die unter Vergrößerung des Strömungswegs und Verbesserung des Wärmeübergangs schraubenförmig gewunden sind. Der Abgassammler 90 ist an seiner wassergekühlten Nachschaltheizfläche 94 gleichfalls mit Rippen 108 versehen und weist einen nach Maßgabe der Volumenverringerung der Verbrennungsgase in Strömungsrichtung abnehmenden Strömungsquerschnitt auf. Der innere Totraum des Abgassammlers 90 ist zu diesem Zweck mit einem Verdrängungskörper 110 ausgefüllt.The boiler contains a combustion chamber 74 which is open on one side towards the front plate 72 and into which the burner tube 78 of an oil or gas blower burner can be inserted through an opening 76 in the front plate 72. The combustion gases generated in the burner flame 80 (arrows 82) are reversed to the front in the combustion chamber and reach the opening 84 and the spirally curved baffles 86 in the region of the front plate 72 radially outward, from there via the annular space 88 to the Exhaust collector 90 and the outlet port 92 to be directed. Both the front plate 72 and the jacket 93 surrounding the annular space 88 and the exhaust manifold 90 are water-cooled. The water inlet 20 and the hot water outlet 24 of the boiler 70 are located at mutually opposite points of the water jacket 92, 94 in the area of a tubular collector 102, 104 connected to the water jacket 92, 94 via passage openings 100. The curved baffles 86 are designed as heat conduction ribs, which improve the heat transfer to the water-cooled front plate 72 and ensure a largely uniform temperature distribution. In the area of the annular space 88 there are also guide plates 106 designed as heat conduction ribs, which are helically wound to increase the flow path and improve the heat transfer. The exhaust manifold 90 is also provided with ribs 108 on its water-cooled secondary heating surface 94 and has one in accordance with the volume reduction of the combustion gases in the flow direction decreasing flow cross-section. For this purpose, the inner dead space of the exhaust manifold 90 is filled with a displacement body 110.

Um das Innere des Heizkessels 70 zu Wartungs- und Reinigungszwecken zugänglich zu machen, sind der die Brennkammer 74 enthaltende zylindrische Teil und der Abgassammler 90 an einer Flanschverbindung 112 lösbar miteinander verbunden. Die Verbindung des Wassermantels 92,94 dieser beiden Teile kann dabei innerhalb der Flanschverbindung 112 oder mit Hilfe von Verbindungsrohren hergestellt werden.In order to make the interior of the boiler 70 accessible for maintenance and cleaning purposes, the cylindrical part containing the combustion chamber 74 and the exhaust manifold 90 are detachably connected to one another at a flange connection 112. The connection of the water jacket 92, 94 of these two parts can be produced within the flange connection 112 or with the aid of connecting pipes.

Der Heizkessel 70, der Pufferspeicher 12 und der Dreiwegemischer 14 für den Anschluß des Heizungsvor-und -rücklaufs 16,18 werden zweckmäßig in einem gemeinsamen wärmegedämmten Gehäuse angeordnet. Für die Versorgung eines Einfamilienhauses reicht ein Heizkessel mit einem Wasserinhalt von ca. 15 bis 25 Litem aus, während der Pufferspeicher einen Inhalt von etwa 100 bis 200 Litern haben sollte. Auch bei größeren Heizanlagen, die eine größere Brennerleistung erfordern, wird der Kesselinhalt kaum mehr als 35 Liter betragen müssen.The boiler 70, the buffer store 12 and the three-way mixer 14 for connecting the heating flow and return 16, 18 are expediently arranged in a common, thermally insulated housing. A boiler with a water content of approx. 15 to 25 liters is sufficient to supply a detached house, while the buffer storage should have a content of approx. 100 to 200 liters. Even with larger heating systems that require a higher burner output, the boiler content will hardly have to be more than 35 liters.

Innerhalb oder außerhalb des wärmegedämmten Gehäuses kann außerdem noch ein nicht dargestellter Warmwasserbereiter vorgesehen werden, dessen Wasserinhalt über einen zusätzlichen, vom Pufferspeicher 12 gespeisten Heizwasserkreislauf aufheizbar ist.A water heater (not shown) can also be provided inside or outside the thermally insulated housing, the water content of which can be heated via an additional heating water circuit fed by the buffer store 12.

