EP0079526B1 - Système de chauffage par rayonnement avec chambres de combustion à action directe - Google Patents

Système de chauffage par rayonnement avec chambres de combustion à action directe Download PDF

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Publication number
EP0079526B1
EP0079526B1 EP82110132A EP82110132A EP0079526B1 EP 0079526 B1 EP0079526 B1 EP 0079526B1 EP 82110132 A EP82110132 A EP 82110132A EP 82110132 A EP82110132 A EP 82110132A EP 0079526 B1 EP0079526 B1 EP 0079526B1
Authority
EP
European Patent Office
Prior art keywords
combustion chamber
heating system
radiant heating
pressure
circulating fan
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP82110132A
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German (de)
English (en)
Other versions
EP0079526A1 (fr
Inventor
Alfred Geibel
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.)
G&H Montage GmbH
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G&H Montage GmbH
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Publication date
Application filed by G&H Montage GmbH filed Critical G&H Montage GmbH
Priority to AT82110132T priority Critical patent/ATE11336T1/de
Publication of EP0079526A1 publication Critical patent/EP0079526A1/fr
Application granted granted Critical
Publication of EP0079526B1 publication Critical patent/EP0079526B1/fr
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D5/00—Hot-air central heating systems; Exhaust gas central heating systems
    • F24D5/06—Hot-air central heating systems; Exhaust gas central heating systems operating without discharge of hot air into the space or area to be heated
    • F24D5/08—Hot-air central heating systems; Exhaust gas central heating systems operating without discharge of hot air into the space or area to be heated with hot air led through radiators

