EP0138070B1 - High-speed carburetter for an otto engine - Google Patents

High-speed carburetter for an otto engine Download PDF

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Publication number
EP0138070B1
EP0138070B1 EP84110945A EP84110945A EP0138070B1 EP 0138070 B1 EP0138070 B1 EP 0138070B1 EP 84110945 A EP84110945 A EP 84110945A EP 84110945 A EP84110945 A EP 84110945A EP 0138070 B1 EP0138070 B1 EP 0138070B1
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EP
European Patent Office
Prior art keywords
valve
flow control
chamber
control valve
duty factor
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
EP84110945A
Other languages
German (de)
French (fr)
Other versions
EP0138070A3 (en
EP0138070A2 (en
Inventor
Burkhard Brandner
Helmut Schilly
Albert Stübs
Dieter Stojek
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.)
Schaeffler Engineering GmbH
Original Assignee
AFT Atlas Fahrzeugtechnik GmbH
Ford Werke GmbH
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 AFT Atlas Fahrzeugtechnik GmbH, Ford Werke GmbH filed Critical AFT Atlas Fahrzeugtechnik GmbH
Priority to AT84110945T priority Critical patent/ATE36739T1/en
Publication of EP0138070A2 publication Critical patent/EP0138070A2/en
Publication of EP0138070A3 publication Critical patent/EP0138070A3/en
Application granted granted Critical
Publication of EP0138070B1 publication Critical patent/EP0138070B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M9/00—Carburettors having air or fuel-air mixture passage throttling valves other than of butterfly type; Carburettors having fuel-air mixing chambers of variable shape or position
    • F02M9/10—Carburettors having air or fuel-air mixture passage throttling valves other than of butterfly type; Carburettors having fuel-air mixing chambers of variable shape or position having valves, or like controls, of elastic-wall type for controlling the passage, or for varying cross-sectional area, of fuel-air mixing chambers or of the entry passage
    • F02M9/106—Pneumatic or hydraulic control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M7/00—Carburettors with means for influencing, e.g. enriching or keeping constant, fuel/air ratio of charge under varying conditions
    • F02M7/12—Other installations, with moving parts, for influencing fuel/air ratio, e.g. having valves
    • F02M7/18—Other installations, with moving parts, for influencing fuel/air ratio, e.g. having valves with means for controlling cross-sectional area of fuel-metering orifice
    • F02M7/20—Other installations, with moving parts, for influencing fuel/air ratio, e.g. having valves with means for controlling cross-sectional area of fuel-metering orifice operated automatically, e.g. dependent on altitude
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S261/00—Gas and liquid contact apparatus
    • Y10S261/56—Variable venturi
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S261/00—Gas and liquid contact apparatus
    • Y10S261/74—Valve actuation; electrical

