EP0635679A1 - Einspritz- und Regelvorrichtung für atmosphärische Gasbrenner von Heizgeräte, insbesondere der Infrarottyp - Google Patents

Einspritz- und Regelvorrichtung für atmosphärische Gasbrenner von Heizgeräte, insbesondere der Infrarottyp Download PDF

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Publication number
EP0635679A1
EP0635679A1 EP94202045A EP94202045A EP0635679A1 EP 0635679 A1 EP0635679 A1 EP 0635679A1 EP 94202045 A EP94202045 A EP 94202045A EP 94202045 A EP94202045 A EP 94202045A EP 0635679 A1 EP0635679 A1 EP 0635679A1
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EP
European Patent Office
Prior art keywords
injector
injection
valve
gas
stage
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
EP94202045A
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English (en)
French (fr)
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EP0635679B1 (de
Inventor
Joseph Strand
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Centre dEtude et de Realisations dEquipment et de Materiel CEREM
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Centre dEtude et de Realisations dEquipment et de Materiel CEREM
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/62—Mixing devices; Mixing tubes
    • F23D14/64—Mixing devices; Mixing tubes with injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/007—Regulating fuel supply using mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
    • F23D2900/14—Special features of gas burners
    • F23D2900/14642—Special features of gas burners with jet mixers with more than one gas injection nozzles or orifices for a single mixing tube
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/12—Fuel valves
    • F23N2235/16—Fuel valves variable flow or proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/12—Fuel valves
    • F23N2235/18—Groups of two or more valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/12—Fuel valves
    • F23N2235/20—Membrane valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/12—Fuel valves
    • F23N2235/24—Valve details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2237/00—Controlling
    • F23N2237/02—Controlling two or more burners