Definitions

  • the invention relates to a radiant heating system with at least one radiant tube arrangement which is guided closed from an outflow side to a backflow side of a directly fired combustion chamber according to the preamble of claim 1.
  • Radiant heating systems of this type with direct firing are explained in practical use for natural gas and liquid gas operation and, for example, in DE-C No. 2743819.
  • the air to be circulated in the radiation pipe arrangement is introduced directly into the combustion chamber and comes into contact with the flame there. Together with the flue gases of the flame, which are only present in a few percent of the air circulated at a high speed of over 10 m / s, the air is fed from the discharge side of the combustion chamber to the suction port of a circulation fan, which passes the air through as a heating medium expediently sends the radiation arrangement in pairs and in countercurrent radiation tubes.
  • the heating medium heats the surface of the radiation pipes, which are installed on the ceiling of a factory, for example, so that they emit radiant heat.
  • the outflow end of the radiation tube arrangement is returned to the combustion chamber, so that the air can re-enter the combustion chamber from there.
  • an overpressure pipe arranged behind the circulation fan By means of an overpressure pipe arranged behind the circulation fan, a small amount of the heating medium is removed from the circuit and into the environment in order to keep the entire circulation volume of the heating medium constant despite the continuous low supply due to the exhaust gases entrained in the combustion chamber.
  • the radiant heating system While with such a radiant heating system a number of essential advantages such as uniform heat emission, lack of drafts, pleasant warmth in the lounge area, no heat build-up under the ceiling, low heating costs and short heating-up times in the context of heating larger halls or the like can be achieved, there is direct firing a problem in the contact of the flame with the circulated air in that the circulated air carries pollutants in the exhaust gases.
  • the radiation tubes are generally designed as spiral-seam tubes and are therefore exposed to possible leaks as well as, of course, in the event of local mechanical damage. Through this, the heating medium with the pollutants from the exhaust gas could leave the closed circuit and penetrate into the hall to be heated or the like, since the radiation tube arrangement receives the heating medium under excess pressure.
  • the invention has for its object to provide a radiant heating system according to the preamble of claim 1, in which any escape of exhaust gas pollutants from the radiation tube arrangement is excluded with certainty.
  • the circulation fan is arranged in the vicinity of the return flow side of the combustion chamber, the radiation tubes lie on the suction side thereof, so that underpressure now prevails in them instead of excess pressure. In the event of any leakage in the radiation tubes, ambient air is thus sucked into the radiation tubes to a limited extent, but the heating medium and thus also pollutants from the exhaust gas can be excluded with certainty.
  • a further advantage of such an arrangement of the circulation fan is that it conveys heating medium at a low temperature at the somewhat cold end of the radiant tube arrangement and, owing to the higher density of the cooler heating medium, has better efficiency and higher delivery capacity for a given drive power.
  • the arrangement according to the invention of the circulation fan on the backflow side of the combustion chamber gives rise to the problem that the combustion chamber itself and through the combustion chamber, at least a part of the radiation tube arrangement with a smaller distance from the pressure side of the circulation fan can nevertheless come under excess pressure.
  • This is disadvantageous because an internal overpressure would then have to be expected at least for part of the length of the radiation tube arrangement and, in the case of the usual atmospheric burner, an overpressure in the combustion chamber would prevent the desired flame formation.
  • the invention further provides that a swirl zone for converting between the pressure side of the circulation fan and the return flow side of the combustion chamber dynamic pressure of the heating medium is provided in static pressure, and that the volume relief opening is provided in the region of this swirling zone.
  • Fig. 1 is a circuit diagram of a radiation heating system according to the invention.
  • Fig. 2 shows a section through the swirl zone of the radiant heating system according to FIG. 1 in an enlarged view to illustrate the chosen design.
  • a radiant heating system essentially consists of a shortened radiation tube arrangement 1, in the radiation tubes of which air is circulated as a heating medium by means of a circulation fan 2 and heated in a combustion chamber 3.
  • the heat is given off by heating the walls of the radiation tubes, in practice the tubes are guided in pairs next to one another and flowed through in countercurrent in order to obtain the most uniform heat output over the entire tube length, averaged over both tubes.
  • the combustion chamber 3 is fired directly, so that the air brushes the flame directly in the interior of the combustion chamber 3, approximately according to the dashed line 4, and is guided through a baffle 5 from the return side designated 6 to the outlet side labeled 7 of the combustion chamber 3 .
  • the combustion chamber 3 is operated atmospherically, but is equipped with a feed blower 8 for the reasons explained below.
  • the circulation fan 2 is arranged, even more strongly than is shown in the drawing as a result of the shortened representation of the radiation tube arrangement 1, in the immediate vicinity of the return side 6 of the combustion chamber 3, so that the air is not forced through the radiation tube arrangement 1, but rather is sucked through.
  • This ensures that, in the event of any leak, at most ambient air can flow into the radiation tubes, but not heating medium, which contains exhaust gases from the combustion chamber 3, can escape into the environment.
  • the circulation fan 2 is thus located at the cooler end of the flow path of the heated air through the radiation tube arrangement 1 and can thus promote already cooled air with more favorable efficiency.
