EP0275401A2 - Chaudière et procédure pour exploiter cette chaudière - Google Patents

Chaudière et procédure pour exploiter cette chaudière Download PDF

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Publication number
EP0275401A2
EP0275401A2 EP87117187A EP87117187A EP0275401A2 EP 0275401 A2 EP0275401 A2 EP 0275401A2 EP 87117187 A EP87117187 A EP 87117187A EP 87117187 A EP87117187 A EP 87117187A EP 0275401 A2 EP0275401 A2 EP 0275401A2
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EP
European Patent Office
Prior art keywords
combustion chamber
wall
boiler according
burner
boiler
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
EP87117187A
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German (de)
English (en)
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EP0275401B1 (fr
EP0275401A3 (en
Inventor
Rolf Bommer
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Individual
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Individual
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Application filed by Individual filed Critical Individual
Priority to AT87117187T priority Critical patent/ATE72319T1/de
Publication of EP0275401A2 publication Critical patent/EP0275401A2/fr
Publication of EP0275401A3 publication Critical patent/EP0275401A3/de
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Classifications

    • 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
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/2007—Arrangement or mounting of control or safety devices for water heaters
    • F24H9/2035—Arrangement or mounting of control or safety devices for water heaters using fluid fuel
    • 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
    • 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
    • F24H1/44—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with combinations of two or more of the types covered by groups F24H1/24 - F24H1/40 , e.g. boilers having a combination of features covered by F24H1/24 - F24H1/40
    • 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
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/355—Control of heat-generating means in heaters
    • F24H15/36—Control of heat-generating means in heaters of burners