Gemäß einem weiteren nicht dargestellten Ausführungsbeispiel -kann der Wärmeerzeuger 10 auch als wassergekühlte Wärmepumpe ausgebildet werden. Mit Hilfe der beschriebenen Regelmechanismen unter Verwendung eines Pufferspeichers 12 und einer Bypassleitung 36 kann eine solche Wärmepumpe unabhängig von der augenblicklichen Leistungsanforderung unter konstanten, an die Auslegungsparameter der Wärmepumpe optimal angepaßten Betriebsbedingungen betrieben werden.According to a further exemplary embodiment, not shown, the heat generator 10 can also be designed as a water-cooled heat pump. With the help of Control mechanisms described using a buffer memory 12 and a bypass line 36, such a heat pump can be operated regardless of the current power requirement under constant operating conditions optimally adapted to the design parameters of the heat pump.

Claims (24)

1. Heizanlage mit einem einen Wassereinlaß (20) und einen Heißwasserauslaß (24) aufweisenden Wärmeerzeuger (10) und mindestens einem über einen Heizungsvorlauf (16) und einen Heizungsrücklauf (18) gegebenenfalls unter Zwischenschaltung eines Mischers (14) mit dem Wärmeerzeuger (10) verbindbaren Heizwasserkreislauf, dadurch gekennzeichnet , daß der Heißwasserauslaß (24) des Wärmeerzeugers (10) unter Bildung eines Ladekreislaufs mit einem Heißwassereinlaß (30) eines Pufferspeichers (12) verbindbar ist, der einen mit dem Wassereinlaß (20) des Wärmeerzeugers verbindbaren Kaltwasserauslaß (32) aufweist, daß von dem Ladekreislauf von einer vor dem Heißwassereinlaß (30) des Pufferspeichers (12) oder einer im Heißwasserbereich des Pufferspeichers (12) befindlichen Stelle (35,38) eine mit dem Wassereinlaß (20) des Wärmeerzeugers (10) verbindbare Bypassleitung (36) abgezweigt ist, daß im Ladekreislauf vor der Abzweigung (35,38) oder hinter der Einmündung (B) der Bypassleitung (36) eine Ladepumpe (22) angeordnet ist, und daß der Heizungsvorlauf (16) des Heizwasserkreislaufs über eine Entladeleitung (54) an einen Heißwasserauslaß (50) des Pufferspeichers (12) anschließbar ist, während der Heizungsrücklauf (18) mit dem Wassereinlaß (20) des Wärmeerzeugers und/oder mit einem Kaltwassereinlaß (52) des Pufferspeichers verbindbar ist.1. Heating system with a water inlet (20) and a hot water outlet (24) having a heat generator (10) and at least one via a heating flow (16) and a heating return (18), optionally with the interposition of a mixer (14) with the heat generator (10) Connectable heating water circuit, characterized in that the hot water outlet (24) of the heat generator (10) can be connected to form a charging circuit with a hot water inlet (30) of a buffer store (12) which has a cold water outlet (32) which can be connected to the water inlet (20) of the heat generator. has that of the charging circuit from a before the hot water inlet (30) of the buffer store (12) or a point (35, 38) located in the hot water area of the buffer store (12), a bypass line (36) which can be connected to the water inlet (20) of the heat generator (10) is branched off in the charging circuit before the branch (35, 38) or behind the mouth (B) of the bypass line (36) a charging pump (22) is arranged, and that the heating flow (16) of the heating water circuit can be connected via a discharge line (54) to a hot water outlet (50) of the buffer tank (12) , while the heating return (18) can be connected to the water inlet (20) of the heat generator and / or to a cold water inlet (52) of the buffer store. 2. Heizanlage nach Anspruch 1, dadurch gekennzeichnet , daß das Verhältnis der Durchflußmengen durch die zum Heißwassereinlaß (30) des Pufferspeichers (12) führende Ladeleitung (26) und die Bypassleitung (36) nach Maßgabe der im Bereich des Heißwasserauslasses (24) des Wärmeerzeugers (10) gemessenen Wassertemperatur einstellbar ist.2. Heating system according to claim 1, characterized in that the ratio of the flow rates through the hot water inlet (30) of the buffer store (12) leading charging line (26) and the bypass line (36) in accordance with the in the area of the hot water outlet (24) of the heat generator (10) measured water temperature is adjustable. 