EP0131694A2 - Device for controlling the idle speed of an internal-combustion engine - Google Patents

Device for controlling the idle speed of an internal-combustion engine Download PDF

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Publication number
EP0131694A2
EP0131694A2 EP84103881A EP84103881A EP0131694A2 EP 0131694 A2 EP0131694 A2 EP 0131694A2 EP 84103881 A EP84103881 A EP 84103881A EP 84103881 A EP84103881 A EP 84103881A EP 0131694 A2 EP0131694 A2 EP 0131694A2
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EP
European Patent Office
Prior art keywords
spring
decoupling
baffle plate
valve element
return spring
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Granted
Application number
EP84103881A
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German (de)
French (fr)
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EP0131694B1 (en
EP0131694A3 (en
Inventor
Andreas Sausner
Gerhard Ruschek
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Mannesmann VDO AG
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Mannesmann VDO AG
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    • 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
    • F02M3/00—Idling devices for carburettors
    • F02M3/06—Increasing idling speed
    • F02M3/07—Increasing idling speed by positioning the throttle flap stop, or by changing the fuel flow cross-sectional area, by electrical, electromechanical or electropneumatic means, according to engine speed
    • F02M3/075—Increasing idling speed by positioning the throttle flap stop, or by changing the fuel flow cross-sectional area, by electrical, electromechanical or electropneumatic means, according to engine speed the valve altering the fuel conduit cross-section being a slidable valve