Definitions

  • the invention relates to a high-speed carburetor for a gasoline engine with a slide that changes the intake manifold cross-section, with a two coaxially arranged nozzle receptacle that is separated from one another by an intermediate chamber, and with a profiled nozzle needle that controls the nozzle cross-section and sits on the slide, and with which the intermediate chamber the outlet channel of a flow control valve is connected to a ferromagnetic valve body, the valve body can be actuated by a coil connected to a pulse generator with an adjustable duty cycle, the inlet channel of the flow control valve is connected to the atmospheric air, and the duty cycle is controlled as a function of operating values.
  • Such a high-speed carburetor with slide has no throttle valve, so that, in contrast to a constant pressure carburetor, practically the full intake manifold pressure is applied to the nozzle in the area of the slide.
  • very high flow velocities at the nozzle and thus good atomization properties result, especially in the partial load range.
  • a negative pressure corresponding to the suction pipe negative pressure builds up in the intermediate chamber between the two nozzles.
  • the cross-sectional ratio of the nozzles or the slope of the nozzle needle determines the size of the negative pressure present between the nozzles in the intermediate chamber.
  • a certain slide position i.e. assign a fuel quantity to a certain negative pressure.
  • this amount of fuel is not always in the optimal operating range of the engine. If the fuel metering is selected for a specific nozzle needle characteristic in such a way that a rich mixture state results, then the negative pressure prevailing there can be reduced by admixing air in the intermediate chamber. This allows the amount of fuel to be reduced and the fuel-air mixture to become leaner.
  • the air admixture brings about a further atomization improvement in addition to the control of the fuel-air mixture.
  • a carburetor of the type mentioned is described in US Pat. No. 3,963,009.
  • the slide adjusts itself according to the negative pressure generated between a main throttle valve and the slide.
  • This mechanical setting is associated with a hysteresis, so that the slide position cannot be reproduced exactly and therefore no clearly determined load-dependent fuel composition is possible.
  • the additional air is regulated depending on the oxygen ratio in the exhaust gas. Other operating parameters cannot be taken into account. It is also not possible to change the additional air for certain operating conditions such as acceleration, starting phase.
  • the object of the invention is a precise metering of the air admixture and thus an optimal mixture control for each operating state depending on all important parameters.
  • valve body is designed as a diaphragm-like, easily movable valve plate, that two coils connected to push-pull outputs of the pulse generator are arranged on opposite sides of the valve plate and that an address memory which can be selected by load values, speed values and temperature values is provided for control is, which contains digital information values for the pulse duty factor in the form of a map arranged in speed characteristic curves according to load and temperature parameters and special acceleration characteristic curves, so that the pulse duty factor and thus the air admixture in the intermediate chamber can be controlled according to the information values.
  • the high-speed carburetor according to the invention differs from the prior art in that the air admixture can be precisely specified by the type of valve control.
  • the valve plate is membrane-like and therefore almost inertia, so that it can follow all accelerations without delay.
  • the valve control by means of a pulsed actuation of the valve plate avoids intermediate positions of the valve plate.
  • the valve plate is essentially always completely in the open position or in the closed position.
  • the duration and the period of the individual movements are determined by the pulse duty factor of the excitation pulses.
  • the pulses can have frequencies up to 1 kHz.
  • the duty cycle is infinitely adjustable between 0% and 100%.
  • the information values for the size of the air admixture can be set independently of the intake manifold vacuum according to the essential operating parameters of the engine.
  • a special speed characteristic with low air admixture can be specified for the starting condition when the engine is cold. An automatic start can therefore be omitted.
  • acceleration phases which are recognized, for example, by a sudden change in the position of the accelerator pedal or a drop in pressure in the intake manifold. Then less additional air turns beige mixes, so that the fuel-air mixture is enriched and higher accelerations are possible. As a result, an acceleration pump can be omitted.
  • the nozzle needle ensures the emergency running properties of the engine if the flow control valve fails.
  • the invention gives the high-speed carburetor properties of a central injection.
  • the invention provides that a pneumatic actuator with an actuating piston is provided for idling control, the piston rod of which serves as an actuator for the slide, and the actuating chamber of the actuator can be connected to the intake manifold of the high-speed carburetor. that a further flow control valve controlled by a pulse generator is provided to control the actuating chamber, which controls a flow path from the actuating chamber to the atmosphere, and that when the speed falls below a target speed value, the pulse duty factor of the pulse generator is controlled in the sense of acting upon the actuating chamber with the intake manifold pressure.
  • the idling speed can be kept constant even with changes in load. It is important that the admixture of air in the intermediate chamber gives a lean mixture even when idling, so that pollutant production is low when idling.
  • the invention provides that the flow control valve has a greater flow than the throttle point on the intake manifold.
  • the combination of idle control and mixture control valve replaces the previously known temperature or time-controlled automatic starts.
  • the «rich» fuel / air mixture required for a cold start can be set via the mixture control valve.
  • the larger amount of air required for cold start and warm-up is supplied to the engine via a correspondingly enlarged slide opening.
  • the invention provides that the connection to the atmosphere contains a throttle point, the flow cross section of which is smaller than the flow cross section of the throttle point on the intake manifold.
  • a high-speed carburetor contains a slide 2 within an atomizer tube 1, which can be actuated by the accelerator pedal in the direction of arrow 37 against a restoring force and adjusts the cross section of the atomizer tube 1.
  • the suction tube 3 connects to the atomizer tube 1.
  • the slider 2 carries a nozzle needle 4 which projects into a nozzle assembly 5.
  • the nozzle assembly 5 contains two nozzles 6, 7 coaxially one behind the other, through the nozzle openings of which the nozzle needle 4 extends.
  • An intermediate chamber 8 is located between the nozzles 6 and 7.
  • the fuel is supplied via a fuel channel 9.
  • the high-speed carburetor does not require a throttle valve. The high flow velocity in the area of the nozzle ensures strong atomization and thus promotes the mixture formation.
  • the intermediate chamber 8 is connected to a flow control valve 11 via a line 10.
  • the flow control valve 11 contains two opposing pot cores 12, 13 which delimit a circular valve chamber 14 between them.
  • An outlet channel 15 to which the line 10 is connected is arranged in the core part of the pot core 12.
  • the mouth of the outlet channel 15 forms a valve seat 16.
  • Inside the valve chamber 14 there is a membrane-like valve plate 17 made of a ferromagnetic material. This valve plate 17 is light and almost without inertia. As a result, it is easily movable under the influence of the magnetic field and always lies fully against the valve mouth at the frequencies used.
  • An inlet duct 18 is connected to the air filter, also not shown, via a line (not shown).
  • Each pot core 12, 13 contains a coil 19, 20.
  • the two coils 19, 20 are connected to push-pull outputs of a pulse generator 21 with a controllable duty cycle of the pulse duration to the pause duration.
  • the pulse duty factor is controlled by a control stage 22, which in turn is coupled to a map memory 23.
  • the inputs 24 of the map memory 23 carry signals about the load state, speed state and temperature state of the respective internal combustion engine.
  • the map memory 23 is designed as an address memory. The addresses are queried by the signals on the inputs 24.
  • the information values stored in the respective memory location are entered into the control stage 22 and determine the pulse generator's duty cycle. This duty cycle determines the relative opening time of the flow control valve and thus the amount of air admixture. This allows the fuel-air mixture to become leaner. In any case, the mixture state can be set precisely.
  • Fig. 2 shows in a) at an output of the pulse generator (21) the pulse shape with a duty cycle close to 0%.
  • the pulse duration is very short, the pulse pause is comparatively long.
  • the duty cycle can of course also change the value Have 0%.
  • 2b) shows a duty cycle close to 100% at the same output of the pulse generator 21.
  • the pulse duration is very long, the pulse pause is very short.
  • the duty cycle can be increased to 100%. Every duty cycle is continuously adjustable between 0% and 100%.
  • a pneumatic actuator in the form of a cylinder 31
  • the pneumatic cylinder 31 contains an actuating piston 32 with a piston rod 33 which bears on a lever 35 which can be pivoted about an axis 34.
  • the lever 35 is coupled to the slide 2 or the nozzle needle 4 via a joint 36.
  • the piston rod 33 When the piston rod 33 is extended, the nozzle needle 4 is carried along in the direction of the arrow 37 as well as when the gas lever is actuated.
  • the piston rod 33 lies loosely on the lever 35, so that the piston rod 33 is not carried along when the accelerator pedal is actuated in the direction of arrow 37.
  • the control chamber 39 of the cylinder 31 is connected via a line 40 to the interior of the intake manifold 3 via a nozzle with a throttle point 38, so that the negative pressure present in the intake manifold 3 is effective directly in the control chamber 39 of the cylinder.
  • the line 40 is connected to a channel 41 of a flow control valve 42 which, like the flow control valve 11, is designed.
  • the flow control valve 42 contains a valve plate 43 and two coils 44 and 45, which are connected to push-pull outputs of a pulse generator 46 with an adjustable duty cycle of pulse duration and pause duration.
  • the duty cycle of the pulse generator is controlled by a control stage 47.
  • a difference circuit 48 compares the nominal signal for the idling speed present on line 49 with the actual signal of the crankshaft speed present on line 50.
  • the valve plate 43 abuts the valve seat 51, the flow control valve 42 is blocked.
  • the outlet of the flow control valve is connected via a line 52 to the cylinder chamber 53 opposite the actuating chamber 39.
  • the actuating chamber 53 is connected to the atmosphere via a nozzle with a throttle point 54.
  • the throttle point 54 has a smaller flow cross section than the flow control valve 42 and the throttle point 38; in addition, the flow resistance of the flow control valve 42 is negligible compared to the flow resistances of the throttle points.
  • the pulse duty factor is controlled so that the valve plate 43 of the flow control valve 42 is lifted off the valve seat 51. As a result, there is a connection to the atmosphere through the open flow control valve 42. A flow forms with a pressure drop at the throttle point 54. Since the opposing surfaces of the piston 32 have different sizes, namely the area in the actuating chamber 39 is smaller and since essentially the same pressure prevails in both cylinder chambers, the actuating piston 32 will move to the left in relation to FIG. 1. The piston rod 33 is retracted so that the nozzle needle 4 is not influenced.
  • the pulse duty factor of the pulse generator 46 is controlled so that the flow control valve 42 is closed to an appropriate extent as a function of the speed deviation.
  • the negative pressure in the intake manifold 3 within the actuating chamber 39 and the atmospheric pressure in the cylinder chamber 53 take effect, so that the piston rod 33 is extended and the nozzle needle 4 turns on.
  • This increases the nozzle cross-section and the air cross-section so that an increased air-fuel mixture can be drawn in.
  • the idle speed increases.
  • the value of the duty cycle determines the adjustment of the slide and thus the change in the idle speed.
  • FIG. 3 A modified embodiment of the idle control is shown in FIG. 3.
  • the pneumatic actuator is designed as a diaphragm actuator 61, the actuating piston 62 of which is articulated with its piston rod 63 to an angle lever 81. Its leg 82 acts on the lever 35 via a coupling rod 83.
  • the actuating chamber 69 of the diaphragm actuator 61 contains a return spring 84.
  • the actuating chamber 69 is connected to the valve chamber 86 of the flow control valve 42 via a line 85.
  • the throttle point 38 is connected via a line 87 to the channel 41 of the flow control valve 42, the valve seat 51 of which can be shut off by the valve plate 43.
  • Another channel 88 of the flow control valve 42 which also has a shut-off valve seat 89, is connected to the atmosphere via a nozzle with a throttle point 90.
  • the diaphragm actuator is controlled in such a way that when the idle speed falls below the pulse generator 46 emits a pulse train keyed in such a way that the valve plate 86 bears against the valve seat 89.
  • the nozzle and the slide are opened, so that the air-fuel mixture is increasingly sucked in.
  • the idle speed increases.
  • the pulse generator 46 is keyed so that the valve plate 43 is held in contact with the valve seat 51.
  • Atmospheric pressure now acts within the actuating chamber 89, so that the return spring 84 resets the piston 62. As a result, the lever 35 also moves back.
  • any intermediate position of the piston 62 can be reached and the actual value of the idling speed can be adjusted to the setpoint.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)

