[go: up one dir, main page]

EP0025085A1 - Control device for internal-combustion engines - Google Patents

Control device for internal-combustion engines Download PDF

Info

Publication number
EP0025085A1
EP0025085A1 EP80103113A EP80103113A EP0025085A1 EP 0025085 A1 EP0025085 A1 EP 0025085A1 EP 80103113 A EP80103113 A EP 80103113A EP 80103113 A EP80103113 A EP 80103113A EP 0025085 A1 EP0025085 A1 EP 0025085A1
Authority
EP
European Patent Office
Prior art keywords
pressure
air pressure
control
control device
actuator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP80103113A
Other languages
German (de)
French (fr)
Other versions
EP0025085B1 (en
Inventor
Manfred Dipl.-Ing. Krämer
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to AT80103113T priority Critical patent/ATE3734T1/en
Publication of EP0025085A1 publication Critical patent/EP0025085A1/en
Application granted granted Critical
Publication of EP0025085B1 publication Critical patent/EP0025085B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/06—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by means dependent on pressure of engine working fluid
    • F02D1/065—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by means dependent on pressure of engine working fluid of intake of air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • F02D1/12—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic
    • F02D1/14—Transmission of control impulse to pump control, e.g. with power drive or power assistance non-mechanical, e.g. hydraulic pneumatic
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a control device according to the generic preamble of the main claim.
  • Known control devices of this type (DE-OS 24 48 656 and 25 32 830) work as a function of the absolute pressure of the intake air in the intake manifold of the engine, specifically for naturally aspirated engines as a function of atmospheric air pressure and for supercharged engines as a function of charge air pressure. Because of the low working capacity of the membrane pressure sockets processing the absolute pressure of the intake air, a control device is connected upstream of the actuator of this device, which actuator is provided with a movable wall, in which the position of a valve member for controlling a servo pressure medium is determined by an evacuated membrane pressure socket acted upon by the intake air pressure.
  • the control device works here as a hydraulic follower piston unit, and the diaphragm pressure must generate the necessary actuator path for rotating an adjustment eccentric or, in the case of DE-OS 25 32 830, a control path required for displacing a space cam.
  • relatively large adjustment paths which are sometimes subject to friction, and therefore correspondingly large sets of diaphragm boxes are necessary.
  • the supply and sealing of the components acted upon by the hydraulic medium are relatively expensive.
  • Control devices operating without servo medium with actuators directly loaded by the diaphragm pressure sockets also have a working capacity which is far too small and the necessary actuating paths are difficult to achieve.
  • Control devices are also known whose diaphragm actuators which are directly acted upon by the charge air pressure, on the other hand, probably have a greater working capacity, but they only work with the differential pressure between the charge air pressure and the atmospheric pressure and cannot emit an absolute pressure signal, as is the case to avoid inadmissible smoke formation, especially during operation of the engine in areas with extreme differences in altitude.
  • the actuators of the known control devices either intervene in the control linkage in order to adapt the control characteristic curve in accordance with the changing absolute pressure of the intake air or limit the full load position of a delivery rate adjustment element of the fuel metering device as a full load stop.
  • control device with the characterizing features of the main claim has the advantage that there are no sealing problems due to the use of compressed air as a servo pressure medium, and depending on the design of the pneumatic pressure transducer, the control air pressure, which is proportional to the absolute pressure of the intake air, can be high enough to generate the necessary work capacity Pressure level can be translated.
  • control air pressure which is proportional to the absolute pressure of the intake air
  • membrane actuators which are otherwise directly actuated by the charge air pressure, can be used as actuators.
  • FIG. 1 shows a first exemplary embodiment serving to explain the basic function
  • FIG. 2 shows a second example containing the essential features of a practical control device
  • FIGS. 3 and 4 each show a partial section through the pneumatic pressure transducer shown in FIG. 2, however with altered for the third and fourth embodiments function of the flapper valve
  • Figure 5 is a pneumatic s ch en pressure transducer for the fifth embodiment with a deviating from Figure 2 working flapper valve.
  • FIG. 1 serves to explain the basic function of the control device according to the invention, which serves in particular as a boost pressure-dependent correction device for supercharged vehicle diesel engines.
  • a first pressure chamber 11 of a pneumatic pressure transducer 12 operating in the manner of a pneumatic pressure balance and serving as a control device is connected to a charge air line 10 connected to the intake manifold of an engine (not shown), to the second pressure chamber 13 consisting of two interconnected subchambers 13a and 13b a servo air line 14 is connected.
  • Compressed air serving as servo pressure medium preferably from an air pressure brake system, is fed into the partial chamber 13a via a servo air line 14 by means of an inflow opening 16 controlled by a valve member 15, from which part of this compressed air continuously flows out via a discharge opening 17 designed as an outflow throttle.