Definitions

  • the invention relates to a device for regulating the idling speed of an internal combustion engine according to the preamble of claim 1.
  • Devices are used to regulate the idling speed in order to set the lowest possible speed, particularly in motor vehicles, which results in favorable consumption and emission values. If the filling of the internal combustion engine remains the same, fluctuations in the idling speed can occur in particular as a result of different loads which are caused by auxiliary units. In addition, the operating state of an internal combustion engine is close to the unstable speed range at which the idling speed is low, in which the engine can die if there is an additional load. Therefore, the air flow or the filling is not fixed at idle, but regulated according to the fluctuations in the idle speed.
  • an actuating current is applied to a solenoid, which is formed, inter alia, as a function of the actual speed, which causes the valve element connected to the solenoid to be adjusted such that the actual speed reaches a predetermined target speed largely independently of disturbance variables.
  • known devices for regulating the idling speed are designed such that the valve element is held in a closed position by the return spring, for example, when the solenoids are de-energized. Only when the solenoid is acted upon by the actuating current does the valve element move against the force of the return spring into a middle position between the fully open and closed position until there is a balance of forces between the magnetic force and the force of the return spring.
  • the valve element is usually designed as a baffle plate, which is movable against cutting an idle air passage opening.
  • the actuator can also be used to set a minimum air mass flow, which can be, for example, less than 2 kg / h.
  • a minimum air mass flow is limited by the fact that, in the previous design of the devices, each movement of the lifting magnet as an electric drive element was rigidly transmitted to the valve element or an impact plate as a sealing element. If the sealing element is moved dynamically against a sealing edge or cutting edge in such an arrangement, the sealing element bounces back from the sealing edge and thus causes an undesired opening.
  • the present invention is therefore based on the object of developing a device for regulating the idling speed of the type mentioned at the outset in such a way that it works precisely even in the region of small air mass flows to be set, in particular without rebounding.
  • a first system which is unable to vibrate consists of the movable part of the electric drive element, in particular a core, with a push rod and a return spring which is directly connected to the movable part of the drive element.
  • the second vibratory system is separated from this first vibratory system by the decoupling spring, which can transmit movements and forces from the first vibratory system to the second vibratory system.
  • the second oscillatory system essentially consists of the sealing member or the valve element, in particular a baffle plate and a counter spring, as well as connecting elements or connecting sections which connect the sealing member with the counter spring on the one hand and the decoupling spring on the other hand.
  • the counter spring is connected directly to the sealing element.
  • the two vibratory systems and the decoupling spring are dimensioned so that with periodic excitation of the first system capable of vibrating, this first system tries via the decoupling spring to press the sealing element against the sealing edge when the sealing element just wants to bounce back from the sealing edge.
  • the force acting on the sealing element which originates from the first vibratory system, is thus phase-shifted by approximately 180 ° against the force acting on the sealing element due to the bouncing process or the impact between the sealing element and the sealing edge.
  • the sealing member does not open periodically in an undesirable manner even with dynamic control in the vicinity of the sealing edge or on the sealing edge. This enables precise control of the idle air mass flow with the smallest values.
  • the decoupling spring is designed as a compression spring, which is compressed under the action of the return spring and the counter spring.
  • the return spring and the counter spring are thus used to establish the static connection via the decoupling spring.
  • the return spring and the counter spring are dimensioned as so-called working springs, while the decoupling spring is relatively hard to cause only slight path losses between the movement of the first vibratory system with the movable part of the drive element to the second vibratory system with the sealing element .
  • the masses of the first vibratory system and the second vibratory system are preferably dimensioned in relation to one another so that the on the seal organ recoil exerted by the sealing edge is not greater than the momentarily exciting force of the first vibratory system.
  • the first oscillatory system is also periodically excited in a manner known per se in order to achieve a mechanical hysteresis of the adjustment of the movable part of the first system and thus of the sealing element. to avoid if possible.
  • the core 1, the push rod 3 and the return spring 6 form a first oscillating spring / mass system.
  • This first vibratory system is connected via the decoupling spring 7 to a second vibratory system.
  • the second system capable of oscillation comprises a sealing element designed as a baffle plate 8, which is connected directly to a counter spring 9.
  • the baffle plate is slidably mounted at points 10 and 11. It is pressed in the idle state and when the coil is de-energized by the return spring 6 via the decoupling spring 7 against a cutting edge-shaped sealing edge 12 which delimits an idle air passage opening.
  • the return spring 6 and the counter spring 9 are designed as compression springs in order to compress the decoupling spring 7 in the static state.
  • the return spring 6 and the counter spring 9 are relatively soft compared to the decoupling spring 7.
  • the springs 6 and 9 can act as working springs, while the decoupling spring 7 causes only slight path losses.
  • the first vibratory system is excited by the coil 2.
  • the adjustment of the push rod 3, which forms part of this first vibratory system, is transferred via the decoupling spring 7 to the second vibratable system with the baffle plate 8 '.
  • the baffle plate abuts the sealing edge 12, it receives an imperfect elastic shock, so that it tends to undesirably expose the idle air passage opening. However, this is prevented by the particularly large force transmitted in this phase against the direction of the recoil by the first oscillating system via the decoupling spring 7.
  • the first vibratory system and the second vibratory system are so matched to one another that the baffle plate in the phase of touching the sealing edge receives a 180 ° phase-shifted impulse from the first vibratory system, which presses the baffle plate onto the sealing edge.
  • the masses of the first vibratable and the second vibratable system are to be coordinated so that the recoil on the baffle plate cannot be greater than the excitation force emanating from the first system.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)

Abstract

In einer Einrichtung zur Regelung der Leerlaufdrehzahl eines Verbrennungsmotors durch Beeinflussung der Füllung mit einem elektromechanischen Stellglied sind ein elektrisches Antriebsorgan (Kern 1, Spule 2) sowie mindestens ein kraftflußführendes Element (Schubstange 3) zwischen dem Antriebsorgan und einem Ventilelement (Prallplatte 8) vorgesehen sowie mindestens eine Rückstellfeder (6), die an dem Antriebsorgan angreift. Um ein Prellen des Dichtorgans möglichst zu vermeiden, ist zwischen dem kraftflußführenden Element (Schubstange 3) und dem Ventilelement (Prallplatte 8) eine vorgespannte Entkoppelfeder (7) angeordnet und eine Gegenfeder (9) greift direkt an dem Ventilelement (Prallplatte 8) an.In a device for regulating the idle speed of an internal combustion engine by influencing the filling with an electromechanical actuator, an electric drive element (core 1, coil 2) and at least one force-flow-guiding element (push rod 3) between the drive element and a valve element (baffle plate 8) are provided and at least a return spring (6) which engages the drive member. In order to avoid bouncing of the sealing element as far as possible, a pre-stressed decoupling spring (7) is arranged between the force flow-guiding element (push rod 3) and the valve element (baffle plate 8) and a counter spring (9) engages directly on the valve element (baffle plate 8).