Abstract

A high-velocity carburetor for an Otto engine comprising a slide for changing the cross-section of the suction pipe, a nozzle connection receiving nozzles and a profiled nozzle needle seated on the slide and controlling the cross-section of the nozzle. One object is the precise adjustment of the air admixture and thus an optimum mixture regulation as a function of the most important parameters for the operational conditions. The nozzle connection contains two nozzles, situated coaxially to one another and separated from one another by an intermediate chamber. The intermediate chamber is connected to an outlet channel of a flow control value having a ferromagnetic membrane-like valve plate. The valve plate is operable by two coils opposing each other and being connected to push-pull outputs of a pulse generator with adjustable pulse duty factor. An input channel of the flow control valve is connected with the atmospheric air via an air filter. For the control of the pulse duty factor an address memory is provided which can be addressed by load values, speed values, and temperature values and which contains in the form of a performance characteristic field information values for the pulse duty factor so that the pulse duty factor and thus the air admixture in the intermediate chamber can be adjusted in accordance with said information values.

Description

Die Erfindung betrifft einen Hochgeschwindigkeitsvergaser für einen Ottomotor mit einem den Saugrohrquerschnitt verändernden Schieber, mit einem zwei koaxial zueinander liegende, durch eine Zwischenkammer voneinander getrennte Düsen aufnehmenden Düsenstock und mit einer profilierten, an dem Schieber sitzenden den Düsenquerschnitt steuernden Düsennadel, und bei welcher die Zwischenkammer an den Austrittskanal eines Durchflusssteuerventils mit einem ferromagnetischen Ventilkörper angeschlossen ist, der Ventilkörper durch eine an einen Impulsgenerator mit einstellbarem Tastverhältnis angeschlossene Spule betätigbar ist, der Eintrittskanal des Durchflusssteuerventils mit der atmosphärischen Luft verbunden ist und die Steuerung des Tastverhältnisses in Abhängigkeit von Betriebswerten erfolgt.The invention relates to a high-speed carburetor for a gasoline engine with a slide that changes the intake manifold cross-section, with a two coaxially arranged nozzle receptacle that is separated from one another by an intermediate chamber, and with a profiled nozzle needle that controls the nozzle cross-section and sits on the slide, and with which the intermediate chamber the outlet channel of a flow control valve is connected to a ferromagnetic valve body, the valve body can be actuated by a coil connected to a pulse generator with an adjustable duty cycle, the inlet channel of the flow control valve is connected to the atmospheric air, and the duty cycle is controlled as a function of operating values.

Ein solcher Hochgeschwindigkeitsvergaser mit Schieber hat keine Drosselklappe, so dass im Gegensatz zu einem Gleichdruckvergaser im Bereich des Schiebers an der Düse praktisch der volle Saugrohrdruck ansteht. Infolgedessen ergeben sich, speziell im Teillastbereich, sehr hohe Strömungsgeschwindigkeiten an der Düse und damit gute Zerstäubungseigenschaften.Such a high-speed carburetor with slide has no throttle valve, so that, in contrast to a constant pressure carburetor, practically the full intake manifold pressure is applied to the nozzle in the area of the slide. As a result, very high flow velocities at the nozzle and thus good atomization properties result, especially in the partial load range.

Entsprechend der Grösse der Ringfläche zwischen Düse und Nadel baut sich in der Zwischenkammer zwischen den beiden Düsen ein Unterdruck entsprechend dem Saugrohrunterdruck auf. Das Querschnittsverhältnis der Düsen bzw. die Steigung der Düsennadel bestimmt die Grösse des zwischen den Düsen in der Zwischenkammer vorhandenen Unterdrucks. Durch die Profilierung der Düsennadel kann man einer bestimmten Schieberstellung, d.h. einem bestimmten Unterdruck, eine Kraftstoffmenge zuordnen. Diese Kraftstoffmenge liegt jedoch nicht immer im optimalen Betriebsbereich des Motors. Wenn man für eine bestimmte Düsennadelcharakteristik die Kraftstoffzumessung so auswählt, dass sich ein fetter Gemischzustand ergibt, so kann über Luftbeimischung in der Zwischenkammer der dort herrschende Unterdruck verringert werden. Dadurch lässt sich die Kraftstoffmenge reduzieren und das Kraftstoff-Luftgemisch abmagern. Die Luftbeimischung (Vormischung) bewirkt ausser der Steuerung des Kraftstoff-Luftgemisches auch eine weitere Zerstäubungsverbesserung.Depending on the size of the ring area between the nozzle and needle, a negative pressure corresponding to the suction pipe negative pressure builds up in the intermediate chamber between the two nozzles. The cross-sectional ratio of the nozzles or the slope of the nozzle needle determines the size of the negative pressure present between the nozzles in the intermediate chamber. By profiling the nozzle needle, a certain slide position, i.e. assign a fuel quantity to a certain negative pressure. However, this amount of fuel is not always in the optimal operating range of the engine. If the fuel metering is selected for a specific nozzle needle characteristic in such a way that a rich mixture state results, then the negative pressure prevailing there can be reduced by admixing air in the intermediate chamber. This allows the amount of fuel to be reduced and the fuel-air mixture to become leaner. The air admixture (premixing) brings about a further atomization improvement in addition to the control of the fuel-air mixture.

Ein Vergaser der eingangs genannten Art ist in der US-A-3 963 009 beschrieben. Dort stellt sich der Schieber unter dem Einfluss einer Membran entsprechend dem zwischen einer Hauptdrosselklappe und dem Schieber erzeugten Unterdruck ein. Diese mechanische Einstellung ist mit einer Hysterese verbunden, so dass die Schieberstellung nicht exakt reproduzierbar und damit keine eindeutig bestimmte lastabhängige Kraftstoffzusammensetzung möglich ist. Die Zusatzluft wird in Abhängigkeit von dem Sauerstoffverhältnis im Abgas geregelt. Weitere Betriebsparameter können nicht berücksichtigt werden. Auch ist es nicht möglich, die Zusatzluft für bestimmte Betriebszustände wie Beschleunigung, Startphase zu ändern.A carburetor of the type mentioned is described in US Pat. No. 3,963,009. There, under the influence of a diaphragm, the slide adjusts itself according to the negative pressure generated between a main throttle valve and the slide. This mechanical setting is associated with a hysteresis, so that the slide position cannot be reproduced exactly and therefore no clearly determined load-dependent fuel composition is possible. The additional air is regulated depending on the oxygen ratio in the exhaust gas. Other operating parameters cannot be taken into account. It is also not possible to change the additional air for certain operating conditions such as acceleration, starting phase.

Aus der DE-A-3 143 395 ist ein Gleichdruckvergaser mit Schieber bekannt, bei dem in der Düseninnenwandung Mündungen eines Nebenluftkanals vorhanden sind, deren Öffnung durch die Bewegung der Düsennadel gesteuert wird. Dadurch soll die Nebenluftmenge geregelt und das Kraftstoff-Luft-Gemisch stabilisiert werden. Die Nebenluft wird also entsprechend der Schieberstellung gesteuert. Abhängig von der Motortemperatur kann der Nebenluftkanal beeinflusst werden. Diese Massnahmen sind jedoch weder hinsichtlich ihrer Zielsetzung noch ihrer konstruktiven Ausbildung bei einem Hochgeschwindigkeitsvergaser anwendbar.From DE-A-3 143 395 a constant pressure carburetor with a slide is known, in which there are orifices of a secondary air duct in the inner wall of the nozzle, the opening of which is controlled by the movement of the nozzle needle. This is to regulate the amount of secondary air and stabilize the fuel-air mixture. The secondary air is thus controlled according to the slide position. The secondary air duct can be influenced depending on the engine temperature. However, these measures cannot be used either with regard to their objectives or their constructive training in a high-speed carburetor.