  • an evacuated membrane pressure cell 18 is arranged, which is acted upon by the charge air pressure PL supplied via the charge air line 10 on the one hand to a housing 19 of the pressure transducer 12 and on the other hand to an actuator 21 provided with the valve member 15.
  • the actuating member 21 is also connected to a control membrane 22 which delimits a partial chamber 13b of the second pressure chamber 13 and which extends from a third pressure chamber 23 arranged between the two partial chambers 13a and 13b the atmospheric air pressure p A entering this pressure chamber 23 is acted upon.
  • the second pressure chamber 13 is connected from the partial chamber 13b via a line 25 to a working space 27 of an actuator 28 delimited by a rolling membrane 26.
  • the rolling diaphragm which is acted upon as a movable wall by a control air pressure p st supplied to the working space 27, actuates an actuating rod 31 against the force of a return spring 29, which engages via a pivot point 31a in a known manner in the control linkage of a speed controller (not shown in more detail) or a pivotable or displaceable full-load stop actuated to limit the position of a delivery rate adjusting member of the fuel metering device.
  • the evacuated diaphragm pressure socket 18 acted upon by the intake air pressure p L counteracts the control diaphragm 22 acted upon by the control air pressure p St , and both diaphragm members 18 and 22 determine the position of the actuating element 21 and d a-regulating the control air pressure p St with the valve element 15.
  • FIGS. 2 to 5 the same or equivalent components adopted from FIG. 1 are given the same names and the parts which differ in their design are provided with an index line.
  • the second exemplary embodiment shown in FIG. 2 shows the essential features of a practical control device with a pneumatic pressure transducer 12 'and a diaphragm actuator 28'.
  • the second pressure chamber 13' consists of a single control chamber and is separated from the first pressure chamber 11 by a partition 33 containing a slide guide 32 for the actuator 21 '.
  • the control membrane acted upon by the control air pressure p St and the atmospheric air pressure p A is formed by the wall 22 'of a second membrane pressure socket 34, the interior 35 of which is acted upon via an opening 36 by the atmospheric air pressure PA prevailing outside the control device 12'.
  • the actuator 21 ' is fastened between these two pressure sockets 18 and 34 and carries a baffle plate serving as a valve member 15 'of a baffle plate valve 37.
  • This baffle plate 15' controls the flow cross-section at an inlet opening 16 'which is designed as a nozzle and is supplied via the servo air line 14 with the inflow opening 16' which is under servo air pressure p S , while the outflow opening is based on the difference in diameter serves game formed between the slide guide 32 and the actuator 21 '.
  • This drain port 17 ' has, in the example shown in Figure 2 a constant throttle cross-section, and the p for controlling the control air pressure St erferder Liche-pressure change is determined by the change in cross section at the inlet opening 16' controlled.
  • control of the pressure level of the control air pressure p St can, however, also be done by controlling both the inflow and outflow cross sections and only by controlling the outflow cross section with an inflow opening provided with a throttle, as shown in FIGS. 3 to 5 and described below.
  • the baffle plate 15 ' controls both the flow cross-section at the inflow opening 16' and the outflow cross-section of a likewise nozzle-shaped outflow opening 38 arranged in the partition wall 32 and opposite the nozzle-shaped inflow opening 16 '.
  • the bore of the slide guide 32 serves only here the guide of the actuator 21 '.
  • the flow cross-sections of the inflow opening 16 'and the outflow opening 38 are alternately controlled by the valve member 15' in such a way that in itself as the inflow cross section increases, the outflow cross section decreases and vice versa.
  • the fourth exemplary embodiment shown in FIG. 4 essentially corresponds to the second exemplary embodiment shown in FIG. 2, but its function is more similar to that of the third exemplary embodiment shown in FIG. 3, since the actuating element designated here with 21 "is provided with an oblique control surface 39, which controls a discharge cross-section of the discharge opening 17 "which can be varied via the stroke of the actuating member 21" with the slide guide 32.
  • the inflow opening 16 'and the discharge opening 17 "work against one another with respect to the cross-sectional control, the baffle plate 15' working on the inflow cross-section the inflow opening 16 'and the oblique control surface 39 of the actuator 21 "controls the outflow cross section at the outflow opening 17".
  • Embodiment shown in the fifth, in Figure 5 is referred to the above the servo-air line 14 supplied with compressed air inflow as a throttle formed with 16 "to control the in the pressure chamber 13 'p prevailing control air pressure St is of the baffle plate 15', only the outflow cross-section of the. - controlled as in Figure 3 nozzle-shaped drain opening 38, and the actuator 21 'is low friction with tight play in the slide guide 32.
  • valve member 15 is loaded in its closing direction by a valve spring 41, the Biasing force leads to a parallel shift of the control air pressure range, whereby the control air pressure P St can be adapted to the working pressure of the actuator.
  • the biasing force of this valve spring 41 can be changed by adjusting means 42 to shift the effective control air pressure range.
  • the setting means is shown as a washer 42, of course, other, in particular continuously adjustable setting members can also be used.
  • this setting means is formed by an externally accessible pressure screw 43, which also serves as an axial and radial bearing for the pressure cell 18.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Fluid-Driven Valves (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