Description

Die Erfindung betrifft eine Einrichtung zur Regelung der Leerlaufdrehzahl eines Verbrennungskraftstoffmotors nach dem Oberbegriff des Anspruchs 1.The invention relates to a device for regulating the idling speed of an internal combustion engine according to the preamble of claim 1.

Zur Regelung der Leerlaufdrehzahl werden Einrichtungen verwandt, um eine möglichst geringe Drehzahl insbesondere in Kraftfahrzeugen einzustellen, die günstige,Verbrauchs- und Emissionswerte zur Folge hat. Beim Gleichbleiben der Füllung des Verbrennungskraftstoffmotors können Schwankungen der Leerlaufdrehzahl insbesondere durch unterschiedliche Belastungen auftreten, die durch Hilfsaggregate verursacht sind. Hinzu kommt, daß bei kleinerer Leerlaufdrehzahl sich der Betriebszustand eines Verbrennungskraftstoffmotors nahe dem instabilen Drehzahlbereich befindet, in dem bei einer weiteren zusätzlichen Belastung der Motor absterben kann. Deswegen wird der Luftdurchfluß, bzw. die Füllung im Leerlauf nicht fest eingestellt, sondern entsprechend den Schwankungen der Leerlaufdrehzahl reguliert. Hierzu wird ein Hubmagnet mit einem Stellstrom beaufschlagt, der unter anderem in Abhängigkeit von der Ist-Drehzahl gebildet wird, die eine solche Verstellung des mit dem Hubmagneten verbundenen Ventilelements bewirkt, daß die Ist-Drehzahl eine vorgegebene Soll-Drehzahl weitgehend unabhängig von Störgrößen erreicht. Im einzelnen sind bekannte Einrichtungen zur Regelung der Leerlaufdrehzahl so ausgebildet, daß bei stromlosen Hubmagneten das Ventilelement durch die Rückstellfeder beispielsweise in einer, geschlossenen Stellung gehalten wird. Erst wenn der Hubmagnet mit dem Stellstrom beaufschlagt wird, bewegt sich das Ventilelement entgegen der Kraft der Rückstellfeder in eine zwischen der voll geöffneten und geschlossenen Stellung befindliche mittlere Stellung, bis ein Kräftegleichgewicht zwischen der Magnetkraft und der Kraft der Rückstellfeder herrscht.Devices are used to regulate the idling speed in order to set the lowest possible speed, particularly in motor vehicles, which results in favorable consumption and emission values. If the filling of the internal combustion engine remains the same, fluctuations in the idling speed can occur in particular as a result of different loads which are caused by auxiliary units. In addition, the operating state of an internal combustion engine is close to the unstable speed range at which the idling speed is low, in which the engine can die if there is an additional load. Therefore, the air flow or the filling is not fixed at idle, but regulated according to the fluctuations in the idle speed. For this purpose, an actuating current is applied to a solenoid, which is formed, inter alia, as a function of the actual speed, which causes the valve element connected to the solenoid to be adjusted such that the actual speed reaches a predetermined target speed largely independently of disturbance variables. In particular, known devices for regulating the idling speed are designed such that the valve element is held in a closed position by the return spring, for example, when the solenoids are de-energized. Only when the solenoid is acted upon by the actuating current does the valve element move against the force of the return spring into a middle position between the fully open and closed position until there is a balance of forces between the magnetic force and the force of the return spring.

Das Ventilelement ist in der Regel als Prallplatte ausgebildet, die gegen Schneiden einer Leerlaufluft-Durchlaßöffnung beweglich ist.The valve element is usually designed as a baffle plate, which is movable against cutting an idle air passage opening.