3. Heizanlage nach Anspruch 2, dadurch gekennzeichnet , daß in der Ladeleitung (26) ein steuerbares Wasserventil (40) angeordnet ist.3. Heating system according to claim 2, characterized in that a controllable water valve (40) is arranged in the charging line (26). 4. Heizanlage nach Anspruch 2, dadurch gekennzeichnet , daß an der Abzweigstelle (35) zwischen der Ladeleitung (26) und der Bypassleitung (36) ein steuerbares Verteilventil (42) angeordnet ist.4. Heating system according to claim 2, characterized in that a controllable distribution valve (42) is arranged at the branch point (35) between the charging line (26) and the bypass line (36). 5. Heizanlage nach Anspruch 2, dadurch gekennzeichnet, daß die Bypassleitung (36) und eine vom Kaltwasserauslaß (32) des Pufferspeichers (12) kommende Leitung (34) an zwei Eingänge eines mit seinem Ausgang zum Wassereinlaß (20) des Wärmeerzeugers (10) führenden steuerbaren Mischventils (46) angeschlossen sind.5. Heating system according to claim 2, characterized in that the bypass line (36) and one of the cold water outlet (32) of the buffer store (12) coming line (34) to two inputs one with its output to the water inlet (20) of the heat generator (10) leading controllable mixing valve (46) are connected. 6. Heizanlage nach einem der Ansprüche 3 bis 5, dadurch gekennzeichnet , daß das steuerbare Wasserventil (40), Verteilventil (42) oder Mischventil (46) über einen im Bereich des Heißwasserauslasses (24) des Wärmeerzeugers (10) angeordneten Temperaturfühler (39) ansteuerbar ist.6. Heating system according to one of claims 3 to 5, characterized in that the controllable water valve (40), distribution valve (42) or mixing valve (46) via a in the region of the hot water outlet (24) of the heat generator (10) arranged temperature sensor (39) is controllable. 7. Heizanlage nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet , daß die Entladeleitung (54) des Pufferspeichers (12) und eine vom Heizungsrücklauf (18) abgezweigte Leitung an die Eingänge (56,58) eines zum Heizungsvorlauf (16) führenden steuerbaren Mischventils (14) angeschlossen sind.7. Heating system according to one of claims 1 to 6, characterized in that the discharge line (54) of the buffer memory (12) and a line branched off from the heating return (18) to the inputs (56, 58) of a heating flow (16) leading controllable Mixing valve (14) are connected. 8. Heizanlage nach einem der Ansprüche 1 bis 7, d a - durch gekennzeichnet , daß der Pufferspeicher (12) als Schichtspeicher ausgebildet ist, dessen Heißwasserein- und -auslässe (30,50) an der Oberseite und dessen Kaltwasseraus- und -einlässe (32,52) an der Unterseite eines wärmeisolierten Speicherbehälters (28) angeordnet sind.8. Heating system according to one of claims 1 to 7, characterized in that the buffer store (12) is designed as a stratified store, the hot water inlets and outlets (30, 50) of which on the top and the cold water outlets and inlets (32 , 52) are arranged on the underside of a heat-insulated storage container (28). 9. Heizanlage nach Anspruch 8, dadurch gekennzeichnet , daß im oberen und unteren Bereich des Speicherbehälters (28) je ein Temperaturfühler (62,64) eines Reglers (66) für die Ansteuerung einer Wärmequelle des Wärmeerzeugers (10) angeordnet ist.9. Heating system according to claim 8, characterized in that a temperature sensor (62, 64) of a controller (66) for controlling a heat source of the heat generator (10) is arranged in the upper and lower region of the storage container (28). 10. Heizanlage nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet , daß der Wärmeerzeuger (10),der Pufferspeicher (12) und gegebenenfalls das an den Heizungsvorlauf (16) und den Heizungsrücklauf (18) angeschlossene Mischventil (14) in einem gemeinsamen wärmegedämmten Gehäuse angeordnet sind.10. Heating system according to one of claims 1 to 9, characterized in that the Heat generator (10), the buffer store (12) and optionally the mixing valve (14) connected to the heating flow (16) and the heating return (18) are arranged in a common, thermally insulated housing. 