Aufgabe der Erfindung ist eine genaue Zumessung der Luftbeimischung und damit für jeden Betriebszustand eine optimale Gemischsteuerung in Abhängigkeit von allen wichtigen Parametern.The object of the invention is a precise metering of the air admixture and thus an optimal mixture control for each operating state depending on all important parameters.

Diese Aufgabe wird nach der Erfindung dadurch gelöst, dass der Ventilkörper als membranartige, leicht bewegliche Ventilplatte ausgebildet ist, dass zwei an Gegentaktausgänge des Impulsgenerators angeschlossene Spulen auf gegenüberliegenden Seiten der Ventilplatte angeordnet sind und dass zur Steuerung ein durch Lastwerte, Drehzahlwerte und Temperaturwerte anwählbarer Adressspeicher vorgesehen ist, der in Form eines in Drehzahlkennlinien nach Last- und Temperaturparametern und nach besonderen Beschleunigungskennlinien geordneten Kennfeldes digitale Informationswerte für das Tastverhältnis enthält, so dass das Tastverhältnis und damit die Luftzumischung in der Zwischenkammer entsprechend den Informationswerten gesteuert werden kann.This object is achieved according to the invention in that the valve body is designed as a diaphragm-like, easily movable valve plate, that two coils connected to push-pull outputs of the pulse generator are arranged on opposite sides of the valve plate and that an address memory which can be selected by load values, speed values and temperature values is provided for control is, which contains digital information values for the pulse duty factor in the form of a map arranged in speed characteristic curves according to load and temperature parameters and special acceleration characteristic curves, so that the pulse duty factor and thus the air admixture in the intermediate chamber can be controlled according to the information values.

Der Hochgeschwindigkeitsvergaser nach der Erfindung unterscheidet sich insofern vom Stand der Technik, als die Luftbeimischung durch die Art der Ventilsteuerung genau vorgegeben werden kann. Die Ventilplatte ist membranartig ausgebildet und daher nahezu trägheitslos, so dass sie verzögerungsfrei allen Beschleunigungen folgen kann. Die Ventilsteuerung mittels einer impulsartigen Betätigung der Ventilplatte vermeidet Zwischenstellungen der Ventilplatte. Die Ventilplatte ist im wesentlichen immer vollständig in der Offenstellung bzw. in der Schliessstellung. Die Dauer und die Periode der einzelnen Bewegungen sind durch das Tastverhältnis der Erregerimpulse festgelegt. Die Impulse können Frequenzen bis zu 1 kHz haben. Das Tastverhältnis ist stufenlos zwischen 0% und 100% verstellbar. Die Informationswerte für die Grösse der Luftbeimischung sind unabhängig vom Saugrohrunterdruck nach den wesentlichen Betriebsparametern des Motors einstellbar. Man kann für den Anlaufzustand bei kaltem Motor eine besondere Drehzahlkennlinie mit niedriger Luftbeimischung vorgeben. Eine Startautomatik kann daher entfallen. Gleiches gilt für Beschleunigungsphasen, die etwa durch eine sprunghafte Änderung der Stellung des Gaspedals bzw. einen Druckabfall im Saugrohr erkannt werden. Dann wird weniger Zusatzluft beigemischt, so dass das Kraftstoff-Luft-Gemisch angefettet wird und höhere Beschleunigungen möglich sind. Eine Beschleunigungspumpe kann infolgedessen entfallen.The high-speed carburetor according to the invention differs from the prior art in that the air admixture can be precisely specified by the type of valve control. The valve plate is membrane-like and therefore almost inertia, so that it can follow all accelerations without delay. The valve control by means of a pulsed actuation of the valve plate avoids intermediate positions of the valve plate. The valve plate is essentially always completely in the open position or in the closed position. The duration and the period of the individual movements are determined by the pulse duty factor of the excitation pulses. The pulses can have frequencies up to 1 kHz. The duty cycle is infinitely adjustable between 0% and 100%. The information values for the size of the air admixture can be set independently of the intake manifold vacuum according to the essential operating parameters of the engine. A special speed characteristic with low air admixture can be specified for the starting condition when the engine is cold. An automatic start can therefore be omitted. The same applies to acceleration phases which are recognized, for example, by a sudden change in the position of the accelerator pedal or a drop in pressure in the intake manifold. Then less additional air turns beige mixes, so that the fuel-air mixture is enriched and higher accelerations are possible. As a result, an acceleration pump can be omitted.

Andererseits sichert die Düsennadel die Notlaufeigenschaften des Motors, wenn das Durchflusssteuerventil ausfällt. Insgesamt verleiht die Erfindung dem Hochgeschwindigkeitsvergaser Eigenschaften einer Zentraleinspritzung.On the other hand, the nozzle needle ensures the emergency running properties of the engine if the flow control valve fails. Overall, the invention gives the high-speed carburetor properties of a central injection.

Damit auch der Leerlauf des Ottomotors mit Hochgeschwindigkeitsvergaser regelbar ist, sieht die Erfindung vor, dass zur Leerlaufregelung ein pneumatisches Stellglied mit einem Stellkolben vorgesehen ist, dessen Kolbenstange als Stellglied für den Schieber dient, dass die Stellkammer des Stellgliedes mit dem Saugrohr des Hochgeschwindigkeitsvergasers verbindbar ist, dass zur Steuerung der Stellkammer ein weiteres von einem Impulsgenerator gesteuertes Durchflusssteuerventil vorgesehen ist, das einen Strömungsweg von der Stellkammer zur Atmosphäre steuert, und dass bei Unterschreiten eines Solldrehzahlwertes das Tastverhältnis des Impulsgenerators im Sinne einer Beaufschlagung der Stellkammer mit dem Saugrohrdruck gesteuert wird.In order that the idling of the gasoline engine can also be controlled with a high-speed carburetor, the invention provides that a pneumatic actuator with an actuating piston is provided for idling control, the piston rod of which serves as an actuator for the slide, and the actuating chamber of the actuator can be connected to the intake manifold of the high-speed carburetor. that a further flow control valve controlled by a pulse generator is provided to control the actuating chamber, which controls a flow path from the actuating chamber to the atmosphere, and that when the speed falls below a target speed value, the pulse duty factor of the pulse generator is controlled in the sense of acting upon the actuating chamber with the intake manifold pressure.

Mit dieser Anordnung erreicht man, dass die Leerlaufdrehzahl auch bei Belastungsänderungen konstant gehalten werden kann. Wichtig ist, dass man durch die Luftbeimischung in der Zwischenkammer auch im Leerlauf ein mageres Gemisch erhält, so dass die Schadstoffproduktion im Leerlauf gering ist.With this arrangement it is achieved that the idling speed can be kept constant even with changes in load. It is important that the admixture of air in the intermediate chamber gives a lean mixture even when idling, so that pollutant production is low when idling.