Es ist erwünscht, daß mit dem Stellglied auch ein minimaler Luftmassenstrom einstellbar ist, der beispielsweise kleiner als 2 kg/h sein kann. Jedoch wird das Minimum des Luftmassenstroms dadurch begrenzt, daß in der bisherigen Gestaltung der Einrichtungen jede Bewegung des Hubmagneten als elektrisches Antriebsorgan starr auf das Ventilelement bzw. eine Prallplatte als Dichtorgan übertragen wurde. Wenn in einer solchen Anordnung das Dichtorgan dynamisch gegen eine Dichtkante bzw. Schneiden bewegt wird, prallt das Dichtorgan von der Dichtkante zurück und bewirkt somit eine unerwünschte Öffnung.It is desirable that the actuator can also be used to set a minimum air mass flow, which can be, for example, less than 2 kg / h. However, the minimum of the air mass flow is limited by the fact that, in the previous design of the devices, each movement of the lifting magnet as an electric drive element was rigidly transmitted to the valve element or an impact plate as a sealing element. If the sealing element is moved dynamically against a sealing edge or cutting edge in such an arrangement, the sealing element bounces back from the sealing edge and thus causes an undesired opening.

Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, eine Einrichtung zur Regelung der Leerlaufdrehzahl der eingangs genannten Gattung so weiterzubilden, daß sie auch im Bereich kleiner einzustellender Luftmassenströme genau, insbesondere ohne Rückprellen arbeitet.The present invention is therefore based on the object of developing a device for regulating the idling speed of the type mentioned at the outset in such a way that it works precisely even in the region of small air mass flows to be set, in particular without rebounding.

Diese Aufgabe wird durch die Gestaltung der Einrichtung mit den in dem Anspruch 1 gekennzeichneten Merkmalen gelost.This object is achieved by the design of the device with the features characterized in claim 1.

Nach dem erfindungsgemäßen Prinzip werden anstatt des bisher vorliegenden schwingungsfähigen Systems, welches beispielsweise aus einem Kern eines Hubmagneten, einer Schubstange, die den Hubmagneten mit dem Dichtorgan, bzw. Ventilelement verbindet, sowie einer Rückstellfeder besteht, woduch dieses eine schwingungsfähige System verhältnismäßig massereich ist, zwei schwingungsfähige Systeme jeweils geringerer Masse geschaffen, und zwar so, daß das Prellverhalten des Dichtorgans bzw. des Ventilelements günstig beeinflußt wird. Im einzelnen besteht ein erstes schwingunsfähiges System aus dem beweglichen Teil des elektrischen Antriebsorgans, insbesondere eines Kerns,mit einer Schubstange sowie einer Rückstellfeder, die direkt mit dem beweglichen Teil des Antriebsorgang in Verbindung steht. "Direkt" bedeutet in diesem Zusammenhang, daß die Rückstellfeder nicht über die vorgesehene Entkoppelfeder auf den beweglichen Teil des Antriebsorgans einwirkt. Von diesem ersten schwingungsfähigen System ist das zweite schwingungsfähige System durch die Entkoppelfeder getrennt, welche Bewegungen und Kräfte von dem ersten schwingungsfähigen System auf das zweite schwingungsfähige System übertragen kann. Das zweite schwingungsfähige System besteht im wesentlichen aus dem Dichtorgari bzw. dem Ventilelement, insbesondere einer Prallplatte sowie einer Gegenfeder, sowie Verbindungselementen oder Verbindungsabschnitten, die das Dichtorgan mit der Gegenfeder einerseits und der Entkoppelfeder andererseits verbinden. Die Gegenfeder ist so direkt mit dem Dichtorgan verbunden.According to the principle according to the invention, instead of the previously vibrable system, which consists, for example, of a core of a lifting magnet, a push rod that connects the lifting magnet to the sealing element or valve element, and a return spring, which makes this a vibrating system relatively massive, two Vibration-capable systems each created a lower mass, in such a way that the bouncing behavior of the sealing member or the valve element is influenced in a favorable manner. In particular, a first system which is unable to vibrate consists of the movable part of the electric drive element, in particular a core, with a push rod and a return spring which is directly connected to the movable part of the drive element. In this context, "direct" means that the return spring does not act on the movable part of the drive element via the decoupling spring provided. The second vibratory system is separated from this first vibratory system by the decoupling spring, which can transmit movements and forces from the first vibratory system to the second vibratory system. The second oscillatory system essentially consists of the sealing member or the valve element, in particular a baffle plate and a counter spring, as well as connecting elements or connecting sections which connect the sealing member with the counter spring on the one hand and the decoupling spring on the other hand. The counter spring is connected directly to the sealing element.