11. Heizanlage nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet , daß der Wärmeerzeuger (10) als Heizkessel (70) mit kleinem Wasserinhalt ausgebildet ist und daß der Pufferspeicher (12) ein Mehrfaches des Wasserinhalts des Heizkessels aufweist.11. Heating system according to one of claims 1 to 10, characterized in that the heat generator (10) is designed as a boiler (70) with a small water content and that the buffer memory (12) has a multiple of the water content of the boiler. 12. Heizanlage nach Anspruch 11, dadurch gekennzeichnet , daß der Heizkessel (70) einen Wasserinhalt von weniger als 35 Liter, vorzugsweise zwischen 15 und 20 Liter aufweist.12. Heating system according to claim 11, characterized in that the boiler (70) has a water content of less than 35 liters, preferably between 15 and 20 liters. 13. Heizanlage nach Anspruch 11 oder 12, dadurch gekennzeichnet , daß eine zur Frontplatte (72) des Heizkessels (70) hin einseitig offene Brennkammer (74) für einen Gas- oder Ölgebläsebrenner (78) vorgesehen ist, daß die Frontplatte (72) zumindest teilweise wassergekühlt ist und als Wärmeleitungsrippen ausgebildete Leitbleche (86) zur Umlenkung der aus der Brennkammer (74) austretenden Verbrennungsgase (82) in einen die Brennkammer umgebenden, an seiner Außenfläche wassergekühlten Ringraum (88) trägt, und daß der Ringraum (88) in einen eine wassergekühlte Nachschaltheizfläche (94) aufweisenden Abgassammler (90) mündet.13. Heating system according to claim 11 or 12, characterized in that a to the front plate (72) of the boiler (70) towards one side open combustion chamber (74) for a gas or oil blowing burner (78) is provided that the front plate (72) at least is partially water-cooled and baffles (86) designed as heat-conducting fins for deflecting the combustion gases (82) emerging from the combustion chamber (74) into an annular space (88) surrounding the combustion chamber and water-cooled on its outer surface, and for the annular space (88) into one a water-cooled secondary heating surface (94) has an exhaust manifold (90). 14. Heizanlage nach Anspruch 13, dadurch gekennzeichnet , daß die an der Frontplatte (72) angeordneten Leitbleche (86) spiralförmig gekrümmt sind.14. Heating system according to claim 13, characterized in that the guide plates (86) arranged on the front plate (72) are curved spirally. 15. Heizanlage nach Anspruch 13 oder 14, dadurch gekennzeichnet , daß die wassergekühlte Außenfläche (93) des Ringraumes (88) schraubenförmig gewundene, als Wärmeleitungsrippen ausgebildete Leitbleche (106) für die Verbrennungsgase (82) trägt.15. Heating system according to claim 13 or 14, characterized in that the water-cooled outer surface (93) of the annular space (88) carries helically wound, designed as heat conducting fins baffles (106) for the combustion gases (82). 16. Heizanlage nach einem der Ansprüche 13 bis 15, dadurch gekennzeichnet , daß der Abgassammler an seiner wassergekühlten Nachschaltheizfläche (94) berippt ist und einen nach Maßgabe der Volumenverringerung der Verbrennungsgase in Strömungsrichtung abnehmenden Strömungsquerschnitt aufweist.16. Heating system according to one of claims 13 to 15, characterized in that the exhaust manifold is finned on its water-cooled secondary heating surface (94) and has a decreasing flow cross section in accordance with the volume reduction of the combustion gases in the flow direction. 17. Heizanlage nach einem der Ansprüche 11 bis 16, dadurch gekennzeichnet , daß der die Brennkammer (74) enthaltende Teil des Heizkessels (70) mit dem Abgassammler (90) lösbar verbunden ist.17. Heating system according to one of claims 11 to 16, characterized in that the part of the boiler (70) containing the combustion chamber (74) is detachably connected to the exhaust manifold (90). 