A control apparatus for internal combustion engines is proposed, in which the adjustment range or the full-load position of a supply quantity adjustment member of the fuel metering apparatus is varied in accordance with the absolute pressure of the aspirated air in the suction tube of the engine in order to attain optimal combustion at the greatest possible torque. The control apparatus (FIG. 1) includes a pneumatic pressure converter and a pneumatic adjustment member. The pneumatic pressure converter, in a first pressure chamber, contains an evacuated diaphragm pressure box exposed to the aspirated air pressure (pL), which acts counter to a second diaphragm pressure box exposed in its interior to atmospheric air pressure (pA) and located in a second pressure chamber connected to a compressed air source. Both pressure boxes are connected via an actuation member supporting a valve member, and the valve member reduces the servo air pressure (pS) to a control air pressure (pSt) which is proportional to the absolute aspirated air pressure (pLK), this control air pressure actuating the diaphragm adjustment member functioning counter to a restoring spring and to atmospheric air pressure.

Description

Die Erfindung geht aus von einer Steuereinrichtung nach dem gattungsbildenden Oberbegriff des Hauptanspruchs.The invention relates to a control device according to the generic preamble of the main claim.

Bekannte Steuereinrichtungen dieser Art (DE-OS 24 48 656 und 25 32 830) arbeiten in Abhängigkeit vom Absolutdruck der Ansaugluft im Saugrohr des Motors, und zwar bei Saugmotoren in Abhängigkeit vom Atmosphärenluftdruck und bei aufgeladenen Motoren in Abhängigkeit vom Ladeluftdruck. Wegen des geringen Arbeitsvermögens der den Absolutdruck der Ansaugluft verarbeitenden Membrandruckdosen, ist dem mit einer beweglichen Wand versehenen Stellglied dieser Einrichtung eine Steuervorrichtung vorgeschaltet, bei der die Stellung eines Ventilglieds zur Steuerung eines Servodruckmediums von einer vom Ansaugluftdruck beaufschlagten evakuierten Membrandruckdose bestimmt wird. Die Steuervorrichtung arbeitet hier als hydraulische Folgekolbeneinheit, und die Membrandruckdose muß einen dem notwendigen Stellgliedweg zur Verdrehung eines Verstellexzenters entsprechenden oder im Falle der DE-OS 25 32 830 einen zur Verschiebung eines Raumnockens erforderlichen Steuerweg erzeugen. Dazu sind zum Teil reibungsbehaftete relativ große Stellwege und somit auch entsprechend große Membrandosensätze notwendig. Überdies bereitet die Zufuhr und Abdichtung der vom Hydraulikmedium beaufschlagten Bauteile einen relativ großen Aufwand.Known control devices of this type (DE-OS 24 48 656 and 25 32 830) work as a function of the absolute pressure of the intake air in the intake manifold of the engine, specifically for naturally aspirated engines as a function of atmospheric air pressure and for supercharged engines as a function of charge air pressure. Because of the low working capacity of the membrane pressure sockets processing the absolute pressure of the intake air, a control device is connected upstream of the actuator of this device, which actuator is provided with a movable wall, in which the position of a valve member for controlling a servo pressure medium is determined by an evacuated membrane pressure socket acted upon by the intake air pressure. The control device works here as a hydraulic follower piston unit, and the diaphragm pressure must generate the necessary actuator path for rotating an adjustment eccentric or, in the case of DE-OS 25 32 830, a control path required for displacing a space cam. For this purpose, relatively large adjustment paths, which are sometimes subject to friction, and therefore correspondingly large sets of diaphragm boxes are necessary. In addition, the supply and sealing of the components acted upon by the hydraulic medium are relatively expensive.

Andere bekannte, ohne Servomedium arbeitende Steuereinrichtungen mit direkt von den Membrandruckdosen beaufschlagten Stellgliedern haben ebenfalls ein viel zu kleines Arbeitsvermögen und die notwendigen Stellwege sind schwierig zu erreichen. Es sind auch Steuereinrichtungen bekannt, deren direkt vom Ladeluftdruck beaufschlagte Membranstellglieder dagegen wohl ein größeres Arbeitsvermögen aufweisen, sie arbeiten jedoch nur mit dem Differenzdruck zwischen dem Ladeluftdruck und dem Atmosphärendruck und können kein Absolutdrucksignal abgeben, wie dies zur Vermeidung einer unzulässigen Rauchbildung vor allem auch beim Betrieb des Motors in Gegenden mit extremen Höhenunterschieden notwendig ist.Other known control devices operating without servo medium with actuators directly loaded by the diaphragm pressure sockets also have a working capacity which is far too small and the necessary actuating paths are difficult to achieve. Control devices are also known whose diaphragm actuators which are directly acted upon by the charge air pressure, on the other hand, probably have a greater working capacity, but they only work with the differential pressure between the charge air pressure and the atmospheric pressure and cannot emit an absolute pressure signal, as is the case to avoid inadmissible smoke formation, especially during operation of the engine in areas with extreme differences in altitude.

Die Stellglieder der bekannten Steuereinrichtungen greifen entweder in das Reglergestänge ein, um die Reglerkennlinie entsprechend dem sich ändernden Absolutdruck der Ansaugluft anzupassen oder begrenzen als Vollastanschlag die jeweils zulässige Vollaststellung eines Fördermengenverstellgliedes der Kraftstoffzumeßeinrichtung.The actuators of the known control devices either intervene in the control linkage in order to adapt the control characteristic curve in accordance with the changing absolute pressure of the intake air or limit the full load position of a delivery rate adjustment element of the fuel metering device as a full load stop.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Steuereinrichtung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß durch die Verwendung von Druckluft als Servodruckmedium keine Abdichtprobleme auftreten, und je nach Auslegung des pneumatischen Druckwandlers kann der dem Absolutdruck der Ansaugluft proportionale Steuerluftdruck auf ein zur Erzeugung des notwendigen Arbeitsvermögens entsprechend hohes Druckniveau übersetzt werden. Überdies können als Stellglieder die bekannten, ansonsten direkt vom Ladeluftdruck betätigten Membranstellglieder verwendet werden.The control device according to the invention with the characterizing features of the main claim has the advantage that there are no sealing problems due to the use of compressed air as a servo pressure medium, and depending on the design of the pneumatic pressure transducer, the control air pressure, which is proportional to the absolute pressure of the intake air, can be high enough to generate the necessary work capacity Pressure level can be translated. In addition, the known membrane actuators, which are otherwise directly actuated by the charge air pressure, can be used as actuators.