Die beiden schwingungsfähigen Systeme und die Entkoppelfeder sind so dimensioniert, daß bei periodischer Anregung des ersten schwingungpfähigen Systems dieses erste System über die Entkoppelfeder versucht, das Dichtorgan verstärkt gegen die Dichtkante zu drücken, wenn das Dichtorgan gerade von der Dichtkante zurückprellen will. Die auf das Dichtorgan einwirkende Kraft, die von dem ersten schwingungsfähigen System herrührt, ist also um etwa 180° gegen die durch den Prellvorgang bzw. den Stoß zwischen dem Dichtorgan und der Dichtkante auf das Dichtorgan einwirkenden Kraft phasenverschoben.The two vibratory systems and the decoupling spring are dimensioned so that with periodic excitation of the first system capable of vibrating, this first system tries via the decoupling spring to press the sealing element against the sealing edge when the sealing element just wants to bounce back from the sealing edge. The force acting on the sealing element, which originates from the first vibratory system, is thus phase-shifted by approximately 180 ° against the force acting on the sealing element due to the bouncing process or the impact between the sealing element and the sealing edge.

Dadurch wird insgesamt erreicht, daß das Dichtorgan auch bei einer dynamischen Steuerung in der Nähe der Dichtkante bzw. auf der Dichtkante nicht in unerwünschter Weise periodisch öffnet. Es läßt sich so eine genaue Regelung des Leerlauf-Luftmassenstroms bei kleinsten Werten erzielen.It is thereby achieved that the sealing member does not open periodically in an undesirable manner even with dynamic control in the vicinity of the sealing edge or on the sealing edge. This enables precise control of the idle air mass flow with the smallest values.

In besonders zweckmäßiger Weise ist nach Anspruch 2 die Entkoppelfeder als Druckfeder ausgebildet, die unter der Wirkung der Rückstellfeder und der Gegenfeder zusammengedrückt wird. Die Rückstellfeder und die Gegenfeder werden also genutzt, um den Kraftschluß über die Entkoppelfeder im statischen Zustand herzustellen.In a particularly expedient manner, the decoupling spring is designed as a compression spring, which is compressed under the action of the return spring and the counter spring. The return spring and the counter spring are thus used to establish the static connection via the decoupling spring.

Gemäß Anspruch 3 sind die Rückstellfeder und die Gegenfeder als sogenannte Arbeitsfedern relativ weich dimensioniert, während die Entkoppelfeder verhältnismäßig hart ist, um nur geringe Wegverluste zwischen der Bewegung des ersten schwingungsfähigen Systems mit dem beweglichen Teil des Antriebsorgans zu dem zweiten schwingungsfähigen System mit dem Dichtorgan zu verursachen.According to claim 3, the return spring and the counter spring are dimensioned as so-called working springs, while the decoupling spring is relatively hard to cause only slight path losses between the movement of the first vibratory system with the movable part of the drive element to the second vibratory system with the sealing element .

Die Massen des ersten schwingungsfähigen Systems und des zweiten schwingungsfähigen Systems sind im Verhältnis zueinander bevorzugt so dimensioniert, daß der auf das Dichtorgan von der Dichtkante ausgeübte Rückstoß nicht größer als die momentan anregende Kraft des ersten schwingungsfähigen Systems ist.The masses of the first vibratory system and the second vibratory system are preferably dimensioned in relation to one another so that the on the seal organ recoil exerted by the sealing edge is not greater than the momentarily exciting force of the first vibratory system.