18. Heizanlage nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet , daß der Wärmeerzeuger (10) eine wassergekühlte Wärmepumpe ist.18. Heating system according to one of claims 1 to 10, characterized in that the heat generator (10) is a water-cooled heat pump. 19. Heizanlage nach einem der Ansprüche 1 bis 19, dadurch gekennzeichnet , daß einer der Heizwasserkreisläufe durch einen Wärmetauscher eines Warmwasserbereiters geführt ist, der vorzugsweise in dem gemeinsamen wärmegedämmten Gehäuse angeordnet ist.19. Heating system according to one of claims 1 to 19, characterized in that one of the heating water circuits is passed through a heat exchanger of a water heater, which is preferably arranged in the common thermally insulated housing. 20. Verfahren zum Betrieb einer Heizanlage, bei welchem Heizwasser durch einen Wärmeerzeuger und mindestens einen an den Wärmeerzeuger angeschlossenen Heizwasserkreislauf umgewälzt wird, dadurch gekennzeichnet, daß das am Wärmeerzeuger austretende aufgeheizte Wasser nach Maßgabe der Austrittstemperatur anteilmäßig auf einen einen Pufferspeicher enthaltenden Ladezweig und einen zur Einlaßstelle des Wärmeerzeugers zurückführenden Bypasszweig verteilt wird, daß dem durch den Bypasszweig zurückgeleiteten Wasser Kaltwasser aus dem Pufferspeicher und/oder dem Heißwasserkreislauf beigemischt wird und daß der Heizwasserkreislauf mit Heißwasser aus dem Pufferspeicher gespeist wird.20. A method of operating a heating system, in which heating water is circulated by a heat generator and at least one heating water circuit connected to the heat generator, characterized in that the exiting at the heat generator heated water is distributed proportionally to a charging branch containing a buffer storage and a bypass branch returning to the inlet point of the heat generator in accordance with the outlet temperature, that cold water from the buffer storage and / or the hot water circuit is mixed with the water returned through the bypass branch and that the heating water circuit with hot water from the Buffer memory is fed. 21. Verfahren nach Anspruch 20, dadurch gekennzeichnet , daß zu Beginn eines Heizzyklus das aus dem Wärmeerzeuger austretende Wasser zunächst vollständig über den Bypasszweig umgewälztwird, bis eine vorgegebene Austrittstemperatur erreicht ist.21. The method according to claim 20, characterized in that at the beginning of a heating cycle, the water emerging from the heat generator is first completely circulated through the bypass branch until a predetermined outlet temperature is reached. 22. Verfahren nach Anspruch 20 oder 21, dadurch gekennzeichnet , daß am Ende eines Heizzyklus das im Wärmeerzeuger befindliche Wasser durch Kaltwasser aus dem Pufferspeicher verdrängt wird.22. The method according to claim 20 or 21, characterized in that at the end of a heating cycle, the water in the heat generator is displaced by cold water from the buffer store. 23. Verfahren nach einem der Ansprüche 20 bis 22, dadurch gekennzeichnet , daß zu Beginn eines Heizzyklus das im Wärmeerzeuger befindliche Wasser durch Heißwasser aus dem Pufferspeicher verdrängt wird.23. The method according to any one of claims 20 to 22, characterized in that at the beginning of a heating cycle the water in the heat generator is displaced by hot water from the buffer store. 24. Verfahren nach einem der Ansprüche 20 bis 23, dadurch gekennzeichnet , daß im Pufferspeicher von dem oben befindlichen Heißwassereinlaß zum unten befindlichen Kaltwasserauslaß ein schichtweise monoton abnehmender Temperaturverlauf aufrechterhalten wird, daß die Wassertemperatur in kleinem Abstand unterhalb des Heißwassereinlasses und oberhalb des Kaltwasserauslasses gemessen wird und daß bei Unter- bzw. Überschreiten einer jeweiligen Solltemperatur ein Heizzyklus ausgelöst bzw. beendet wird.24. The method according to any one of claims 20 to 23, characterized in that a layer-wise monotonically decreasing temperature profile is maintained in the buffer storage from the top hot water inlet to the bottom cold water outlet, that the water temperature is measured at a short distance below the hot water inlet and above the cold water outlet and that when falling below or exceeding a respective Target temperature a heating cycle is triggered or ended.
EP84102841A 1983-03-18 1984-03-15 Heating installation Expired EP0122475B1 (en)