Definitions

  • the invention relates to a method for operating a boiler according to the preamble of patent claim 1 and a boiler according to the preamble of patent claim 6.
  • a boiler is known in which a forced draft burner burns with a horizontally directed flame in a combustion chamber, which is arranged horizontally and on its lower side which is essentially parallel to the axis of the flame of the forced draft burner over its entire length and Width opens against a flue gas collecting space penetrated by heat exchangers.
  • the wall of the firebox is cooled by a water jacket through which the domestic water to be heated and the water from the heating system flow.
  • the water jacket cooling the wall of the combustion chamber absorbs the main part of the heat generated by the burner, while the heat exchangers arranged in the subsequent flue gas collecting chamber only act as a post-heating surface, which cool the flue gases to the temperature of around 160 to 180 ° C, with which the flue gases enter the fireplace.
  • the large volume of the water jacket surrounding the wall of the combustion chamber causes this wall to be strongly cooled, and the forced draft burner must therefore be operated with a constant burner output which is matched to the cooling of the combustion chamber wall.
  • a reduction in the burner output e.g. to adapt to a lower heating requirement in the transition period, would lead to subcooling of the flame, which would result in a high pollutant content in the flue gases and even condensation on the combustion chamber wall.
  • the capacity of the forced draft burner cannot be reduced to adapt to a reduced heating requirement.
  • the burner is operated intermittently at its full output. This intermittent operation in turn results in frequent burner starts, in each of which the entire volume of the water jacket cooling the combustion chamber wall must be warmed up. In this heating phase, there is always undercooling of the burner flame, which results in a high pollutant content and poor efficiency.
  • combustion aids are preferably installed in small boilers with a low output of up to approx. 40 kW.
  • the combustion chamber wall which is enclosed and cooled by the water jacket, is a cylindrical casting wall, into which a stainless steel tube is coaxially inserted, into which the burner flame burns.
  • the stainless steel tube is held at a distance from the cast wall by inwardly directed ribs.
  • the hot combustion chamber formed by the stainless steel tube is therefore practically not cooled. Due to the low heat capacity and the lack of cooling, this combustion chamber quickly becomes high when the burner is started Temperature on, so that residue-free combustion of the fuel is guaranteed not only during continuous operation, but also very quickly when the burner is started. Only when the combustion gases flow between the combustion chamber and the casting wall of the combustion chamber are heat removed from them.
  • the high temperature in the hot combustion chamber and the long residence time of the combustion gases in the hot combustion chamber cause a strong conversion of the nitrogen in the air into NO x , so that the exhaust gases have a high proportion of harmful nitrogen oxides.
  • the combustion chamber wall coaxially surrounding the hot combustion chamber cannot adequately extract the heat from the hot flue gases.
  • downstream heating surfaces are still necessary in order to achieve sufficient efficiency.
  • the combustion chamber wall which is generally made of cast iron with the surrounding water jacket, has a high heat capacity, so that the boiler has a high inertia.
  • the heat capacity is particularly influenced by the fact that the combustion chamber has to be of large volume in order to accommodate the hot combustion chamber used and to form a sufficient heat exchanger surface.
  • the invention has for its object to provide a boiler which has at residue free as possible combustion of fossil fuels the lowest possible NO x moiety of the exhaust gases, preferably also in an adjustment of the burner output in a changing heat demand.
  • the essential idea of the invention is to extract the heat from the combustion gases not at the wall of the combustion chamber, but practically exclusively at the heat exchangers of the flue gas collecting space.
  • the wall of the firebox is cooled only very slightly, this cooling being dimensioned such that the temperature on the inside of the wall of the firebox does not rise above about 600.degree. C. even during continuous operation with full burner output.
  • This gentle cooling of the combustion chamber wall causes the combustion gases at the edge of the burner flame to be cooled very quickly to a temperature at which practically no appreciable formation of NO x occurs.
  • the cooling of the combustion chamber wall does not serve the purpose of heating the heating or service water, the cooling is kept so low that undercooling of the combustion gases on the combustion chamber wall does not occur even when the burner output is reduced.
  • the burner output can therefore be reduced to approximately 1/10 of the maximum output without the cooling of the wall of the combustion chamber leading to a cooling of the combustion gases below the temperature of approximately 180 ° C., at which the combustion of the fuels no longer takes place completely.
  • the burner output can therefore be varied within a very large range, preferably from 1 to 10, without the burner area being lower performance an incomplete combustion and condensation occurs on the wall of the combustion chamber and without the NO x content of the exhaust gases increasing in the area of high burner output.
  • the hot combustion gases only come into contact with the heat exchangers through which the combustion heat is removed when they have already left the combustion chamber and have entered the flue gas collecting chamber. The cooling of the combustion gases at the heat exchangers can therefore not cause the flame to cool down.
  • the combustion chamber can have a particularly small volume. It only has to be so large that it essentially encloses the flame of the burner.