Das erste schwingungsfähige System wird in an sich bekannter Weise auch deswegen periodisch angeregt, um eine mechanische Hysterese der Verstellung des beweglichen Teils des ersten Systems und damit des Dichtorgan-? möglichst zu vermeiden.The first oscillatory system is also periodically excited in a manner known per se in order to achieve a mechanical hysteresis of the adjustment of the movable part of the first system and thus of the sealing element. to avoid if possible.

Die Erfindung wird im folgenden anhand einer Zeichnung mit einer Figur erläutert, in der ein bevorzugtes Ausführungsbeispiel der Einrichtung teilweise im Längsschnitt vereinfachend dargestellt ist:

  • In der Zeichnung ist mit 1 ein Kern eines angedeuteten Hubmagneten bezeichnet. Der Hubmagnet wird durch eine Spule 2 erregt. Zu dem Hubmagneten gehören den magnetischen Fluß führende ferromagnetische Teile, um infolge der Erregung eine Kraftwirkung auf den Kern 1 auszuüben. Diese den magnetischen Fluß führenden ferromagnetische Teile sind jedoch nicht dargestellt, da sie auf das dynamische Verhalten der Einrichtung keine unmittelbaren Einfluß haben. Der Kern 1 ist mittels einer Schubstange 3 an zwei Stellen 4 und 5 verschiebbar gelagert. Diese Stellen können in dem den magnetischen Fluß führenden ferromagnetischen Teil angeordnet sein. Ein Ende der Schubstange 3 führt zu einer Rückstellfeder 6. Ein anderes Ende der Schubstange 3 steht mit einer Entkoppelfeder 7 in Verbindung.
The invention is explained below with reference to a drawing with a figure, in which a preferred exemplary embodiment of the device is shown in simplified form, partly in longitudinal section:
  • In the drawing, 1 denotes a core of an indicated solenoid. The solenoid is excited by a coil 2. The lifting magnet includes the magnetic flux guiding ferromagnetic parts in order to exert a force on the core 1 as a result of the excitation. However, these ferromagnetic parts carrying the magnetic flux are not shown, since they have no direct influence on the dynamic behavior of the device. The core 1 is slidably mounted at two points 4 and 5 by means of a push rod 3. These locations can be arranged in the ferromagnetic part guiding the magnetic flux. One end of the push rod 3 leads to a return spring 6. Another end of the push rod 3 is connected to a decoupling spring 7.

Der Kern 1, die Schubstange 3 und die Rückstellfeder 6 bilden ein erstes schwingungsfähiges Feder/Masse-System.The core 1, the push rod 3 and the return spring 6 form a first oscillating spring / mass system.

Dieses erste schwingungsfähige System steht über die Entkoppelfeder 7 mit einem zweiten schwingungsfähigen System in Verbindung.This first vibratory system is connected via the decoupling spring 7 to a second vibratory system.

Das zweite schwingungsfähige System umfaßt ein als Prallplatte 8 ausgebildetes Dichtorgan, welches direkt mit einer Gegenfeder 9 in Verbindung steht. Die Prallplatte ist an Stellen 10 und 11 verschiebbar gelagert. Sie wird im Ruhezustand und bei entregter Spule durch die Rückstellfeder 6 über die Entkoppelfeder 7 gegen eine schneidenförmige Dichtkante 12 gedrückt, welche eine Leerlauf-Luftdurchlaßöffnung begrenzt.The second system capable of oscillation comprises a sealing element designed as a baffle plate 8, which is connected directly to a counter spring 9. The baffle plate is slidably mounted at points 10 and 11. It is pressed in the idle state and when the coil is de-energized by the return spring 6 via the decoupling spring 7 against a cutting edge-shaped sealing edge 12 which delimits an idle air passage opening.