Durch die in den Unteransprüchen aufgeführten Merkmale sind vorteilhafte Verbesserungen und weitere Ausgestaltungen der im Hauptanspruch angegebenen Steuereinrichtung möglich. So ist bei der Merkmalskombination des Anspruchs 2 trotz Verwendung eines gegen den Umgebungs- bzw. Atmosphärenluftdruck arbeitenden Stellgliedes ohne großen Aufwand eine genaue, dem Absolutdruck der Ansaugluft proportionale Korrektur des Stellbereichs oder der Vollaststellung des Fördermengenverstellglieds der Kraftstoffzumeßeinrichtung steuerbar. Durch die Verwendung zweier Membrandruckdosen ergibt sich gemäß dem Merkmal des Anspruchs 4 ein sehr einfacher Aufbau des pneumatischen Druckwandlers, und die zu wählende Druckübersetzung kann ohne Änderung anderer Bauteile durch Auswahl d-er Membrandruckdosengröße bestimmt werden, wodurch entweder bei gleichbleibendem Stellglied das Arbeitsvermögen vergrößert oder bei gleichem Arbeitsvermögen das Stellglied verkleinert werden kann.The features listed in the subclaims permit advantageous improvements and further refinements of the control device specified in the main claim. Thus, in the combination of features of claim 2, despite the use of an actuator that works against the ambient or atmospheric air pressure, an exact correction of the adjustment range or the full load position of the delivery rate adjustment element of the fuel metering device that is proportional to the absolute pressure of the intake air can be controlled. The use of two diaphragm pressure sockets results in a very simple construction of the pneumatic pressure transducer, and the pressure ratio to be selected can be determined without changing other components by selecting the diaphragm pressure socket size, which either increases the working capacity while the actuator remains the same or same actuator the actuator can be reduced.

Durch die Verwendung des in Anspruch 5 angegebenen Prallplattenventils und auch durch die Merkmale einer der Ansprüche 6 bis 10 ist bei sehr kleinen Betätigungswegen des Ventilgliedes eine sehr exakte Steuerung des Steuerluft- druckes erreichbar, und durch die Merkmale der Ansprüche 8 oder 9 gelangt die bei der Steuerung des Steuerluftdruckes abströmende Luftmenge in die mit dem Ansaugrohr verbundene erste Druckkammer, wodurch ein Abblasen der Steuerluft in den Motorraum vermieden wird, bzw. es wird eine zusätzliche Abströmleitung überflüssig. Durch die Merkmale der Ansprüche 11 und 12 ist auf einfache Weise eine Verschiebung des wirksamen Steuerluftdruckbereichs auf einem erwünschten Druckbereich möglich, und in Anspruch 13 ist die Verwendung eines bekannten Membranstellgliedes festgelegt.By utilizing the flapper valve in claim 5 and also by the features of one of claims 6 to 10 of the valve member is at very small actuating Because a very accurate control of the control air - pressure attainable, and passes through the features of claims 8 or 9, wherein Control of the control air pressure is the amount of air flowing into the first pressure chamber connected to the intake pipe, thereby preventing the control air from being blown into the engine compartment, or an additional outflow line becomes superfluous. The features of claims 11 and 12 make it possible to shift the effective control air pressure range to a desired pressure range in a simple manner, and claim 13 defines the use of a known diaphragm actuator.

Zeichnungdrawing

Fünf Ausführungsbeispiele werden nachstehend anhand der Zeichnung beschrieben. Es zeigen in vereinfachter Darstellung Figur 1 ein erstes, der Erläuterung der Grundfunktion dienendes Ausführungsbeispiel, Figur 2 ein zweites, die wesentlichen Merkmale einer praktisch ausgeführten Steuereinrichtung enthaltendes Beispiel, Figuren 3 und 4 je einen-Teilschnitt durch den in Figur 2 dargestellten pneumatischen Druckwandler, jedoch mit für das dritte und vierte Ausführungsbeispiel veränderter Funktion des Prallplattenventils und Figur 5 einen pneumati- schen Druckwandler für das fünfte Ausführungsbeispiel mit einem abweichend von Figur 2 arbeitenden Prallplattenventil.Five exemplary embodiments are described below with reference to the drawing. 1 shows a first exemplary embodiment serving to explain the basic function, FIG. 2 shows a second example containing the essential features of a practical control device, FIGS. 3 and 4 each show a partial section through the pneumatic pressure transducer shown in FIG. 2, however with altered for the third and fourth embodiments function of the flapper valve, and Figure 5 is a pneumatic s ch en pressure transducer for the fifth embodiment with a deviating from Figure 2 working flapper valve.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Das in Figur 1 dargestellte Ausführungsbeispiel dient der Erläuterung der Grundfunktion der erfindungsgemäßen Steuereinrichtung, die insbesondere als ladedruckabhängige Korrektureinrichtung für aufgeladene Fahrzeug-Dieselmotoren dient. An eine mit dem Saugrohr eines Motors (nicht dargestellt) verbundene Ladeluftleitung 10 ist eine erste Druckkammer 11 eines in Art einer pneumatischen Druckwaage arbeitenden und als Steuervorrichtung dienenden pneumatischen Druckwandlers 12 angeschlossen, an dessen zweite, aus zwei miteinander verbundenen Teilkammern 13a und 13b bestehende Druckkammer 13 eine Servoluftleitung 14 angeschlossen ist. Über die Servoluftleitung 14 wird mittels einer von einem Ventilglied 15 gesteuerten Zuflußöffnung 16 als Servodruckmedium dienende Druckluft, vorzugsweise aus einer Luftdruckbremsanlage, in die Teilkammer 13a zugeführt, aus der ein Teil dieser Druckluft über eine als Abströmdrossel ausgebildete Abflußöffnung 17 dauernd abströmt.The exemplary embodiment shown in FIG. 1 serves to explain the basic function of the control device according to the invention, which serves in particular as a boost pressure-dependent correction device for supercharged vehicle diesel engines. A first pressure chamber 11 of a pneumatic pressure transducer 12 operating in the manner of a pneumatic pressure balance and serving as a control device is connected to a charge air line 10 connected to the intake manifold of an engine (not shown), to the second pressure chamber 13 consisting of two interconnected subchambers 13a and 13b a servo air line 14 is connected. Compressed air serving as servo pressure medium, preferably from an air pressure brake system, is fed into the partial chamber 13a via a servo air line 14 by means of an inflow opening 16 controlled by a valve member 15, from which part of this compressed air continuously flows out via a discharge opening 17 designed as an outflow throttle.