  • the pressure side of the circulation fan 2 is then at a very short distance from the return flow side 6 of the combustion chamber 3, so that without additional measures there is a risk that the overpressure on the pressure side of the circulation fan 2 will enter the combustion chamber 3 and through it into the initial area of the Radiation tube arrangement 1 is continued, so that an initial region of the radiation tubes would still receive excess pressure and atmospheric combustion could not be easily maintained.
  • a swirl zone designated overall with 10 is inserted in the connection stub 9, which in practice is short, between the pressure side of the circulation fan 2 and the backflow side 6 of the combustion chamber 3, in which dynamic pressure of the air is converted into static pressure.
  • a volume relief opening 11 of large cross section is provided, from which an overpressure pipe 12 is led to the outside air at 13.
  • Such a quantity of air is discharged through the pressure pipe 12 as corresponds to the additional gas quantity generated in the combustion chamber 3 by the exhaust gases of the flame denoted by 14, which must be introduced into the closed circuit and consequently also removed from it again.
  • the structural design of the swirling zone 10 can be seen in more detail in FIG. 2. Thereafter, in the example, the swirling zone 10 is designed as a chamber 15, into which ends 9a and 9b of the connecting piece 9 protrude and end at a mutual distance a, which corresponds approximately to the diameter d of the connecting piece 9.
  • the distance a or the diameter d can be, for example, 300 mm.
  • the chamber can have a circular cross section and a diameter D corresponding to 2 xd, in the example case it can be 600 mm.
  • the quantity relief opening 11 is arranged approximately in a round shape with a diameter d 'of 100 mm net and leads into the overpressure tube 12, the large cross section of the quantity relief opening 10 allowing largely unimpeded and low-speed extraction of the air in the outer annular space of the chamber 15.
  • the outer annular space of the chamber 15 thus serves, as it were, as a pressure supply space for the pressure pipe 12, neglecting the frictional resistance in the pressure pipe 12, this storage space of the chamber 15 can be regarded as open to the environment via the quantity relief opening 11.
  • the feed blower 8 ensures that the feed pressure is always kept at a maximum of about 15 mm WS above the combustion chamber pressure by means of the feed blower 8 in order to support a clean flame formation.
  • the circulation fan 2 starts after the main switch and the control switch (not shown) are switched on.
  • the voltage is switched through to a gas pressure monitor 16.
  • the gas pressure monitor 16 only switches the voltage on to a vacuum monitor 17 and a combustion air pressure monitor 18 when the gas pressure is above the set minimum pressure.
  • the vacuum monitor 17 for example set to -1 mbar, is connected a maximum of 1 m behind the discharge side 7 of the combustion chamber 3 and monitors the vacuum in the entire radiation pipe arrangement 1. If the vacuum at the vacuum monitor 17 corresponds to the set value, voltage is released to the combustion air pressure monitor 18 and from there to a terminal of a flame monitor 19 designated by 7. The program sequence of the flame monitor 19 then takes place.
  • the ignition stage is released if combustion air pressure is present. Monitoring takes place via the combustion air pressure monitor 18. After ignition and feedback to the flame monitor 7, the main load is switched on via a slowly opening magnetic valve of the flame monitor 19. If there is no burner ignition, the system is switched off.
  • the flow temperature in the radiation pipe arrangement 1 is monitored and regulated via a control thermostat 20. After reaching the set flow temperature, the large step is switched back to the small step (approx. 35%) via the control thermostat 20.
  • the system is switched off using a room thermostat, not shown.
  • the feed blower 8 feeds combustion air in an amount of approximately 1.1 m 3 / h per 1000 kcal, the control of the air pressure switch 18 taking place.
  • a flow temperature sensor and at 23 a return temperature sensor of the radiation tube arrangement 1 are illustrated, while 24 denotes a measuring device for detecting the air quantity and the air pressure in the radiation tube arrangement 1.
  • the diffuser sheets 25 are schematically shown in FIG. 1, which could be used in the area of the distance a between the nozzle ends 9a, 9b in order to bring about a greater swirling out of the edge region of the flow coming from the nozzle end 9a. In practice, however, it has been shown that such diffuser sheets 25 are not required for the described dimensioning of the diameter d and the distance a.
  • a fine adjustment of the pressure or the amount of exhaust gas in the pressure pipe 12 can take place via a regulating flap 26 in the connecting piece 9 downstream of the swirling zone 10 and / or via a regulating flap 27 in the pressure pipe 12, in which a measuring device 28 is also arranged, which measures the fixed set amount of exhaust gas for a given combustion output and the exhaust gas temperature; which may be between 110 and 160 ° C. Since regulating flaps 26 and 27 are fundamentally flow obstacles that generate flow losses, it is desirable that they are regularly open during operation and that they are only used for fine adjustment if necessary. In principle, even without regulating flaps 26 and 27, by appropriate dimensioning in the area of the swirl zone 10, the required amount of exhaust gas is blown off through the pressure pipe 12 and a pressure drop to approximately atmospheric pressure takes place in the connecting piece 9 behind the swirl zone 10.
  • the pressure pipe 12 can contain a heat exchanger in a manner not shown in which the residual energy of the hot exhaust gas is partially made usable again. Ver on the flow conditions in the pressure pipe 12 equally large cross-section, this has no significant influence.
  • the entire radiation tube arrangement 1 lies in a negative pressure area and therefore it is impossible for pollutants to escape into the environment when leaks occur, while on the other hand no increased drive power of the circulation fan 2 is required and the latter can even be made smaller, since it conveys cooler air in the vicinity of the return flow side 6 of the combustion chamber 3 than in the area of the discharge side 7.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Gas Burners (AREA)