Die Rückstellfeder 6 und die Gegenfeder 9 sind als Druckfedern ausgebildet, um die Entkoppelfeder 7 im statischen Zustand zusammenzudrücken. Die Rückstellfeder 6 und die Gegenfeder 9 sind gegenüber der Entkoppelfeder 7 verhältnismäßig weich. Somit können die Federn 6 und 9 als Arbeitsfedern wirken, während die Entkoppelfeder 7 nur geringe Wegverluste verursacht.The return spring 6 and the counter spring 9 are designed as compression springs in order to compress the decoupling spring 7 in the static state. The return spring 6 and the counter spring 9 are relatively soft compared to the decoupling spring 7. Thus, the springs 6 and 9 can act as working springs, while the decoupling spring 7 causes only slight path losses.

Im Betrieb der Einrichtung wird das erste schwingungsfähige System durch die Spule 2 erregt.During operation of the device, the first vibratory system is excited by the coil 2.

Die Verstellung der Schubstange 3, die einTeil dieses ersten schwingungsfähigen Systems bildet, wird über die Entkoppelfeder 7 auf das zweite schwingungsfähige System mit der Prallplatte 8`übertragen. Wenn die Prallplatte gegen die Dichtkante 12 stößt, erhält sie einen unvollkommenen elastischen Stoß zurück, so daß sie insofern dazu tendiert, die Leerlauf-Luftdurchlaßöffnung in unerwünschter Weise momentan freizugeben. Dies wird jedoch durch die über die Entkoppelfeder 7 von dem ersten schwingungsfähigen System in dieser Phase übertragene besonders große Kraft entgegen der Richtung des Rückstoßes verhindert. Hierzu sind also das erste schwingungsfähige System und das zweite schwingungsfähige System so aufeinander abgestimmt, daß die Prallplatte in der Phase der Berührung der Dichtkante einen um 180° phasengedrehten Impuls von dem ersten schwingungsfähigen System erhält, der die Prallplatte auf die Dichtkante drückt. Die Massen des ersten schwingungsfähigen und des zweiten schwingungsfähigen Systems sind dabei so aufeinander abzustimmen, daß der Rückstoß auf die Prallplatte nicht größer als die von dem ersten System ausgehende anregende Kraft sein kann.The adjustment of the push rod 3, which forms part of this first vibratory system, is transferred via the decoupling spring 7 to the second vibratable system with the baffle plate 8 '. When the baffle plate abuts the sealing edge 12, it receives an imperfect elastic shock, so that it tends to undesirably expose the idle air passage opening. However, this is prevented by the particularly large force transmitted in this phase against the direction of the recoil by the first oscillating system via the decoupling spring 7. For this purpose, the first vibratory system and the second vibratory system are so matched to one another that the baffle plate in the phase of touching the sealing edge receives a 180 ° phase-shifted impulse from the first vibratory system, which presses the baffle plate onto the sealing edge. The masses of the first vibratable and the second vibratable system are to be coordinated so that the recoil on the baffle plate cannot be greater than the excitation force emanating from the first system.

Insgesamt wird damit ein besonders großer nutzbarer Arbeitsbereich der Einrichtung erzielt, der insbesondere auch im Bereich kleiner Luftmassenströme genaue Einstellungen erlaubt.Overall, a particularly large usable working area of the device is achieved, which allows precise settings, particularly in the area of small air mass flows.

Claims (3)