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DE19833309741 DE3309741A1 (en) 1983-03-18 1983-03-18 HEATING SYSTEM AND METHOD FOR THE OPERATION THEREOF

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Cited By (6)

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Publication number Priority date Publication date Assignee Title
GB2160957A (en) * 1984-06-27 1986-01-02 Gledhill Water Storage Improvements relating to water heating apparatus
EP0238776A2 (en) * 1986-02-21 1987-09-30 MANNESMANN Aktiengesellschaft Method of running a heating installation and heat accumulator for this heating installation
FR2617579A1 (en) * 1987-07-03 1989-01-06 Airelec Ind Central heating boiler for a forced-air gas burner comprising a dry hearth and a heating resistor
DE3809251A1 (en) * 1988-03-18 1989-10-12 Josef Moosmann Heating installation and method of operating a heating installation
DE3917930A1 (en) * 1988-06-07 1989-12-14 Vaillant Joh Gmbh & Co Heating installation
CN109405055A (en) * 2018-10-17 2019-03-01 河北建筑工程学院 A kind of heat supply and accumulation of heat decouple operating system with heat source

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DE102004001170A1 (en) * 2004-01-07 2005-08-04 Cetetherm Gmbh Bypass in the reaction storage advance
CN104964328A (en) * 2015-06-15 2015-10-07 上海意利法暖通科技有限公司 Water mixing and pressurizing distributing device

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US4175698A (en) * 1977-11-11 1979-11-27 Tekram Associates, Inc. Method and apparatus for conservation of energy in a hot water heating system
DE3145636A1 (en) * 1980-12-01 1982-07-01 Rembert 6845 Hohenems Zortea Heating installation for hot-water preparation

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4175698A (en) * 1977-11-11 1979-11-27 Tekram Associates, Inc. Method and apparatus for conservation of energy in a hot water heating system
DE3145636A1 (en) * 1980-12-01 1982-07-01 Rembert 6845 Hohenems Zortea Heating installation for hot-water preparation

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2160957A (en) * 1984-06-27 1986-01-02 Gledhill Water Storage Improvements relating to water heating apparatus
EP0238776A2 (en) * 1986-02-21 1987-09-30 MANNESMANN Aktiengesellschaft Method of running a heating installation and heat accumulator for this heating installation
EP0238776A3 (en) * 1986-02-21 1988-03-02 Mannesmann Aktiengesellschaft Method of running a heating installation and heat accumulator for this heating installation
FR2617579A1 (en) * 1987-07-03 1989-01-06 Airelec Ind Central heating boiler for a forced-air gas burner comprising a dry hearth and a heating resistor
DE3809251A1 (en) * 1988-03-18 1989-10-12 Josef Moosmann Heating installation and method of operating a heating installation
DE3917930A1 (en) * 1988-06-07 1989-12-14 Vaillant Joh Gmbh & Co Heating installation
CN109405055A (en) * 2018-10-17 2019-03-01 河北建筑工程学院 A kind of heat supply and accumulation of heat decouple operating system with heat source

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ATE44410T1 (en) 1989-07-15
DE3309741A1 (en) 1984-09-20
DE3478871D1 (en) 1989-08-10
EP0122475B1 (en) 1989-07-05
EP0122475A3 (en) 1986-02-26

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