In der ersten Druckkammer 11 ist eine evakuierte Membrandruckdose 18 angeordnet, die von dem über die Ladeluftleitung 10 zugeführten Ladeluftdruck PL beaufschlagt einerseits an einem Gehäuse 19 des Druckwandlers 12 und andererseits an einem mit dem Ventilglied 15 versehenen Betätigungsglied 21 befestigt ist. Das Betätigungsglied 21 ist außerdem mit einer die eine Teilkammer 13b der zweiten Druckkammer 13 begrenzenden Steuermembran 22 verbunden, die von einer dritten, zwischen den beiden Teilkammern 13a und 13b angeordneten Druckkammer 23 aus von dem über eine Öffnung 24 in diese Druckkammer 23 gelangenden Atmosphärenluftdruck pA beaufschlagt ist. Die zweite Druckkammer 13 ist von der Teilkammer 13b aus über eine Leitung 25 mit einem von einer Rollmembran 26 begrenzten Arbeitsraum 27 eines Stellgliedes 28 verbunden. Die als bewegliche Wand von einem dem Arbeitsraum 27 zugeführten Steuerluftdruck pst beaufschlagte Rollmembran betätigt entgegen der Kraft einer Rückstellfeder 29 eine Stellstange 31, die über einen Anlenkpunkt 31a in bekannter Weise in das Reglergestänge eines nicht näher dargestellten Drehzahlreglers eingreift oder einen verschwenk-oder verschiebbaren Vollastanschlag zur Begrenzung der Lage eines Fördermengenverstellgliedes der Kraftstoffzumeßeinrichtung betätigt.In the first pressure chamber 11, an evacuated membrane pressure cell 18 is arranged, which is acted upon by the charge air pressure PL supplied via the charge air line 10 on the one hand to a housing 19 of the pressure transducer 12 and on the other hand to an actuator 21 provided with the valve member 15. The actuating member 21 is also connected to a control membrane 22 which delimits a partial chamber 13b of the second pressure chamber 13 and which extends from a third pressure chamber 23 arranged between the two partial chambers 13a and 13b the atmospheric air pressure p A entering this pressure chamber 23 is acted upon. The second pressure chamber 13 is connected from the partial chamber 13b via a line 25 to a working space 27 of an actuator 28 delimited by a rolling membrane 26. The rolling diaphragm, which is acted upon as a movable wall by a control air pressure p st supplied to the working space 27, actuates an actuating rod 31 against the force of a return spring 29, which engages via a pivot point 31a in a known manner in the control linkage of a speed controller (not shown in more detail) or a pivotable or displaceable full-load stop actuated to limit the position of a delivery rate adjusting member of the fuel metering device.