Claims (9)

1. Système de chauffage par rayonnement comportant au moins un dispositif à tube de rayonnement (1) fermé allant d'un côté départ du flux (7) à un côté retour du flux (6) d'une chambre de combustion (3) à action directe, dispositif dans lequel peut circuler à vitesse élevée un fluide de chauffage gazeux, en particulier de l'air, au moyen d'un ventilateur de circulation (2); et comportant une ouverture (11 ) de décharge de débit, ouverte en direction de l'air extérieur, pour permettre la sortie, hors du circuit fermé, du débit superflu du fluide de chauffage correspondant à l'introduction de gaz d'évacuation dans la chambre de combustion, caractérisé en ce que le ventilateur de circulation (2) est disposé au voisinage du côté retour de flux (6) de la chambre de combustion (3); en ce qu'entre le côté surpression du ventilateur de circulation (2) et le côté retour de flux (6) de la chambre de combustion se trouve une zone tourbillonnante (10) pour transformer la pression dynamique du flux de chauffage en pression statique; et en ce que l'ouverture de décharge de débit (11) est prévue dans la région de la zone tourbillonnante (10).
2. Système de chauffage par rayonnement selon la revendication 1, caractérisé en ce que sur la chambre de combustion (3) est disposé un ventilateur d'alimentation (8) pour produire une surpression des gaz de combustion.
3. Système de chauffage par rayonnement selon l'une des revendications 1 ou 2, caractérisé en ce qu'un noyau de flux, qui se trouve dans la région de l'axe de la conduite, passe essentiellement sans tourbillonner à travers la zone tourbillonnante (10).
4. Système de chauffage par rayonnement selon la revendication 3, caractérisée en ce qu'il est prévu dans la tubulure de liaison (9), entre le ventilateur de circulation (2) et la chambre de combustion (3), un élargissement de section (chambre 15) pour recevoir les zones de bordure, exposées au tourbillonnement, du flux.
5. Système de chauffage par rayonnement selon la revendication 4, caractérisé en ce que l'élargissement est conçu sous la forme d'une chambre coaxiale (15) installée sur le chemin de la tubulure de liaison (9).
6. Système de chauffage par rayonnement selon l'une des revendications 4 ou 5, caractérisé en ce que l'élargissement présente un diamètre D correspondant à peu près au double du diamètre (d) des extrémités de tubulure (9a ou 9b) qui se raccordent dans cet élargissement.
7. Système de chauffage par rayonnement selon l'une des revendications 4 à 6, caractérisé en ce que les extrémités (9a, 9b) de la tubulure de liaison (9) entre le ventilateur de circulation (2) et la chambre de combustion (3) pénètrent dans le volume interne de l'élargissement (chambre 15).
8. Système de chauffage par rayonnement selon l'une des revendications 4 à 7, caractérisé en ce que la distance axiale (a) entre les extrémités de tubulure (9a, 9b) correspond à peu près au diamètre (d) des extrémités de tubulure (9a, 9b).
9. Système de chauffage par rayonnement selon l'une des revendications 1 à 8, caractérisé en ce que l'ouverture de décharge de débit (11) présente une section importante avec un diamètre supérieur à environ 50 mm et en particulier supérieur à environ 100 mm.
EP82110132A 1981-11-03 1982-11-03 Système de chauffage par rayonnement avec chambres de combustion à action directe Expired EP0079526B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82110132T ATE11336T1 (de) 1981-11-03 1982-11-03 Strahlungsheizungsanlage mit direkt befeuerter brennkammer.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3143602A DE3143602C2 (de) 1981-11-03 1981-11-03 Strahlungsheizungsanlage mit direkt befeuerter Brennkammer
DE3143602 1981-11-03