Definitions

  • the invention relates to an injection and regulation device between a minimum power, called idling power, and a maximum power, called nominal power, for atmospheric gas burners of heating appliances, in particular of the infrared type, comprising a pipe air supply with an air inlet mouth and a Venturi element.
  • This device is also of the type comprising gas injection means connected to gas supply pipe means, arranged in the air supply pipe of each burner, upstream of the Venturi element, and means for regulating the quantity of gas delivered to the injection means.
  • Such a device is, moreover, particularly suitable for equipping heating apparatuses called upon to operate at a low nominal pressure.
  • burners operating at low pressure that is to say at a pressure generally less than 500 mbar, are affected by a deterioration in the quality of combustion if the supply pressure drops below the nominal value for which they were designed.
  • the problem therefore concerns "low pressure" devices, that is, for example, a device operating at a nominal pressure of 350 mbar for which the intake of aspirated air and the injection of gas delivered by the injector do not remain not proportional over a pressure range falling below 50% of the nominal speed.
  • the present invention aims to solve this problem and has the essential objective of providing an injection and regulation device making it possible to maintain good carburetion of atmospheric gas burners intended to operate in nominal low pressure mode when it is desired to modulate their regime up to at minimum idle from nominal pressure.
  • a second stage injector is understood to include devices comprising several stages, and / or devices comprising several injectors per stage).
  • the principle of the invention is therefore to provide several injectors used in cascade, making it possible to reduce the size of the respective injectors for a given quantity of gas delivered, and leading to an increase in the speed of ejection of the gas flow and to a improvement of the air suction effect at the inlet of the Venturi element.
  • one of the injectors is arranged in the axis of the air supply pipe, each of the other injectors being inclined relative to said axis so as to converge towards the latter.
  • At least one of the second stage injectors is mounted on an injector tube housing a needle having a tapered end of cross section adapted to penetrate the injection nozzle, said needle being associated with actuating means able to move it so as to bring it either in a closed position of the gas supply to the injector, or in regulation positions where it generates variations in flow rate depending on its position.
  • Such an arrangement makes it possible to generate a gradual opening and closing of the injection nozzle of the second stage injectors and to obtain an optimal gas ejection speed at all speeds.
  • At least one of the injectors of the second stage is advantageously mounted on an injector carrier tube housing a needle having a tapered end of section adapted to penetrate the injection nozzle, the carrier tube injector being associated with a valve provided with a movable member, and the needle being integral with the movable member of said valve and coming in the extension thereof, so as to bring said needle into regulation positions where it generates variations in flow rate depending on its position.
  • this arrangement makes it possible to gradually close and open the injection nozzles and to optimize the gas ejection speed.
  • the regulation means are of the individual type and include a controlled valve for regulating the gas flow rate, associated with each burner of a heating appliance, and connected to a main supply line for gas.
  • the idling pre-injector allows to create, when the controlled valve is closed, a pressure drop allowing to obtain a pressure corresponding to the minimum idling speed of the associated burner.
  • this pre-injector is preferably a conventional type injector comprising a body forming a plug with an injection orifice, towards one of its ends, said injector being positioned "head to tail" so that the gas penetrates through the injection port.
  • the purpose of this provision is to avoid the accumulation and agglomeration of micro-impurities from the pipes and from the commercial gas itself.
  • the internal profile of said injector is conical for technological necessity of perforation of the calibrated orifice. This internal conicity, forming a bottleneck for micro-impurities which can agglomerate and settle there, often leads to the obstruction of small caliber injectors.
  • This second embodiment constitutes a more economical solution than that described above because it makes it possible to eliminate the shut-off valves of the second stage injectors, this economic gain being however obtained at the expense of a slight drop in performance at the end. from the closing or at the beginning of the opening of the controlled valve.
  • the position of the first stage injector must be adapted to the fact that said injector, on the one hand, is supplied with a fixed gas pressure corresponding to the nominal pressure and, on the other hand, must provide an injection flow corresponding to the minimum idling speed.
  • a first advantageous solution aimed at satisfying these requirements consists in making a device comprising a second stage injector disposed in the axis of the air supply pipe, and a first stage injector inclined relative to said axis so as to converge towards the latter, and positioned so that its injection nozzle is offset longitudinally forward with respect to that of the second stage injector.
  • Another solution consists in making a device comprising a second stage injector disposed in the axis of the air supply pipe, and a first stage injector inclined with respect to said axis so as to converge on the latter, and positioned so that its injection nozzle is offset longitudinally towards the rear relative to that of the second injector stage, said device then comprising an obstacle arranged so as to intercept the flow of gas delivered by the first stage injector.
  • This second solution which consists in adjusting the gas ejection speed by interposing an obstacle on the path of the gas jet in order to slow down its speed and modify, by decreasing, the quantity of air entrained, turns out to be the most advantageous.