  • the small volume of the combustion chamber also shortens the residence time of the combustion gases near the flame and thus further reduces the NO x generation.
  • the combustion chamber encloses the flame of the burner on three long sides and on the end face opposite the burner, while it is open on the fourth long side against the flue gas collecting space. This flame surrounds the flame through the recirculation of the hot combustion gases against the direction of the flame in the manner of the reverse flame in boilers with a hot combustion chamber.
  • the lateral opening of the combustion chamber towards the flue gas collection chamber additionally causes the combustion gases to circulate about an axis parallel to the flame, so that two cylinders of the combustion gases circulating helically circulating against the direction of the flame flow bilaterally in the combustion chamber the.
  • the combustion gases are guided along the preferably barrel-shaped, longitudinal wall of the combustion chamber and gently cooled, so that their temperature does not rise above the temperature at which NO x formation begins to increase. Due to the roller-shaped circulation, the gases cooled on the combustion chamber wall are partially returned to the core of the flame, so that a complete residue-free combustion of the fossil fuels is guaranteed.
  • a part of the circulating gases continuously flows to the heat exchangers in the flue gas collecting space.
  • the flue gas collecting space is preferably arranged below the combustion chamber. This favors the flow of the flue gases increasingly cooled at the heat exchanger and, in particular, an advantageous condensate discharge at the bottom of the flue gas collecting space is possible if the boiler is designed as a so-called condensing boiler, in which the flue gases on the outlet side of the heat exchanger are cooled to below the dew point that the water vapor contained in the exhaust gases is condensed and separated with the remaining pollutant (in particular sulfur oxides, ash, fuel oil residues).
  • the heat exchangers which preferably pass through the flue gas collecting space as pipe registers, can be designed with a relatively low heat capacity, so that the boiler reacts with low inertia and low energy losses.
  • the wall of the combustion chamber is thin-walled with a low heat capacity and is corrosion-resistant at least on the inside.
  • the low heat capacity be acts a minimal inertia of the combustion chamber wall, so that it reaches the desired optimal temperature between about 300 and 500 ° C within seconds when the burner is ignited.
  • the supercooling of the flame and the associated pollutant emissions are therefore minimal even when the burner is started.
  • the burner output can also be varied without adversely affecting the efficiency and the pollutant content of the exhaust gases, the burner output can be reduced with a lower heat requirement, so that the number of burner starts can be considerably reduced.
  • the corrosion-resistant, gently cooled firebox wall with low heat capacity required according to the invention can be implemented in different ways.
  • the wall of the firebox can consist of two layers.
  • the inner wall layer is thin-walled and consists of a corrosion-resistant material, preferably of a steel sheet with a thickness of about 0.5 to 2.5 mm or of a thin-walled ceramic material.
  • the outer wall layer is preferably loosely arranged on the inner wall layer and held on the inner wall layer with a pretension under uniform contact pressure.
  • the outer wall layer preferably consists of a copper or aluminum sheet with a wall thickness of approximately 0.5 to 1.5 mm, on which water-carrying coils are soldered or welded for cooling or are formed as embossed water channels.
  • the externally tensioned over the inner wall layer Outer wall layer has the advantage that the outer wall layer can be replaced in order to adapt its cooling capacity to the burner.
  • the cooling capacity can be controlled by the contact pressure of the outer wall layer against the inner wall layer, for. B. is varied by hydraulic regulation of the bias. With increasing contact pressure, the contact area between the inner and outer wall layer and thus the heat transfer for cooling increases.
  • the good heat-conducting material of the outer wall layer ensures uniform cooling of the entire wall of the combustion chamber despite the small number of coils arranged at a mutual distance.
  • the wall of the firebox can also be made of cast material, e.g. B. cast iron exist, the cooling water leading water channels are cast, which are arranged in small numbers at a mutual distance.
  • cast material e.g. B. cast iron exist
  • the cooling water leading water channels are cast, which are arranged in small numbers at a mutual distance.
  • the burner output is varied over a wide range during operation to adapt to a different heat requirement, it is advantageous to also adapt the cooling of the combustion chamber wall in order to keep its temperature as optimal as possible from about 400 to 500 ° C.
  • the liquid throughput can be controlled through the water channels carrying the cooling water.
  • water is preferably used which is already present in the heat exchangers, preferably in the heat exchanger furthest from the burner warms. This results from the fact that the combustion chamber wall is not intended for heating water, but should only be cooled gently so that the wall temperature does not rise too much.
  • the combustion chamber wall can also be cooled by air.
  • the air heated during cooling of the combustion chamber wall can advantageously be used as combustion air for the forced air burner.
  • the heat exchangers arranged under the combustion chamber are preferably designed such that they only guide the combustion gases from top to bottom and have no horizontal trains for the combustion gases. In addition to the favorable flow conditions for the combustion gases, this has the advantage that any combustion residues, such as soot and the like, cannot deposit on the heat exchangers, but instead fall down through the heat exchangers, so that they are collected and disposed of together with the condensate will. The effectiveness of the heat exchanger is therefore not affected by deposits.