Der vom Ansaugluftdruck pL beaufschlagten evakuierten Membrandruckdose 18 wirkt die vom Steuerluftdruck pSt beaufschlagte Steuermembran 22 entgegen, und beide Membranglieder 18 und 22 bestimmen die den Steuerluftdruck pSt regelnde Stellung des Betätigungsgliedes 21 und da-mit des Ventilgliedes 15. Wenn die Druckluft über die fest eingestellte Abströmdrossel 17 ständig aus der zweiten Druckkammer.13 abfließt, wird bei einem Gleichgewichtszustand zwischenden von der Membrandruckdose 18 und der Steuermembran 22 auf das Betätigungsglied 21 ausgeübten Betätigungskräften der in der Druckkammer 13 herrschende Steuerluftdruck pSt proportional dem Absolutdruck der in die erste Druckkammer 11 über die Ladeluftleitung 10 zugeführten Ansaugluft gesteuert, und zwar indem durch das Ventilglied 15 der Zuflußquerschnitt der Zuflußöffnung 16 entsprechend dem zu steuernden-Steuerluftdruck pSt eingestellt wird. Bei Druckerhöhung in der ersten Druckkammer 11 wird dieser Zuflußquerschnitt vergrößert und bei Druckabsenkung verkleinert. Da der Steuerluftdruck pSt direkt proportional dem Absolutdruck der Ansaugluft und immer ein über dem niedrigsten Atmosphärendruck liegender Überdruck ist, kann als Stellglied, wie gezeigt, ein handelsübliches gegen Atmosphärendruck arbeitendes Membranstellglied 28 verwendet werden.The evacuated diaphragm pressure socket 18 acted upon by the intake air pressure p L counteracts the control diaphragm 22 acted upon by the control air pressure p St , and both diaphragm members 18 and 22 determine the position of the actuating element 21 and d a-regulating the control air pressure p St with the valve element 15. When the compressed air exceeds the fixed discharge throttle 17 continuously flows out of the second pressure chamber 13, is in a state of equilibrium between the actuating forces exerted by the diaphragm pressure cell 18 and the control membrane 22 on the actuator 21 of the control air pressure p St prevailing in the pressure chamber 13 proportional to the absolute pressure of the first pressure chamber 11 controlled via the charge air line 10 intake air, namely by a through the valve member 15, the inflow cross section of the inflow opening 1 6 according to the control air pressure p St to be controlled is provided. When the pressure in the first pressure chamber 11 increases, this inflow cross section is enlarged and reduced when the pressure drops. Since the control air pressure p St is directly proportional to the absolute pressure of the intake air and always an overpressure above the lowest atmospheric pressure, a commercially available diaphragm actuator 28 working against atmospheric pressure can be used as the actuator, as shown.

In den in den Figuren 2 bis 5 dargestellten Ausführungsbeispielen sind die aus Figur 1 übernommenen gleichen oder gleichwirkenden Bauteile gleich bezeichnet und die in ihrer Bauart abweichenden Teile mit einem Indexstrich versehen.In the exemplary embodiments shown in FIGS. 2 to 5, the same or equivalent components adopted from FIG. 1 are given the same names and the parts which differ in their design are provided with an index line.

Das in Figur 2 dargestellte zweite Ausführungsbeispiel zeigt die wesentlichen Merkmale einer praktisch ausgeführten Steuereinrichtung mit einem pneumatischen Druckwandler 12' und einem Membranstellglied 28'. Bei dem pneumatischen Druckwandler 12' besteht die zweite Druckkammer 13' aus einem einzigen Steuerraum und ist von der ersten Druckkammer 11 durch eine eine Gleitführung 32 für das mit 21' bezeichnete Betätigungsglied enthaltende Trennwand 33 getrennt. Die vom Steuerluftdruck pSt und dem Atmosphärenluftdruck pA beaufschlagte Steuermembran ist in diesem Ausführungsbeispiel von der Wand 22' einer zweiten Membrandruckdose 34 gebildet, deren Innenraum 35 über eine Öffnung 36 von dem außerhalb der Steuervorrichtung 12' herrschenden Atmosphärenluftdruck PA beaufschlagt ist. Zwischen diesen beiden Membrandruckdosen 18 und 34 ist das Betätigungsglied 21' befestigt und trägt eine als Ventilglied dienende Prallplatte 15' eines Prallplattenventils 37. Diese Prallplatte 15' steuert den Durchflußquerschnitt an einer als Düse ausgebildeten und über die Servoluftleitung 14 mit der unter Servoluftdruck pS stehenden Druckluft versorgten Zuflußöffnung 16', während als Abflußöffnung das von der Durchmesserdifferenz zwischen der Gleitführung 32 und dem Betätigungsglied 21' gebildete Spiel dient. Diese Abflußöffnung 17' weist in dem in Figur 2 dargestellten Beispiel einen konstanten Drosselquerschnitt auf, und die zur Steuerung des Steuerluftdrucks pSt erferder-liche Druckänderung wird durch die Querschnittsänderung an der Zuflußöffnung 16' gesteuert.The second exemplary embodiment shown in FIG. 2 shows the essential features of a practical control device with a pneumatic pressure transducer 12 'and a diaphragm actuator 28'. In the pneumatic pressure transducer 12 ', the second pressure chamber 13' consists of a single control chamber and is separated from the first pressure chamber 11 by a partition 33 containing a slide guide 32 for the actuator 21 '. In this exemplary embodiment, the control membrane acted upon by the control air pressure p St and the atmospheric air pressure p A is formed by the wall 22 'of a second membrane pressure socket 34, the interior 35 of which is acted upon via an opening 36 by the atmospheric air pressure PA prevailing outside the control device 12'. The actuator 21 'is fastened between these two pressure sockets 18 and 34 and carries a baffle plate serving as a valve member 15 'of a baffle plate valve 37. This baffle plate 15' controls the flow cross-section at an inlet opening 16 'which is designed as a nozzle and is supplied via the servo air line 14 with the inflow opening 16' which is under servo air pressure p S , while the outflow opening is based on the difference in diameter serves game formed between the slide guide 32 and the actuator 21 '. This drain port 17 'has, in the example shown in Figure 2 a constant throttle cross-section, and the p for controlling the control air pressure St erferder Liche-pressure change is determined by the change in cross section at the inlet opening 16' controlled.

Die Steuerung der Druckhöhe des Steuerluftdrucks pSt kann jedoch auch durch Steuerung sowohl des Zufluß- als auch Abströmquerschnitts als auch nur durch Steuerung des Abflußquerschnitts bei mit einer Drossel versehener Zuflußöffnung geschehen, wie dies in den Figuren 3 bis 5 dargestellt und nachfolgend beschrieben ist.The control of the pressure level of the control air pressure p St can, however, also be done by controlling both the inflow and outflow cross sections and only by controlling the outflow cross section with an inflow opening provided with a throttle, as shown in FIGS. 3 to 5 and described below.