  • the obstacle can be achieved in a very simple way, for example by means of a screw projecting inside the air supply pipe, and its position can be adjusted very easily up to obtaining optimum operating conditions.
  • injection and regulation devices according to the invention are shown in the figures associated with infrared heaters 1 as used in the agricultural sector for heating livestock buildings.
  • such heaters 1 first include a reflector 2 in the form of a dome intended to be suspended above the location chosen using for example a chain 3, and containing the diffusion, combustion and radiation organs (such organs, not shown, may in particular be of the type described in US Pat. No. 5,060,629 in the name of the applicant).
  • a reflector 2 in the form of a dome intended to be suspended above the location chosen using for example a chain 3, and containing the diffusion, combustion and radiation organs (such organs, not shown, may in particular be of the type described in US Pat. No. 5,060,629 in the name of the applicant).
  • Each heating appliance 1 further comprises an air / gas supply pipe consisting of a bent pipe 4 conventionally provided with a venturi element 5 and an inlet mouth 6 for the primary combustion air.
  • This heating device 1 also comprises, in a conventional manner, a safety valve 7 connected to a pipe 8 for supplying gas to said device, and the outlet of which is connected to gas injection means arranged upstream of the venturi element 5 and described below.
  • heating devices 1 are intended to operate in nominal low pressure mode with the possibility of modulating their speed up to a minimum idle speed.
  • the regulation means allowing this modulation are either centralized (FIGS. 1, 2, 3, 4, 9, 10) and therefore common to several heating devices, or individual and composed of a controlled gas flow regulation valve associated with each appliance ( Figures 5 to 8).
  • FIG. 1 represents an installation provided with centralized regulation means, comprising a main supply pipe 9 to which pipes 8 for supplying gas to the heating appliances are connected.
  • These centralized regulation means consist, in a conventional manner, of a regulation table 10 with thermostatic valve or power regulator controlled by a servo-motor, the whole being arranged in parallel with respect to a bypass line 11 on which is an idle pressure reducer 12.
  • each heating device comprises a first stage injector 13 connected directly to a outlet of the safety valve 7 and arranged to extend in the axis of the pipe 4.
  • This heating device further comprises a second stage injector 14 inclined with respect to the axis of the pipe 4 and recessed with respect to the first stage injector 13.
  • This injector 14 is connected to a second outlet of the safety valve 7 by means of a bypass pipe 15 on which is mounted a membrane valve 16.
  • This second stage injector 14 is, moreover, directly secured to an internal protrusion 17 of the pipe 4, pierced with a gas supply bore 18.
  • the membrane valve 16 is conventionally adapted to close the bypass line 15 when the gas pressure in the latter becomes less than a predetermined threshold.
  • Such an embodiment is particularly suitable for heating installations whose nominal supply pressure is greater than 100 mbar, with a possible pressure variation between 20 mbar and the nominal power.
  • the first stage injector 13 is calibrated to give an injection rate suitable for the pressure of 20 mbar.
  • FIGS. 5 to 8 are aimed at heating appliances provided with their own individual regulating member, consisting of a thermostatic valve, the design of which will be described later with reference to FIG. 11.
  • the thermostatic valve 19 is arranged upstream of the safety valve 7.
  • the gas supply pipe 8 has a branch section 20 comprising an idle pre-injector 21.
  • Such an idle pre-injector 21 is designed to create, when the thermostatic valve 19 is closed, a pressure drop enabling a pressure corresponding to the minimum idling speed to be obtained.
  • the pre-injector 21 is also made up of a conventional injector positioned "head to tail" so that the gas enters through its injection orifice.
  • the injectors are arranged identically to those of the heater of FIG. 4: the first stage injector 22 is connected directly to the safety valve 7 and extends in the axis of the pipe 4, and the second stage injector 23 is inclined relative to the said axis, and connected to the safety valve 7 by a bypass pipe 24 comprising a membrane valve 25.
  • Such an embodiment is particularly suitable for heating installations whose nominal supply pressure is greater than 150 mbar, with a possible variation between 20 mbar and the nominal power.
  • the first stage injector 22 is calibrated to give an injection flow rate suitable for the pressure supplied by the pre-injector 21.
  • the thermostatic valve 26 is arranged downstream of the safety valve 7.
  • the first stage injector 27 is connected directly to one of the outputs of the safety valve 7 by a bypass line 28 and is located in place of the second stage injector (14 or 23) of the preceding variants, that is to say inclined relative to the axis of the pipe 4, and recessed with respect to the second stage injector 29 which extends to it in the axis of the pipe 4.
  • an obstacle 30, consisting of a screw projecting inside the pipe 4 is arranged so as to intercept the gas flow delivered by this injector in order to slow down the speed of the gas jet and reduce the amount of air entrained by the latter.
  • the first stage injector 27 can be adapted to have a length such that its injection nozzle is disposed in front of that of the second stage injector 29. In this case the obstacle 30 is useless.
  • Such an embodiment is particularly suitable for heating installations whose nominal supply pressure is between 100 and 150 mbar, and constitutes a particularly economical solution.
  • the first stage injector 31 is similar to that of the previous embodiment, that is to say directly connected to the safety valve 7 by a bypass line 32, disposed inclined relative to the axis of the pipe 4, set back relative to the second stage injector 33, and associated with an obstacle 34 intercepting the flow of gas.
  • the second stage injector 33 extends as for it in the axis of the pipe 4 and is mounted on the end of an injector carrier tube 35, secured towards its other end on the body 36 of the thermostatic valve. 37, as shown in FIG. 8.