  • a spray device for a cleaning liquid preferably water
  • the cleaning liquid rinses both the wall of the Combustion chamber as well as the heat exchanger and flows down through the heat exchanger, where it is collected and disposed of.
  • the entire boiler can be cleaned in this way if necessary or automatically at predetermined time intervals in an extremely simple manner, without manual cleaning work or even a partial disassembly of the boiler is necessary.
  • the wall of the flue gas collecting space can be produced in one piece with the wall of the combustion chamber, and in the case of a double-layer wall of the combustion chamber with the inner wall layer. Since the combustion chamber is functionally completely separate from the heat exchanger and the flue gas collection chamber, it is also possible to design the heat exchanger and the flue gas collection chamber as separate components which are detachably connected to the combustion chamber in a gas-tight and water-tight manner. As a result, a heat exchanger adapted to the respective requirements can be used in a particularly simple manner in connection with a combustion chamber, which can be produced in series for a wide range of applications. It is also possible to replace the firebox without any other changes to the boiler if this is appropriate to adapt to a future improvement in the burner design. Finally, this has the advantage that the firebox can also be used in connection with heat exchangers and flue gas plenums from other manufacturers.
  • the combustion chamber can have a volume of preferably approx. 6 to 12 dm3.
  • the length to width ratio is preferably between 1.5 and 1.0, while the ratio length to height of the firebox is preferably in the range between 2.0 and 1.0.
  • the boiler consists of a barrel-shaped, curved combustion chamber 1, which is closed on its two axial end faces. In the middle of an end wall there is an opening 9 in which a compressed air oil or gas blower burner (according to DIN 4788, parts 2 to 5) can be used.
  • the flame 10 of the burner burns horizontally in the axial direction into the combustion chamber 1.
  • the combustion chamber 1 is open over its entire axial length and merges into a flue gas collecting chamber 11, which has the same length and width as the combustion chamber 1.
  • the open passage area between the combustion chamber and the flue gas collection space 11 is approximately 1/3 to 1/4 of the entire circumferential surface of the casing of the fire space 1.
  • the flue gas collection space 11 is horizontally penetrated by a heat exchanger 12 which is in the form of a pipe register. Below the heat exchanger 12 there is an outlet 13 through which the flue gas collecting space 11 can be connected to a chimney.
  • the length of the combustion chamber 11 is approximately 1.5 to 1.0 times its width and approximately 2.0 to 1.0 times its height.
  • the total volume of combustion chamber 1 is approximately 6 to 12 dm3.
  • the combustion chamber 1 and the flue gas collecting chamber 11 are enclosed in a gas-tight manner by a common wall 4 which consists of a 0.5 to 2.5 mm thick steel sheet.
  • a common wall 4 which consists of a 0.5 to 2.5 mm thick steel sheet.
  • an outer wall layer 5 is arranged on the outside of the wall 4, which lies in loose contact with the end faces and the peripheral surface areas of the wall 4.
  • the outer wall layer 5 is fixed to the wall 4 by means of screws or pins 14 in the region of the lower edge of the combustion chamber 1.
  • the outer wall layer 5 consists of a copper or aluminum sheet with a thickness of 0.5 to 1.5 mm. It is guided from the attachment points by the screws or pins 14 in two parts upwards over the combustion chamber 1 and z. B.
  • springs 8 seated on the bolts 15 tension the outer wall layer 5 over the wall 4 and bring about a contact pressure of the outer wall layer 5 against the wall 4, which leads to a regionally heat-conducting contact between the wall 4 and the outer wall layer 5.
  • An increase in the pressure of the springs 8 causes a larger contact and thus a better heat transfer between the wall 4 and the outer wall layer 5, while a weaker pressure of the springs 8 leads to less contact and poorer heat transfer.
  • springs 8 preferably hydraulically controllable tensioning means can also be provided, which tension the outer wall layer 5 with an adjustable contact pressure and thus with an adjustable heat transfer over the wall 4.
  • meandering coils 7 are arranged, which are evenly distributed run at a mutual distance on the end and outer surfaces of the outer wall layer 5.
  • the mutual distance between the individual turns of the coils 7 is measured according to the required cooling capacity.
  • the coils 7 can be soldered and welded onto the outer wall layer 5, as shown in FIG. 4, and have a round or oval cross section, as shown in FIG. 4 by the cross sections 7 and 7 '.
  • the outer wall layer can also be a double-skin sheet with embossed channels as coils 7 ⁇ , as is indicated in FIG. 5.
  • a coolant is passed through the coils 7, for which purpose a fraction of the water preheated in the heat exchanger 12 is preferably used, which is branched off in a controllable flow rate via a control valve 6.
  • the hot combustion gases of the flame 10 flow back in an axial recirculation flow 2 against the direction of the flame 10.
  • This recirculation can be further promoted by a bulge 16, indicated in FIG. 1, in the end wall of the combustion chamber 1 opposite the burner. Due to the asymmetrical opening of the combustion chamber 1 against the flue gas collecting chamber 11, the combustion gases flowing back axially receive an additional movement component in the radial direction, which primarily leads the combustion gases flowing upwards from the flame 10 along the cooled combustion chamber wall 4 downwards. A part of the combustion gases guided downward in this way with the radial circulation flow 3 flows through the heat accumulation shear 12 in the flue gas collection chamber 11, while the other part is returned to the flame 10 by the roller-shaped circulation 3.