Damit sich der Unterdruck im Saugrohr möglichst schnell innerhalb des pneumatischen Zylinders auswirken kann, sieht die Erfindung vor, dass das Durchflusssteuerventil einen grösseren Durchfluss als die Drosselstelle an dem Saugrohr hat. Ausser der beschriebenen Leerlaufregelung ersetzt die Kombination von Leerlaufregelung und Gemischsteuerventil die bisher bekannten temperatur- bzw. zeitgesteuerten Startautomatiken. Über das Gemischsteuerventil kann das für Kaltstart benötigte «fette» Kraftstoff-Luftgemisch eingestellt werden. Über die temperaturabhängige Vorgabe einer gegenüber der Heissleerlaufdrehzahl überhöhten Warmlaufdrehzahl wird dem Motor die benötigte grössere Luftmenge bei Kaltstart und Warmlauf über eine entsprechend vergrösserte Schieberöffnung zugeführt.So that the negative pressure in the intake manifold can act as quickly as possible within the pneumatic cylinder, the invention provides that the flow control valve has a greater flow than the throttle point on the intake manifold. In addition to the idle control described, the combination of idle control and mixture control valve replaces the previously known temperature or time-controlled automatic starts. The «rich» fuel / air mixture required for a cold start can be set via the mixture control valve. Via the temperature-dependent specification of a warm-up speed that is excessive compared to the hot idling speed, the larger amount of air required for cold start and warm-up is supplied to the engine via a correspondingly enlarged slide opening.

Damit die Leerlaufregelung für den Unterdruck im Saugrohr eine möglichst geringe Belastung darstellt und damit die Rückstellung des Stellgliedes verzögert erfolgt, sieht die Erfindung vor, dass die Verbindung zur Atmosphäre eine Drosselstelle enthält, deren Durchflussquerschnitt kleiner als der Durchflussquerschnitt der Drosselstelle an dem Saugrohr ist.So that the idle control for the negative pressure in the intake manifold represents the lowest possible load and the actuating element is reset with a delay, the invention provides that the connection to the atmosphere contains a throttle point, the flow cross section of which is smaller than the flow cross section of the throttle point on the intake manifold.

Eine Ausführungsform der Erfindung wird im folgenden unter Bezugnahme auf die anliegende Zeichnung erläutert, in der darstellen:

  • Fig. 1 den Hochgeschwindigkeitsvergaser schematisch,
  • Fig. 2 ein Impulsdiagramm für die Steuerung des Durchflusssteuerventils und
  • Fig. 3 eine abgewandelte Ausführungsform der Erfindung.
An embodiment of the invention is explained below with reference to the accompanying drawing, in which:
  • 1 shows the high-speed carburetor schematically,
  • Fig. 2 is a timing diagram for the control of the flow control valve and
  • Fig. 3 shows a modified embodiment of the invention.

Ein Hochgeschwindigkeitsvergaser enthält innerhalb eines Zerstäuberrohres 1 einen Schieber 2, der von dem Gaspedal in Pfeilrichtung 37 entgegen einer Rückstellkraft betätigbar ist und den Querschnitt des Zerstäuberrohres 1 einstellt. An das Zerstäuberrohr 1 schliesst sich das Saugrohr 3 an. Der Schieber 2 trägt eine Düsennadel 4, die in einen Düsenstock 5 hineinragt. Der Düsenstock 5 enthält koaxial hintereinander zwei Düsen 6, 7, durch deren Düsenöffnungen die Düsennadel 4 hindurchreicht. Zwischen den Düsen 6 und 7 befindet sich eine Zwischenkammer 8. Der Kraftstoff wird über einen Kraftstoffkanal 9 zugeführt. Der Hochgeschwindigkeitsvergaser benötigt keine Drosselklappe. Die hohe Strömungsgeschwindigkeit im Bereich der Düse sichert eine starke Zerstäubung und fördert so die Gemischausbildung.A high-speed carburetor contains a slide 2 within an atomizer tube 1, which can be actuated by the accelerator pedal in the direction of arrow 37 against a restoring force and adjusts the cross section of the atomizer tube 1. The suction tube 3 connects to the atomizer tube 1. The slider 2 carries a nozzle needle 4 which projects into a nozzle assembly 5. The nozzle assembly 5 contains two nozzles 6, 7 coaxially one behind the other, through the nozzle openings of which the nozzle needle 4 extends. An intermediate chamber 8 is located between the nozzles 6 and 7. The fuel is supplied via a fuel channel 9. The high-speed carburetor does not require a throttle valve. The high flow velocity in the area of the nozzle ensures strong atomization and thus promotes the mixture formation.

Die Zwischenkammer 8 ist über eine Leitung 10 mit einem Durchflusssteuerventil 11 verbunden. Das Durchflusssteuerventil 11 enthält zwei einander gegenüberstehende Topfkerne 12, 13, die zwischen sich eine kreisförmige Ventilkammer 14 begrenzen. In dem Kernteil des Topfkernes 12 ist ein Austrittskanal 15 angeordnet, an den die Leitung 10 angeschlossen ist. Die Mündung des Austrittskanals 15 bildet einen Ventilsitz 16. Innerhalb der Ventilkammer 14 befindet sich eine membranartige Ventilplatte 17 aus einem ferromagnetischen Stoff. Diese Ventilplatte 17 ist leicht und nahezu tragheitslos. Sie ist infolgedessen unter dem Einfluss des Magnetfeldes leicht beweglich und legt sich bei den angewandten Frequenzen immer voll an die jeweilige Ventilmündung an. Ein Eintrittskanal 18 ist über eine nichtdargestellte Leitung mit dem ebenfalls nicht dargestellten Luftfilter verbunden.The intermediate chamber 8 is connected to a flow control valve 11 via a line 10. The flow control valve 11 contains two opposing pot cores 12, 13 which delimit a circular valve chamber 14 between them. An outlet channel 15 to which the line 10 is connected is arranged in the core part of the pot core 12. The mouth of the outlet channel 15 forms a valve seat 16. Inside the valve chamber 14 there is a membrane-like valve plate 17 made of a ferromagnetic material. This valve plate 17 is light and almost without inertia. As a result, it is easily movable under the influence of the magnetic field and always lies fully against the valve mouth at the frequencies used. An inlet duct 18 is connected to the air filter, also not shown, via a line (not shown).

Jeder Topfkern 12, 13 enthält eine Spule 19, 20. Die beiden Spulen 19, 20 sind an Gegentaktausgänge eines Impulsgenerators 21 mit steuerbarem Tastverhältnis der Impulsdauer zur Pausendauer angeschlossen. Das Tastverhältnis ist durch eine Steuerstufe 22 gesteuert, die ihrerseits mit einem Kennfeldspeicher 23 gekoppelt ist. Die Eingänge 24 des Kennfeldspeichers 23 führen Signale über den Lastzustand, Drehzahlzustand und Temperaturzustand des jeweiligen Verbrennungsmotors. Der Kennfeldspeicher 23 ist als Adressspeicher ausgebildet. Die Adressen werden durch die Signale auf den Eingängen 24 abgefragt. Die in dem jeweiligen Speicherplatz gespeicherten Informationswerte werden in die Steuerstufe 22 eingegeben und legen das Tastverhältnis des Impulsgenerators fest. Dieses Tastverhältnis legt die relative Öffnungsdauer des Durchflusssteuerventils und damit die Menge der Luftbeimischung fest. Dadurch kann das Kraftstoff-Luftgemisch abgemagert werden. Jedenfalls lässt sich der Gemischzustand genau einstellen.Each pot core 12, 13 contains a coil 19, 20. The two coils 19, 20 are connected to push-pull outputs of a pulse generator 21 with a controllable duty cycle of the pulse duration to the pause duration. The pulse duty factor is controlled by a control stage 22, which in turn is coupled to a map memory 23. The inputs 24 of the map memory 23 carry signals about the load state, speed state and temperature state of the respective internal combustion engine. The map memory 23 is designed as an address memory. The addresses are queried by the signals on the inputs 24. The information values stored in the respective memory location are entered into the control stage 22 and determine the pulse generator's duty cycle. This duty cycle determines the relative opening time of the flow control valve and thus the amount of air admixture. This allows the fuel-air mixture to become leaner. In any case, the mixture state can be set precisely.