Beim dritten Ausführungsbeispiel nach Figur 3 steuert die Prallplatte 15' sowohl den Durchflußquerschnitt an der Zuflußöffnung 16' als auch den Abflußquerschnitt einer in der Trennwand 32 angeordneten, der düsenförmigen Zuflußöffnung 16' gegenüberliegenden, ebenfalls düsenförmigen Abflußöffnung 38. Die Bohrung der Gleitführung 32 dient hier lediglich der Führung des Betätigungsgliedes 21'. Die Durchflußquerschnitte der Zuflußöffnung 16' und der Abflußöffnung 38 werden hier wechselweise durch das Ventilglied 15' derart gesteuert, daß bei sich vergrößerndem Zuflußquerschnitt sich der Abflußquerschnitt verkleinert und umgekehrt.In the third exemplary embodiment according to FIG. 3, the baffle plate 15 'controls both the flow cross-section at the inflow opening 16' and the outflow cross-section of a likewise nozzle-shaped outflow opening 38 arranged in the partition wall 32 and opposite the nozzle-shaped inflow opening 16 '. The bore of the slide guide 32 serves only here the guide of the actuator 21 '. The flow cross-sections of the inflow opening 16 'and the outflow opening 38 are alternately controlled by the valve member 15' in such a way that in itself as the inflow cross section increases, the outflow cross section decreases and vice versa.

Das in Figur 4 dargestellte vierte Ausführungsbeispiel entspricht'im wesentlichen dem in Figur 2 dargestellten zweiten Ausführungsbeispiel, in seiner Funktion ähnelt es jedoch mehr dem in Figur 3 dargestellten dritten Ausführungsbeispiel, da das hier mit 21" bezeichnete Betätigungsglied mit einer schrägen Steuerfläche 39 versehen ist, die mit der Gleitführung 32 einen über den Hub des Betätigungliedes 21" veränderlichen Abflußquerschnitt der Abflußöffnung 17" steuert. Damit. arbeiten auch bei diesem Ausführungsbeispiel die Zuflußöffnung 16' und die Abflußöffnung 17" bezüglich der Querschnittssteuerung gegeneinander, wobei die Prallplatte 15' den Zuflußquerschnitt an der Zuflußöffnung 16' und die schräge Steuerfläche 39 des Betätigungsgliedes 21" den Abflußquerschnitt an der Abflußöffnung 17" steuert.The fourth exemplary embodiment shown in FIG. 4 essentially corresponds to the second exemplary embodiment shown in FIG. 2, but its function is more similar to that of the third exemplary embodiment shown in FIG. 3, since the actuating element designated here with 21 "is provided with an oblique control surface 39, which controls a discharge cross-section of the discharge opening 17 "which can be varied via the stroke of the actuating member 21" with the slide guide 32. Thus, in this exemplary embodiment as well, the inflow opening 16 'and the discharge opening 17 "work against one another with respect to the cross-sectional control, the baffle plate 15' working on the inflow cross-section the inflow opening 16 'and the oblique control surface 39 of the actuator 21 "controls the outflow cross section at the outflow opening 17".

Beim fünften, in Figur 5 dargestellten Ausführungsbeispiel ist die über die Servoluftleitung 14 mit Druckluft versorgte Zuflußöffnung als Drossel ausgebildet und mit 16" bezeichnet. Zur Steuerung des in der Druckkammer 13' herrschenden Steuerluftdrucks pSt wird von der Prallplatte 15' nur der Abflußquerschnitt der - wie in Figur 3 düsenförmig ausgebildeten Abflußöffnung 38 gesteuert, und das Betätigungsglied 21' ist reibungsarm mit engem Spiel in der Gleitführung 32 geführt.Embodiment shown in the fifth, in Figure 5 is referred to the above the servo-air line 14 supplied with compressed air inflow as a throttle formed with 16 "to control the in the pressure chamber 13 'p prevailing control air pressure St is of the baffle plate 15', only the outflow cross-section of the. - controlled as in Figure 3 nozzle-shaped drain opening 38, and the actuator 21 'is low friction with tight play in the slide guide 32.

In den Figuren 2 bis 5 ist das Ventilglied 15' in seiner Schließrichtung von einer Ventilfeder 41 belastet, deren Vorspannkraft zu einer Parallelverschiebung des Steuerluftdruckbereichs führt, wodurch der Steuerluftdruck PSt an den Arbeitsdruck des Stellglieds angepaßt werden kann. Wie in Figur 2 dargestellt, kann die Vorspannkraft dieser Ventilfeder 41 durch Einstellmittel 42 zur Verschiebung des wirksamen Steuerluftdruckbereichs verändert werden. Der Einfachheit halber ist das Einstellmittel als Unterlegscheibe 42 dargestellt, selbstverständlich können auch andere, vor allem stufenlos einstellbare Einstellglieder verwendet werden.In Figures 2 to 5, the valve member 15 'is loaded in its closing direction by a valve spring 41, the Biasing force leads to a parallel shift of the control air pressure range, whereby the control air pressure P St can be adapted to the working pressure of the actuator. As shown in Figure 2, the biasing force of this valve spring 41 can be changed by adjusting means 42 to shift the effective control air pressure range. For the sake of simplicity, the setting means is shown as a washer 42, of course, other, in particular continuously adjustable setting members can also be used.