  • This injector-carrying tube 35 also houses a needle 38 having a tapered end of section adapted to penetrate the injection nozzle of the injector 33, so as to generate variations in flow rate which depend on the relative position of said nozzle. tapered end relative to said injection nozzle.
  • This needle 38 has, in addition, a length adapted so that its end opposite its tapered end extends in the extension of the injector tube 35.
  • Thermostatic valve 37 comprises a valve body divided into two body half 36a, 36b, delimiting an annular internal groove housing the periphery of a membrane 39.
  • One of these body halves 36a has a front threaded hole 40 for fixing the injector tube 35, and a lateral threaded hole 41 intended for connection of the thermostatic valve 37 with the safety valve 7.
  • This half of body 36a further comprises a seat 42 coaxial with the front threaded orifice 40, and communicating with said front orifice by means of a bore 43 opening into the respective bottoms of said orifice and seat.
  • the second body half 36b delimits an internal chamber 44 provided with a vent hole 45 ensuring that said chamber is brought to atmospheric pressure.
  • the thermostatic valve 37 further comprises a valve 46 of a shape adapted to cooperate with the seat 42, and a conventional bellows 47 with expandable fluid, arranged on either side of the membrane, bearing against a floating piece 48 integral of said membrane.
  • This thermostatic valve 37 and the injector tube 35 are arranged, as shown in Figure 8, so that the needle 38 abuts against the valve 46, and is moved in the direction of closure of the nozzle d injection during an extension of the bellows 47.
  • Such an embodiment is particularly suitable for heating installations whose supply pressure is of the order of 100 mbar, equipped with heating devices with large calorific power (5,000 to 10,000 Watts).
  • the gradual opening and closing of the injection nozzle of the second stage injector 33 makes it possible to obtain an optimal gas speed at all speeds.
  • FIGS. 9 and 10 aims, finally, at a heating appliance equipping a heating installation provided with centralized regulation means such as that shown diagrammatically in FIG. 1.
  • This heating device comprises a first stage injector 50 connected directly to the safety valve 7 by a bypass pipe 51, and secured to the internal projection 17 of the pipe 4, so as to extend along an axis inclined by relative to the axis of said pipe.
  • the second stage injector 52 meanwhile, extends in the axis of the pipe 4, in front of the first stage injector 50, and is mounted on the end of a tube 53 of the injector holder which is secured, towards its other end, on the body of a membrane valve 54 as shown in FIG. 10.
  • This injector holder tube 53 also houses a needle 55 having a tapered end of section adapted to penetrate the injection nozzle of the injector 52, so as to generate variations in flow rate which depend on the relative position of said injector. tapered end relative to said injection nozzle.
  • This needle 55 has, moreover, a length adapted so that its end opposite its tapered end extends in the extension of the injector tube 53.
  • the membrane valve 54 comprises a valve body divided into two body halves 54a, 54b delimiting an annular internal groove housing the periphery of a membrane 56.
  • One of these body halves 54a has a front threaded hole 57 for fixing the injector tube 53, and a lateral threaded hole 58 intended for the connection of the diaphragm valve 54 with the safety valve 7.
  • the second half of body 54b delimits an internal chamber 59 provided with a vent hole 60 ensuring that said chamber is brought to atmospheric pressure, inside which opens the threaded front orifice 57.
  • This membrane valve finally comprises, in a conventional manner, a spring 61 housed in the chamber 59, bearing at one end on a floating part 62 secured to the membrane 56, and at its other end on a movable stop 63 whose position is controlled by an adjusting screw 64.
  • This membrane valve 54 and the injector tube 53 are arranged so that the needle 55 is secured to the floating part 62 and is moved longitudinally as a function of the pressure of the supply gas modulated by the centralized regulation means.
  • the injector tube 53 forms a seat 65
  • the needle 55 has a valve-shaped flange 66 capable of closing the seat 65, in the deployed position of the spring 58 corresponding to a lower gas supply pressure. at the preset threshold for closing the diaphragm valve 54.
  • this version is particularly suitable for heating installations whose supply pressure is of the order of 100 mbar, fitted with large power heating devices.
  • FIG. 11 is a block diagram of the thermostatic valves 19, 26 equipping the devices represented in FIGS. 5 and 6.
  • This thermostatic valve is divided into two chambers 67, 68 by a membrane 69 secured at its periphery to the valve body, and carrying a floating part 70.
  • This valve conventionally comprises, on the one hand, a valve 71 bearing against the floating part 70 and urged in the direction of opening of said valve by a spring 72, and on the other hand, a bellows 73 with expandable fluid coming to bear against the opposite face of the floating part 70 in order to urge the valve 71 in the closing direction, during its elongation.
  • FIG. 12 is a schematic diagram of the membrane valves 16, 25 equipping the devices shown in FIGS. 4 and 5.
  • This membrane valve is divided into two chambers 74, 75 by a membrane 76 carrying a floating part 77.
  • a valve 78 integral with the floating part 77, while the other chamber 75 contains a spring 79 which bears at one end against the floating part 77, and at its end opposite, against a movable stop 80 whose position is adjusted by an adjustment screw 81.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Gas Burners (AREA)
  • Regulation And Control Of Combustion (AREA)
EP94202045A 1993-07-23 1994-07-14 Einspritz- und Regelvorrichtung für atmosphärische Gasbrenner von Heizgeräte, insbesondere der Infrarottyp Expired - Lifetime EP0635679B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9309379A FR2708085B1 (fr) 1993-07-23 1993-07-23 Dispositifs d'injection et de régulation pour brûleurs atmosphériques à gaz fonctionnant à faible pression nominale.
FR9309379 1993-07-23