Fig. 2 zeigt in a) an einem Ausgang des Impulsgenerators (21) die Impulsform mit einem Tastverhältnis nahe 0%. Die Impulsdauer ist sehr klein, die Impulspause vergleichsweise lang. Das Tastverhältnis kann selbstverständlich auch den Wert 0% haben. Fig. 2b) zeigt ein Tastverhältnis nahe 100% an demselben Ausgang des Impulsgenerators 21. Die Impulsdauer ist sehr lang, die Impulspause sehr kurz. Das Tastverhältnis kann bis auf 100% gesteigert werden. Zwischen 0% und 100% ist jedes Tastverhältnis stufenlos einstellbar.Fig. 2 shows in a) at an output of the pulse generator (21) the pulse shape with a duty cycle close to 0%. The pulse duration is very short, the pulse pause is comparatively long. The duty cycle can of course also change the value Have 0%. 2b) shows a duty cycle close to 100% at the same output of the pulse generator 21. The pulse duration is very long, the pulse pause is very short. The duty cycle can be increased to 100%. Every duty cycle is continuously adjustable between 0% and 100%.

Man kann also für eine Mehrzahl von Drehzahlkennlinien, die parameterabhängig anwählbar sind, das Mischungsverhältnis des Kraftstoff-LuftGemisches durch Luftbeimischung festlegen. Diese Kennlinien, die in dem Adressspeicher abgespeichert sind, bilden ein Kennfeld, das eine optimale Gemischzusammensetzung garantiert.It is therefore possible to determine the mixing ratio of the fuel-air mixture by adding air to a plurality of speed characteristics, which can be selected depending on the parameters. These characteristics, which are stored in the address memory, form a map that guarantees an optimal mixture composition.

Bei Ottomotoren bereitet die Leerlaufeinstellung Schwierigkeiten, weil sich die Leerlaufdrehzahl bei Belastungsänderungen leicht ändert. Bei vorgegebener Leerlaufdrehzahl muss man normalerweise mit einem überfetteten Kraftstoff-Luft- gemisch fahren, damit ein einwandfreier Leerlauf gewährleistet ist und der Motor nicht stehenbleibt. Dieses bedeutet eine erhöhte Schadstoffproduktion.With petrol engines, idling adjustment is difficult because the idling speed changes slightly when the load changes. At a given idle speed, you normally have to drive with an over-rich fuel-air mixture so that perfect idling is guaranteed and the engine does not stop. This means an increased pollutant production.

In Weiterbildung der Erfindung ist eine Regelung der Leerlaufdrehzahl mittels eines pneumatischen Stellgliedes in Form eines Zylinders 31 vorgesehen. In der Zeichnung ist der Zylinder 31 nur schematisch angegeben. Seine wirkliche Lage schneidet selbstverständlich nicht den Ansaugkanal. Der pneumatische Zylinder 31 enthält einen Stellkolben 32 mit einer Kolbenstange 33, die an einem um eine Achse 34 schwenkbaren Hebel 35 anliegt. Der Hebel 35 ist über ein Gelenk 36 mit dem Schieber 2 bzw. der Düsennadel 4 gekoppelt. Beim Ausfahren der Kolbenstange 33 wird jeweils die Düsennadel 4 ebenso wie bei einer Betätigung des Gashebels in Pfeilrichtung 37 mitgenommen. Andererseits liegt die Kolbenstange 33 an dem Hebel 35 lose an, so dass die Kolbenstange 33 bei einer Betätigung des Gaspedals in Pfeilrichtung 37 nicht mitgenommen wird.In a development of the invention, regulation of the idling speed by means of a pneumatic actuator in the form of a cylinder 31 is provided. In the drawing, the cylinder 31 is only shown schematically. Of course, its real position does not cut the intake duct. The pneumatic cylinder 31 contains an actuating piston 32 with a piston rod 33 which bears on a lever 35 which can be pivoted about an axis 34. The lever 35 is coupled to the slide 2 or the nozzle needle 4 via a joint 36. When the piston rod 33 is extended, the nozzle needle 4 is carried along in the direction of the arrow 37 as well as when the gas lever is actuated. On the other hand, the piston rod 33 lies loosely on the lever 35, so that the piston rod 33 is not carried along when the accelerator pedal is actuated in the direction of arrow 37.

Über eine Düse mit einer Drosselstelle 38 ist die Stellkammer 39 des Zylinders 31 über eine Leitung 40 mit dem Inneren des Saugrohres 3 verbunden, so dass der im Saugrohr 3 anstehende Unterdruck unmittelbar in der Stellkammer 39 des Zylinders wirksam ist. Die Leitung 40 ist andererseits an einen Kanal 41 eines Durchflusssteuerventils 42 angeschlossen, das ebenso wie das Durchflusssteuerventil 11 ausgebildet ist. Das Durchflusssteuerventil 42 enthält eine Ventilplatte 43 und zwei Spulen 44 und 45, die an Gegentaktausgänge eines Impulsgenerators 46 mit einstellbarem Tastverhältnis von Impulsdauer und Pausendauer angeschlossen sind. Das Tastverhältnis des Impulsgenerators wird von einer Steuerstufe 47 gesteuert. Ein Differenzkreis 48 vergleicht das auf einer Leitung 49 anstehende Sollsignal für die Leerlaufdrehzahl mit dem auf der Leitung 50 anstehenden Istsignal der Kurbelwellendrehzahl. Wenn die Ventilplatte 43 an dem Ventilsitz 51 anliegt, ist das Durchflusssteuerventil 42 gesperrt. Der Ausgang des Durchflusssteuerventils ist über eine Leitung 52 mit der der Stellkammer 39 gegenüberliegenden Zylinderkammer 53 verbunden. Die Stellkammer 53 ist über eine Düse mit einer Drosselstelle 54 mit der Atmosphäre verbunden. Die Drosselstelle 54 hat einen kleineren Durchflussquerschnitt als das Durchflusssteuerventil 42 und die Drosselstelle 38; ausserdem ist der Durchflusswiderstand des Durchflusssteuerventils 42 gegenüber den Durchflusswiderständen der Drosselstellen vernachlässigbar.The control chamber 39 of the cylinder 31 is connected via a line 40 to the interior of the intake manifold 3 via a nozzle with a throttle point 38, so that the negative pressure present in the intake manifold 3 is effective directly in the control chamber 39 of the cylinder. The line 40, on the other hand, is connected to a channel 41 of a flow control valve 42 which, like the flow control valve 11, is designed. The flow control valve 42 contains a valve plate 43 and two coils 44 and 45, which are connected to push-pull outputs of a pulse generator 46 with an adjustable duty cycle of pulse duration and pause duration. The duty cycle of the pulse generator is controlled by a control stage 47. A difference circuit 48 compares the nominal signal for the idling speed present on line 49 with the actual signal of the crankshaft speed present on line 50. When the valve plate 43 abuts the valve seat 51, the flow control valve 42 is blocked. The outlet of the flow control valve is connected via a line 52 to the cylinder chamber 53 opposite the actuating chamber 39. The actuating chamber 53 is connected to the atmosphere via a nozzle with a throttle point 54. The throttle point 54 has a smaller flow cross section than the flow control valve 42 and the throttle point 38; in addition, the flow resistance of the flow control valve 42 is negligible compared to the flow resistances of the throttle points.