Publications (2)

Publication Number Publication Date
EP0079526A1 EP0079526A1 (fr) 1983-05-25
EP0079526B1 true EP0079526B1 (fr) 1985-01-16

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ID=6145493

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82110132A Expired EP0079526B1 (fr) 1981-11-03 1982-11-03 Système de chauffage par rayonnement avec chambres de combustion à action directe

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EP (1) EP0079526B1 (fr)
AT (1) ATE11336T1 (fr)
DE (2) DE3143602C2 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3403993A1 (de) * 1984-02-06 1985-08-14 Kraftanlagen Ag, 6900 Heidelberg Einrichtung zur raumheizung
US4712734A (en) * 1986-05-08 1987-12-15 Johnson Arthur C W Low-intensity infrared heating system with effluent recirculation
IT1266128B1 (it) * 1993-10-11 1996-12-20 Termotecniche Fraccaro O T F S Dispositivo per il riscaldamento di locali
FR2787557B1 (fr) * 1998-12-22 2001-03-09 Dominique Boudrie Dispositif et procede de chauffage a basse temperature
FR2874419B1 (fr) * 2004-08-17 2006-10-06 Lgl France Sa Dispositif de chauffage pour une installation de conditionnement d'air d'une enceinte
ITPD20050133A1 (it) * 2005-05-11 2006-11-12 Systema Spa Impianto di riscaldamento a tubi radianti
ITTV20050171A1 (it) * 2005-11-08 2007-05-09 Termotecniche Fraccaro O T F S Dispositivo per il riscaldamento, la produzione di energia elettrica ed il raffrescamento di locali.
GB2443642A (en) * 2006-11-10 2008-05-14 Whiteside Accoutants Hot air radiator comprising an air extracting machine
ITVI20090234A1 (it) 2009-09-25 2011-03-26 Termotecniche Fraccaro S R L Off Dispositivo per il riscaldamento di ambienti ad alta efficienza energetica, nonche' sistema riscaldante comprendente tale dispositivo
EP3056809A1 (fr) 2015-02-12 2016-08-17 Carlieuklima S.p.A. Installation de chauffage à conduites rayonnantes
ITUB20152466A1 (it) * 2015-07-24 2017-01-24 Oscar Pallaro Impianto di riscaldamento a nastri radianti
IT201600085950A1 (it) * 2016-08-18 2018-02-18 Oscar Pallaro Impianto di riscaldamento a condotti radianti

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE375820C (de) * 1923-05-18 Otto Schulz Zentralheizung
FR606020A (fr) * 1924-11-13 1926-06-05 J & O G Pierson Perfectionnement au chauffage à l'aide de gaz chauds
US3399833A (en) * 1966-12-14 1968-09-03 Comb Res Corp Low intensity radiant heater system and burner therefor
GB1448073A (en) * 1974-05-08 1976-09-02 Radiant Tube Systems Ltd Space heating systems and apparatus
DE2743819C3 (de) * 1977-09-29 1980-08-21 Gruenzweig + Hartmann Montage Gmbh, 6700 Ludwigshafen Deckenstrahlungsheizung für Hallen u.a. Bauten

Also Published As

Publication number Publication date
ATE11336T1 (de) 1985-02-15
DE3143602C2 (de) 1984-05-10
DE3261975D1 (en) 1985-02-28
EP0079526A1 (fr) 1983-05-25
DE3143602A1 (de) 1983-05-11

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