1. Einrichtung zur Regelung der Leerlaufdrehzahl eines Verbrennungskraftstoffmotors durch Beeinflussung der Füllung mit einem elektromechanischen Stellglied, das ein elektrisches Antriebsorgan sowie mindestens ein kraftflußführendes Element zwischen dem Antriebsorgan und einem Ventilelement aufweist, sowie mit mindestens einer Rückstellfeder, die an dem Antriebsorgan angreift, dadurch gekennzeichnet , daß zwischen dem kraftflußführenden Element (Schubstange 3) und dem Ventilelement (Prallplatte 8) eine vorgespannte Entkoppelfeder (7) angeordnet ist und daß eine Gegenfeder (9) direkt (d.h. diesseits der Entkoppelfeder 7) mit dem Ventilelement in Verbindung steht.1. Device for regulating the idling speed of an internal combustion engine by influencing the filling with an electromechanical actuator which has an electric drive element and at least one force-flow-guiding element between the drive element and a valve element, and with at least one return spring which acts on the drive element, characterized in that that a prestressed decoupling spring (7) is arranged between the force flow-guiding element (push rod 3) and the valve element (baffle plate 8) and that a counter spring (9) is connected directly (ie on this side of the decoupling spring 7) to the valve element. 2. Einrichtung nach Anspruch 1, dadurch gekennzeichnet,
daß die Entkoppelfeder (7) als Druckfeder ausgebildet ist, die unter der Wirkung der Rückstellfeder (6) und der Gegenfeder (9) im Ruhezustand zusammengedrückt wird.2. Device according to claim 1, characterized in
that the decoupling spring (7) is designed as a compression spring which is compressed under the action of the return spring (6) and the counter spring (9) in the idle state. 3. Einrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet ,
daß das Verhältnis der Federkonstanten der Entkoppelfeder (7) zu der Rückstellfeder (6) bzw. der Gegenfeder (9) 2 : 1 bis 3 : 1 beträgt.3. Device according to claim 1 or 2, characterized in that
that the ratio of the spring constants of the decoupling spring (7) to the return spring (6) or the counter spring (9) is 2: 1 to 3: 1.
EP84103881A 1983-07-15 1984-04-07 Device for controlling the idle speed of an internal-combustion engine Expired EP0131694B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3325548A DE3325548A1 (en) 1983-07-15 1983-07-15 DEVICE FOR CONTROLLING THE IDLE SPEED OF A COMBUSTION FUEL ENGINE
DE3325548 1983-07-15

Publications (3)

Publication Number Publication Date
EP0131694A2 true EP0131694A2 (en) 1985-01-23
EP0131694A3 EP0131694A3 (en) 1985-04-10
EP0131694B1 EP0131694B1 (en) 1986-07-02

Family

ID=6204047

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84103881A Expired EP0131694B1 (en) 1983-07-15 1984-04-07 Device for controlling the idle speed of an internal-combustion engine

Country Status (3)

Country Link
US (1) US4562809A (en)
EP (1) EP0131694B1 (en)
DE (2) DE3325548A1 (en)

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EP0322850A1 (en) * 1987-12-24 1989-07-05 WEBER S.r.l. Electromagnetic air control valve for an internal combustion engine fuel supply device
US5836521A (en) * 1995-03-09 1998-11-17 Dysekompagniet I/S Valve device with impact member and solenoid for atomizing a liquid

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Publication number Priority date Publication date Assignee Title
US9394864B2 (en) 2014-06-11 2016-07-19 Ford Global Technologies, Llc Multi-frequency quarter-wave resonator for an internal combustion engine vehicle
US10302052B2 (en) 2016-11-16 2019-05-28 Ford Global Technologies, Llc Vacuum actuated multi-frequency quarter-wave resonator for an internal combustion engine

Citations (1)

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Publication number Priority date Publication date Assignee Title
FR2410738A1 (en) * 1977-12-05 1979-06-29 Bendix Corp IDLE SPEED CONTROL SYSTEM FOR AUTOMOTIVE ENGINES

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FR2410738A1 (en) * 1977-12-05 1979-06-29 Bendix Corp IDLE SPEED CONTROL SYSTEM FOR AUTOMOTIVE ENGINES

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0322850A1 (en) * 1987-12-24 1989-07-05 WEBER S.r.l. Electromagnetic air control valve for an internal combustion engine fuel supply device
US4909475A (en) * 1987-12-24 1990-03-20 Weber S.R.L. Electromagnetic air control valve for an internal combustion engine fuel supply device
US5836521A (en) * 1995-03-09 1998-11-17 Dysekompagniet I/S Valve device with impact member and solenoid for atomizing a liquid

Also Published As

Publication number Publication date
US4562809A (en) 1986-01-07
DE3460262D1 (en) 1986-08-07
EP0131694B1 (en) 1986-07-02
DE3325548A1 (en) 1985-01-24
EP0131694A3 (en) 1985-04-10

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