Solange der Istwert der Leerlaufdrehzahl auf der Leitung 50 grösser als der Sollwert auf der Leitung 49 ist, wird das Tastverhältnis so gesteuert, dass die Ventilplatte 43 des Durchflusssteuerventils 42 von dem Ventilsitz 51 abgehoben ist. Infolgedessen besteht über das geöffnete Durchflusssteuerventil 42 eine Verbindung zur Atmosphäre. Es bildet sich eine Strömung mit einem Druckabfall an der Drosselstelle 54 aus. Da die einander gegenüberstehenden Flächen des Kolbens 32 unterschiedliche Grössen haben, und zwar die Fläche in der Stellkammer 39 kleiner ist und da in beiden Zylinderkammern im wesentlichen derselbe Druck herrscht, wird sich der Stellkolben 32 bezogen auf Fig. 1 nach links bewegen. Die Kolbenstange 33 wird zurückgefahren, so dass keine Beeinflussung der Düsennadel 4 erfolgt.As long as the actual value of the idling speed on line 50 is greater than the setpoint on line 49, the pulse duty factor is controlled so that the valve plate 43 of the flow control valve 42 is lifted off the valve seat 51. As a result, there is a connection to the atmosphere through the open flow control valve 42. A flow forms with a pressure drop at the throttle point 54. Since the opposing surfaces of the piston 32 have different sizes, namely the area in the actuating chamber 39 is smaller and since essentially the same pressure prevails in both cylinder chambers, the actuating piston 32 will move to the left in relation to FIG. 1. The piston rod 33 is retracted so that the nozzle needle 4 is not influenced.

Wenn der Istwert der Leerlaufdrehzahl unter den gewünschten Sollwert absinkt, wird das Tastverhältnis des Impulsgenerators 46 so gesteuert, dass das Durchflusssteuerventil 42 in entsprechendem Ausmass in Abhängigkeit von der Drehzahlabweichung geschlossen wird. Infolgedessen wird der Unterdruck im Saugrohr 3 innerhalb der Stellkammer 39 und der Atmosphärendruck in der Zylinderkammer 53 wirksam, so dass die Kolbenstange 33 ausgefahren wird und die Düsennadel 4 anstellt. Damit wird der Düsenquerschnitt und der Luftquerschnitt vergrössert, so dass vermehrt Luft-Kraftstoff-Gemisch angesaugt werden kann. Die Leerlaufdrehzahl steigt an. Der Wert des Tastverhältnisses legt die Verstellung des Schiebers und damit die Änderung der Leerlaufdrehzahl fest.If the actual value of the idle speed drops below the desired setpoint, the pulse duty factor of the pulse generator 46 is controlled so that the flow control valve 42 is closed to an appropriate extent as a function of the speed deviation. As a result, the negative pressure in the intake manifold 3 within the actuating chamber 39 and the atmospheric pressure in the cylinder chamber 53 take effect, so that the piston rod 33 is extended and the nozzle needle 4 turns on. This increases the nozzle cross-section and the air cross-section so that an increased air-fuel mixture can be drawn in. The idle speed increases. The value of the duty cycle determines the adjustment of the slide and thus the change in the idle speed.

Eine abgewandelte Ausführungsform der Leerlaufregelung ist in Fig. 3 dargestellt. In diesem Fall ist das pneumatische Stellglied als Membransteller 61 ausgebildet, dessen Stellkolben 62 mit seiner Kolbenstange 63 an einen Winkelhebel 81 angelenkt ist. Dessen Schenkel 82 beaufschlagt über eine Koppelstange 83 den Hebel 35. Die Stellkammer 69 des Membranstellers 61 enthält eine Rückstellfeder 84. Die Stellkammer 69 ist über eine Leitung 85 mit der Ventilkammer 86 des Durchflusssteuerventils 42 verbunden. Die Drosselstelle 38 ist über eine Leitung 87 mit dem Kanal 41 des Durchflusssteuerventils 42 verbunden, dessen Ventilsitz 51 durch die Ventilplatte 43 absperrbar ist. Ein weiterer Kanal 88 des Durchflusssteuerventils 42, der ebenfalls einen absperrbaren Ventilsitz 89 aufweist, ist über eine Düse mit einer Drosselstelle 90 mit der Atmosphäre verbunden.A modified embodiment of the idle control is shown in FIG. 3. In this case, the pneumatic actuator is designed as a diaphragm actuator 61, the actuating piston 62 of which is articulated with its piston rod 63 to an angle lever 81. Its leg 82 acts on the lever 35 via a coupling rod 83. The actuating chamber 69 of the diaphragm actuator 61 contains a return spring 84. The actuating chamber 69 is connected to the valve chamber 86 of the flow control valve 42 via a line 85. The throttle point 38 is connected via a line 87 to the channel 41 of the flow control valve 42, the valve seat 51 of which can be shut off by the valve plate 43. Another channel 88 of the flow control valve 42, which also has a shut-off valve seat 89, is connected to the atmosphere via a nozzle with a throttle point 90.

Die Regelung des Membranstellers erfolgt in der Weise, dass bei Unterschreiten der Leerlaufdrehzahl der Impulsgenerator 46 eine derart getastete Impulsfolge abgibt, dass die Ventilplatte 86 an dem Ventilsitz 89 anliegt. Infolgedessen ist der volle Unterdruck des Saugrohrs 3 über die Drosselstelle 38 in der Stellkammer 69 wirksam, so dass der Hebel 35 angestellt wird. Infolgedessen werden die Düse und der Schieber geöffnet, so dass vermehrt Luft-Kraftstoff-Gemisch angesaugt wird. Die Leerlaufdrehzahl steigt infolgedessen an. Sobald die Leerlaufdrehzahl ihren Sollwert erreicht, wird der Impulsgenerator 46 umgetastet, so dass die Ventilplatte 43 an dem Ventilsitz 51 in Anlage gehalten wird. Nunmehr wird innerhalb der Stellkammer 89 Atmosphärendruck wirksam, so dass die Rückstellfeder 84 den Kolben 62 zurückstellt. Der Hebel 35 bewegt sich infolgedessen ebenfalls zurück. Durch Steuerung des Tastverhältnisses kann man jede Zwischenstellung des Kolbens 62 erreichen und so den Istwert der Leerlaufdrehzahl jeweils auf den Sollwert nachführen.The diaphragm actuator is controlled in such a way that when the idle speed falls below the pulse generator 46 emits a pulse train keyed in such a way that the valve plate 86 bears against the valve seat 89. As a result, the full negative pressure of the suction pipe 3 via the throttle point 38 in the actuating chamber 69, so that the lever 35 is turned on. As a result, the nozzle and the slide are opened, so that the air-fuel mixture is increasingly sucked in. As a result, the idle speed increases. As soon as the idle speed reaches its desired value, the pulse generator 46 is keyed so that the valve plate 43 is held in contact with the valve seat 51. Atmospheric pressure now acts within the actuating chamber 89, so that the return spring 84 resets the piston 62. As a result, the lever 35 also moves back. By controlling the duty cycle, any intermediate position of the piston 62 can be reached and the actual value of the idling speed can be adjusted to the setpoint.