Publications (2)

Publication Number Publication Date
EP0635679A1 true EP0635679A1 (de) 1995-01-25
EP0635679B1 EP0635679B1 (de) 1998-10-07

Family

ID=9449778

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EP94202045A Expired - Lifetime EP0635679B1 (de) 1993-07-23 1994-07-14 Einspritz- und Regelvorrichtung für atmosphärische Gasbrenner von Heizgeräte, insbesondere der Infrarottyp

Country Status (6)

Country Link
US (1) US5549099A (de)
EP (1) EP0635679B1 (de)
JP (1) JPH07269850A (de)
DE (1) DE69413756T2 (de)
ES (1) ES2124362T3 (de)
FR (1) FR2708085B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0754914A1 (de) * 1995-07-19 1997-01-22 Centre D'etude Et De Realisations D'equipement Et De Materiel (C.E.R.E.M.) S.A.R.L. Einspritzvorrichtung für atmosphärische Gasbrenner von Heizgeräten, insbesondere des Infrarottyps
US10888827B2 (en) 2018-02-23 2021-01-12 Hennecke Gmbh Component mixing jet

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29908550U1 (de) 1999-05-14 1999-08-12 Honeywell B.V., Amsterdam Vorrichtung zum Erzeugen eines Gemisches aus Gas und Verbrennungsluft für einen Brenner
US8246344B1 (en) * 2003-07-29 2012-08-21 Samuel Schrock Gas lamp
US9328937B2 (en) 2011-06-07 2016-05-03 L.B. White Company, Inc. Variable rate heating for agricultural purposes
DE102012106230A1 (de) 2012-07-11 2014-05-15 Kraussmaffei Technologies Gmbh Komponentenzufuhrdüse
CN110906327A (zh) * 2019-11-08 2020-03-24 杭州富尔顿热能设备有限公司 可调燃比文丘里管

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE535137C (de) * 1931-10-03 Ignis Huettenbaugesellschaft M Mischduesenbrenner mit mehreren Duesen
US2939524A (en) * 1957-08-29 1960-06-07 Roper Corp Geo D Control system for gas burners
US3599661A (en) * 1970-02-05 1971-08-17 Walton W Cushman Self-modulating gas burner
DE2151611A1 (de) * 1971-10-16 1973-04-19 Rheinstahl Ag Atmosphaerischer gasbrenner
JPS5888273A (ja) * 1981-11-19 1983-05-26 Paloma Ind Ltd 大型ガス燃焼器の供給ガス圧降下防止装置付きガス圧力調整器

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2642821A1 (fr) * 1989-02-07 1990-08-10 Etu Realisa Equip Materie Cent Radiant infra-rouge a gaz avec pre-chambre de diffusion et thermocouple a fusible haute temperature

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE535137C (de) * 1931-10-03 Ignis Huettenbaugesellschaft M Mischduesenbrenner mit mehreren Duesen
US2939524A (en) * 1957-08-29 1960-06-07 Roper Corp Geo D Control system for gas burners
US3599661A (en) * 1970-02-05 1971-08-17 Walton W Cushman Self-modulating gas burner
DE2151611A1 (de) * 1971-10-16 1973-04-19 Rheinstahl Ag Atmosphaerischer gasbrenner
JPS5888273A (ja) * 1981-11-19 1983-05-26 Paloma Ind Ltd 大型ガス燃焼器の供給ガス圧降下防止装置付きガス圧力調整器

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 7, no. 187 (M - 236) 16 August 1983 (1983-08-16) *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0754914A1 (de) * 1995-07-19 1997-01-22 Centre D'etude Et De Realisations D'equipement Et De Materiel (C.E.R.E.M.) S.A.R.L. Einspritzvorrichtung für atmosphärische Gasbrenner von Heizgeräten, insbesondere des Infrarottyps
US10888827B2 (en) 2018-02-23 2021-01-12 Hennecke Gmbh Component mixing jet

Also Published As

Publication number Publication date
EP0635679B1 (de) 1998-10-07
ES2124362T3 (es) 1999-02-01
FR2708085B1 (fr) 1996-05-24
DE69413756T2 (de) 1999-06-17
DE69413756D1 (de) 1998-11-12
FR2708085A1 (fr) 1995-01-27
JPH07269850A (ja) 1995-10-20
US5549099A (en) 1996-08-27

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