EP0122475A2 - Installation de chauffage - Google Patents

Installation de chauffage 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)
English (en)
Other versions
EP0122475A3 (en
EP0122475B1 (fr
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/de
Publication of EP0122475A2 publication Critical patent/EP0122475A2/fr
Publication of EP0122475A3 publication Critical patent/EP0122475A3/de
Application granted granted Critical
Publication of EP0122475B1 publication Critical patent/EP0122475B1/fr
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)
  • Percussion Or Vibration Massage (AREA)
  • Heating, Cooling, Or Curing Plastics Or The Like In General (AREA)
  • Control And Other Processes For Unpacking Of Materials (AREA)
  • Polarising Elements (AREA)
  • Housings, Intake/Discharge, And Installation Of Fluid Heaters (AREA)
EP84102841A 1983-03-18 1984-03-15 Installation de chauffage Expired EP0122475B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84102841T ATE44410T1 (de) 1983-03-18 1984-03-15 Heizanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3309741 1983-03-18
DE19833309741 DE3309741A1 (de) 1983-03-18 1983-03-18 Heizanlage sowie verfahren zu deren betrieb

Publications (3)

Publication Number Publication Date
EP0122475A2 true EP0122475A2 (fr) 1984-10-24
EP0122475A3 EP0122475A3 (en) 1986-02-26
EP0122475B1 EP0122475B1 (fr) 1989-07-05

Family

ID=6193858

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84102841A Expired EP0122475B1 (fr) 1983-03-18 1984-03-15 Installation de chauffage

Country Status (3)

Country Link
EP (1) EP0122475B1 (fr)
AT (1) ATE44410T1 (fr)
DE (2) DE3309741A1 (fr)

Cited By (6)

* 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
EP0238776A3 (en) * 1986-02-21 1988-03-02 Mannesmann Aktiengesellschaft Method of running a heating installation and heat accumulator for this heating installation
FR2617579A1 (fr) * 1987-07-03 1989-01-06 Airelec Ind Chaudiere de chauffage central pour bruleur a air souffle, comprenant un foyer sec et une resistance chauffante
DE3809251A1 (de) * 1988-03-18 1989-10-12 Josef Moosmann Heizanlage und verfahren zum betrieb einer heizanlage
DE3917930A1 (de) * 1988-06-07 1989-12-14 Vaillant Joh Gmbh & Co Heizungsanlage
CN109405055A (zh) * 2018-10-17 2019-03-01 河北建筑工程学院 一种供热和蓄热同热源解耦运行系统

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004001170A1 (de) * 2004-01-07 2005-08-04 Cetetherm Gmbh Bypaß im Reaktionsspeichervorlauf
CN104964328A (zh) * 2015-06-15 2015-10-07 上海意利法暖通科技有限公司 一种混水加压分配装置

Family Cites Families (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
AT382450B (de) * 1980-12-01 1987-02-25 Zortea Rembert Heizanlage zur warmwasserbereitung

Cited By (6)

* 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
EP0238776A3 (en) * 1986-02-21 1988-03-02 Mannesmann Aktiengesellschaft Method of running a heating installation and heat accumulator for this heating installation
FR2617579A1 (fr) * 1987-07-03 1989-01-06 Airelec Ind Chaudiere de chauffage central pour bruleur a air souffle, comprenant un foyer sec et une resistance chauffante
DE3809251A1 (de) * 1988-03-18 1989-10-12 Josef Moosmann Heizanlage und verfahren zum betrieb einer heizanlage
DE3917930A1 (de) * 1988-06-07 1989-12-14 Vaillant Joh Gmbh & Co Heizungsanlage
CN109405055A (zh) * 2018-10-17 2019-03-01 河北建筑工程学院 一种供热和蓄热同热源解耦运行系统

Also Published As

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

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