Claims (7)

1. High-velocity carburettor for an Otto engine comprising a slide (3), which changes the cross section of the induction pipe, a jet connection, which accommodates two jets (6, 7) disposed coaxially with respect to one another and separated from one another by an intermediate chamber (8), and a profiled jet needle (4) which is mounted on the slide and controls the jet cross section, in which the intermediate chamber (8) is connected to the outlet port (15) of a flow control valve (11) with a ferromagnetic valve body (17), the valve body (17) can be operated by a coil (19, 20) which is connected to a pulse generator (21) with an adjustable duty factor, the inlet port (18) of the flow control valve (11) is connected to the atmospheric air and the duty factor is controlled in accordance with operating data, characterised in that the valve body is formed as a diaphragm-like valve plate (17) which can easily be moved, that two coils (19, 20), which are connected to opposite polarity outputs of the pulse generator, are arranged on opposite sides of the valve plate, and that an address memory (23), which can be addressed using load values, speed values and temperature values and which contains digital data, in the form of a family of characteristics arranged in speed characteristics according to load and temperature parameters and special acceleration characteristics, for the duty factor, is provided for control purposes, so that the duty factor and thus the air addition in the intermediate chamber can be controlled in accordance with the data.
2. High-velocity carburettor according to claim 1, characterised in that a pneumatic adjusting element (31, 61) with an adjusting piston (32, 62) is provided for idling adjustment, the piston rod (33, 63) of which piston serves as an adjusting element for the slide (2), that the adjusting chamber (39, 69) of the adjusting element can be connected to the induction pipe (3) of the high-velocity carburettor, that a further flow control valve (43), which is controlled by a pulse generator (46), is provided to control the adjusting chamber (39, 69) and controls a flow path from the adjusting chamber to the atmosphere, and that if a nominal speed value is not reached the duty factor of the pulse generator (46) is controlled in the sense that the induction pipe pressure is effective in the adjusting chamber.
3. High-velocity carburettor according to claim 2, characterised in that the connection between the adjusting chamber and the induction pipe contains a constriction (38).
4. High-velocity carburettor according to claim 2 or 3, characterised in that the flow through the flow control valve (42) is greater than that through the constriction (38) at the induction pipe (3).
5. High-velocity carburettor according to one of claims 3 to 4, characterised in that the connection to the atmosphere contains a further constriction (54, 90) whose flow cross section is smaller that the flow cross section of the constriction (33) to the induction pipe.
6. High-velocity carburettor according to one of claims 2 to 5, characterised in that the adjusting element is formed as a double-acting cylinder (31), the adjusting chamber (39) of which is traversed by the piston rod and is directly connected to the induction pipe and the opposite cylinder chamber (53) of which is connected on one side to the atmosphere and on the other to the flow control valve (42).
7. High-velocity carburettor according to one of claims 2 to 5, characterised in that the adjusting element is formed as a diaphragm adjuster (61), the adjusting chamber (69) of which is connected to the valve chamber (86) of the flow control valve (42), that a port (41), which leads to a closeable valve seat (51), of the flow control valve (42) is connected to the induction pipe, and the other port (88), which leads to a closeable valve seat (89), of the flow control valve is connected to the atmosphere, the valve plate (43) co-operating with both valve seats.
EP84110945A 1983-10-13 1984-09-13 High-speed carburetter for an otto engine Expired EP0138070B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84110945T ATE36739T1 (en) 1983-10-13 1984-09-13 HIGH SPEED CARBURETTOR FOR A GASOLINE ENGINE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3337261 1983-10-13
DE19833337261 DE3337261A1 (en) 1983-10-13 1983-10-13 CARBURETTOR FOR AN OTTO ENGINE

Publications (3)

Publication Number Publication Date
EP0138070A2 EP0138070A2 (en) 1985-04-24
EP0138070A3 EP0138070A3 (en) 1986-03-19
EP0138070B1 true EP0138070B1 (en) 1988-08-24

Family

ID=6211744

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84110945A Expired EP0138070B1 (en) 1983-10-13 1984-09-13 High-speed carburetter for an otto engine

Country Status (6)

Country Link
US (1) US4627401A (en)
EP (1) EP0138070B1 (en)
JP (1) JPS60101261A (en)
AT (1) ATE36739T1 (en)
CA (1) CA1233381A (en)
DE (2) DE3337261A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3736757C1 (en) * 1987-10-30 1989-05-18 Black & Decker Overseas Ag Table milling device
DE3902283A1 (en) * 1989-01-26 1990-08-02 Vdo Schindling FUEL-AIR MIXTURE FOR COMBUSTION ENGINES
US6840509B2 (en) * 2000-03-17 2005-01-11 Michael Blixt Carburetor for an internal combustion engine
SE522940C2 (en) * 2000-03-17 2004-03-16 Michael Blixt Carburetor for an internal combustion engine
US6672570B2 (en) * 2000-11-17 2004-01-06 Walbro Japan, Inc. Variable venturi carburetor
US7628387B1 (en) * 2008-07-03 2009-12-08 Briggs And Stratton Corporation Engine air/fuel mixing apparatus

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US2911183A (en) * 1955-04-07 1959-11-03 Baso Inc Magnetic valves
US3383084A (en) * 1966-12-12 1968-05-14 Air Force Usa Pulse-actuated valve
JPS5118023B2 (en) * 1972-04-14 1976-06-07
FR2228158B1 (en) * 1973-05-04 1977-08-19 Sibe
JPS5142269B2 (en) * 1973-05-18 1976-11-15
JPS5333048Y2 (en) * 1974-12-07 1978-08-15
JPS572673Y2 (en) * 1976-03-18 1982-01-18
JPS5698545A (en) * 1980-01-10 1981-08-08 Fuji Heavy Ind Ltd Air fuel ratio controller
FR2478202A1 (en) * 1980-03-17 1981-09-18 Sibe CARBURETOR DEVICE FOR INTERNAL COMBUSTION ENGINE
JPS5781148A (en) * 1980-11-10 1982-05-21 Toyota Motor Corp Variable venturi carburetor
DE3222439C2 (en) * 1981-06-17 1984-05-17 Bosch und Pierburg System oHG, 4040 Neuss Device for the speed-dependent closing limitation of a carburetor main throttle
JPS58106158A (en) * 1981-12-21 1983-06-24 Toyota Motor Corp Feeding fuel control unit for variable choke carburetor
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US4517134A (en) * 1982-12-27 1985-05-14 Nissan Motor Company, Ltd. Variable venturi carburetor

Also Published As

Publication number Publication date
EP0138070A3 (en) 1986-03-19
DE3473624D1 (en) 1988-09-29
DE3337261C2 (en) 1990-07-05
DE3337261A1 (en) 1985-05-02
EP0138070A2 (en) 1985-04-24
ATE36739T1 (en) 1988-09-15
US4627401A (en) 1986-12-09
CA1233381A (en) 1988-03-01
JPS60101261A (en) 1985-06-05

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