  • the axial recirculation with the cylindrical rotation on both sides of the flame 10 along the cooled wall 4 results on the one hand in a sufficient return of the combustion gases into the flame 10 to ensure complete combustion, and on the other hand a certain cooling of the combustion gases returned to the flame Too high a flame temperature prevents and thus counteracts the NO x formation.
  • the portion of the hot combustion gases flowing continuously downward into the flue gas collecting space, in conjunction with the small volume of the combustion chamber 1, causes the combustion gases in the combustion chamber 1 to dwell briefly, which likewise counteracts the formation of NO x in the exhaust gases.
  • FIG. 6 shows a second embodiment of the boiler.
  • the combustion chamber 1 with its wall 4 is a separate component, which is detachably connected to the heat exchanger 12 by means of screw bolts 14, which also serve to fasten the outer wall layer 5.
  • the heat exchanger 12 is in turn detachably connected to the subsequent flue gas collecting space 11 by screw bolts 14.
  • the connection between the combustion chamber 1 and the heat exchanger 12 and between the heat exchanger 12 and the flue gas collecting chamber 11 is gas-tight and liquid-tight.
  • a condensate drain 17 is provided in the floor of the flue gas collecting space 11.
  • Figure 7 shows a third embodiment in which the wall 4 of the combustion chamber 1 made of a thin-walled cast material, for. B. consists of a cast metal or a ceramic material.
  • the coils 7 are formed by channels cast onto the wall 4.
  • the heat exchanger 12, the flue gas collection chamber 11 and the connection of the combustion chamber 1 with the heat exchanger 12 and the heat exchanger 12 with the flue gas collection chamber 11 correspond to the exemplary embodiment in FIG. 6.
  • the cold return water of a heating system is fed to the heat exchanger 12 via a return line R1, in which it is fed heated and fed back into the heating system via the flow line V1.
  • a branch R1 is branched off from the return line R1, via which a small portion of the flow of the cold return water is introduced into the coils 7 for cooling the combustion chamber wall 4.
  • a flow line V2 feeds the cooling water after flowing through the coil 7 into the flow line V1 and thus into the heating system.
  • a control valve 18 inserted in line V2 controls the flow rate of the cooling water through the coils 7 in accordance with the temperature of the return water in line R2 determined by means of a sensor 19. By controlling the flow rate by means of the control valve 18, it is ensured that the temperature inside the wall 4 does not rise above 600 ° C. and, when the burner is reduced in power, does not decrease to such an extent that the combustion gases in the combustion chamber 1 are subcooled.
  • FIG. 8 shows a further embodiment in which the wall 4 of the combustion chamber is constructed in the same way as in the embodiment in FIG. 7.
  • two heat exchangers 12 are arranged one behind the other in the direction of flow of the flue gases.
  • the return water of the heating system is fed to the upper heat exchanger 12 near the burner via the return line R1 and, after heating in the heat exchanger 12, is returned to the heating system via the flow line V1.
  • the lower heat exchanger 12 remote from the burner serves to further cool the flue gases which have already cooled on the upper heat exchanger until they condense, so that the boiler can be operated as a condensing boiler.
  • FIG. 9 shows a fifth exemplary embodiment of the boiler, in which the wall 4 of the combustion chamber 1 is made of a thin steel sheet in the same way as in the exemplary embodiment in FIG stands.
  • the wall 4 is enclosed by an airtight, heat-insulating cover 18 in such a way that an air duct 19 extending over the entire surface of the wall 4 remains free between the wall 4 and the cover 18.
  • An air flow is passed through this air duct 19 for cooling the wall 4 by means of a suitable fan.
  • the heated air of this air stream can advantageously be fed to the burner as combustion air.
  • FIG. 10 shows a sixth embodiment of the boiler, which corresponds essentially to the embodiment shown in Figure 9.
  • a spray device 22 is arranged at the top in the combustion chamber.
  • This spray device 22 consists of a heat-resistant pipeline extending in the longitudinal direction of the combustion chamber 1 with outlet openings for a cleaning liquid, preferably water, distributed over the circumference and the length.
  • a cleaning liquid preferably water
  • the sprayed-in water also flows from top to bottom through the heat exchanger 12 and also rinses off any combustion residues deposited thereon. All the flushing water from the wall 4 of the combustion chamber 1 and from the heat exchanger 12 with the flushed combustion residues is in the bottom of the flue gas collecting chamber 11 collected and derived via the condensate drain 17.
  • a line 24 is branched from the flow line V1, through which a partial flow of the water heated in the heat exchanger I2 is returned to the flow line R1 and mixed with the cold flow water.
  • a control valve 26 inserted into the line 24 controls the flow rate through the line 24 in accordance with the temperature determined by a sensor 28 on the inlet side of the heat exchanger 12. In this way, a minimum temperature of the water entering the heat exchanger 12 via the return line R1 can be maintained. in order to avoid undercooling of the burner flame 10 by the uppermost heat exchanger 12 even with a reduced burner output and a low return temperature.
EP87117187A 1987-01-20 1987-11-21 Chaudière et procédure pour exploiter cette chaudière Expired - Lifetime EP0275401B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87117187T ATE72319T1 (de) 1987-01-20 1987-11-21 Heizkessel und verfahren zum betreiben des heizkessels.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3701439A DE3701439C3 (de) 1987-01-20 1987-01-20 Verfahren zum Betreiben eines Heizkessels und nach diesem Verfahren betriebener Heizkessel
DE3701439 1987-01-20

Publications (3)

Publication Number Publication Date
EP0275401A2 true EP0275401A2 (fr) 1988-07-27
EP0275401A3 EP0275401A3 (en) 1988-11-09
EP0275401B1 EP0275401B1 (fr) 1992-01-29

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ID=6319106

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87117187A Expired - Lifetime EP0275401B1 (fr) 1987-01-20 1987-11-21 Chaudière et procédure pour exploiter cette chaudière

Country Status (4)

Country Link
US (1) US4796569A (fr)
EP (1) EP0275401B1 (fr)
AT (1) ATE72319T1 (fr)
DE (2) DE3701439C3 (fr)

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CN107702320A (zh) * 2016-09-30 2018-02-16 重庆重锅能源科技有限公司 环保节能锅炉

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NL194652C (nl) * 1989-05-20 2002-10-04 Vaillant Joh Gmbh & Co Doorstroomwaterverhitter.
DE19581074C1 (de) * 1994-09-21 2000-05-31 Rudolf Justl Brennwertkessel
DE10156124B4 (de) * 2001-11-16 2004-06-24 Astrium Gmbh Flüssigkeitsgekühltes Raketentriebwerk mit mäanderförmigen Kühlkanälen
RU2617071C2 (ru) * 2013-02-21 2017-04-19 Общество С Ограниченной Ответственностью Промышленная Компания "Технология Металлов" Способ охлаждения корпуса плавильного агрегата и плавильный агрегат для его осуществления
US20190353402A1 (en) * 2018-05-17 2019-11-21 Dong Yong Hot Water System Inc. Temperature control system of gas-fired water heater

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DE3701439C3 (de) 1994-07-28
DE3701439A1 (de) 1988-07-28
EP0275401B1 (fr) 1992-01-29
EP0275401A3 (en) 1988-11-09
US4796569A (en) 1989-01-10
ATE72319T1 (de) 1992-02-15
DE3776543D1 (de) 1992-03-12
DE3701439C2 (fr) 1989-05-24

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