Zur Verschiebung des wirksamen Steuerluftdruckbereichs und zur Einstellung der Lage des Ventilgliedes 15' kann auch die Einbaulage mindestens einer der beiden Membrandruckdosen 18 und 34 durch Einstellmittel verändert werden. In dem in Figur 2 dargestellten Ausführungsbeispiel ist dieses Einstellmittel von einer von außen zugänglichen Druckschraube 43 gebildet, die zugleich als Axial- und Radiallagerung für die Druckdose 18 dient.To shift the effective control air pressure range and to adjust the position of the valve member 15 ', the installation position of at least one of the two diaphragm pressure sockets 18 and 34 can also be changed by adjusting means. In the exemplary embodiment shown in FIG. 2, this setting means is formed by an externally accessible pressure screw 43, which also serves as an axial and radial bearing for the pressure cell 18.

Durch entsprechende Wahl der Durchmesserunterschiede zwischen den Druckdosen 18 und 34, z.B. bei einem Flächenverhältnis von 2 : 1, wird bei den in Fig..2 bis 5 dargestellten Ausführungsbeispielen eine Druckübersetzung zwischen den beiden in den Druckkammern 11 und 13' herrschenden Drücken von PL : PSt = 1 : 2 und damit eine entsprechende Erhöhung des Arbeitsvermögens erreicht; und durch die Vorspannkraft der Ventilfeder 41 und die Eigenfederung der Druckdosen 18 und 34 ist der gesamte wirksame Steuerdruckbereich so festgelegt, daß mit Sicherheit auch der vor allem beim Beschleunigen während des Starts auftretende zeitweilige Unterdruck im Saugrohr des Motors in einen für ein sicheres Arbeiten des Stellgliedes 28' erforderlichen Steuerluftdruck pSt umgesetzt wird.By appropriate selection of the diameter differences between the pressure cans 18 and 34, for example with an area ratio of 2: 1, in the exemplary embodiments shown in FIGS. 2 to 5, a pressure ratio between the two pressures of PL prevailing in the pressure chambers 11 and 13 'becomes : PSt = 1: 2 and thus a corresponding increase in working capacity; and by the biasing force of the valve spring 41 and the self-suspension of the pressure sockets 18 and 34, the entire effective control pressure range is determined so that the temporary vacuum in the intake manifold of the engine, which occurs especially during acceleration during start-up, is certain to ensure safe operation of the actuator 28 'required control air pressure p St is implemented.

Claims (13)

1. Steuereinrichtung für Brennkraftmaschinen, insbesondere ladedruckabhängige Korrektureinrichtung für aufgeladene Fahrzeug-Dieselmotoren, mit einer in Abhängigkeit vom Absolutdruck der Ansaugluft im Saugrohr des Motors gesteuerten und von einem Servodruckmedium verschiebbaren beweglichen Wand eines den Stellbereich oder die Vollaststellung eines Fördermengenverstellgliedes der Kraftstoffzumeßeinrichtung verändernden Stellgliedes, und mit einer die Stellung eines Ventilgliedes zur Steuerung des Servodruckmediums mittels einer vom Ansaugluftdruck beaufschlagten evakuierten Membrandruckdose bestimmenden Steuervorrichtung, dadurch gekennzeichnet, daß als Servodruckmedium Druckluft, vorzugsweise aus einer Luftdruckbremsanlage, verwendet wird und daß die Steuervorrichtung aus einem den Servoluftdruck (pS) auf einen dem Absolutdruck (PL) der Ansaugluft proportionalen Steuerluftdruck (PSt) reduzierenden pneumatischen Druckwandler (12, 12') besteht.1.Control device for internal combustion engines, in particular charge-pressure-dependent correction device for supercharged vehicle diesel engines, with a movable wall which is controlled as a function of the absolute pressure of the intake air in the intake manifold of the engine and which can be displaced by a servo pressure medium, and an actuator which changes the setting range or the full load position of a delivery quantity adjusting member of the fuel metering device one determining the position of a valve member for controlling the servo pressure medium by means of a control device acted upon by the evacuated diaphragm pressure can, characterized in that compressed air, preferably from an air pressure brake system, is used as the servo pressure medium and that the control device changes the servo air pressure (p S ) to an absolute pressure ( PL ) of the intake air proportional control air pressure (P St ) reducing pneumatic pressure converter (12, 12 '). 2. Steuereinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der pneumatische Druckwandler (12, 12') außer einer die evakuierte Membrandruckdose (18) enthaltenden und vom Ansaugluftdruck (pL) beaufschlagten ersten Druckkammer (11) eine vom Steuerluftdruck (pSt) beaufschlagte zweite Druckkammer (13, 13') aufweist, welche mit einer vom Steuerluftdruck (pSt) beaufschlagten und gegen den Atmosphärenluftdruck (PA) arbeitenden Steuermembran (22) sowie einer der Zufuhr der Druckluft dienenden Zuflußöffnung (16, 16', 16") und einer Abflußöffnung (17, 17', 17" 38) versehen ist, daß der Durchflußquerschnitt mindestens einer dieser beiden öffnungen (16, 16', 17", 38) zur Festlegung des Steuerluftdrucks (pSt) vom Ventilglied (15, 15') änderbar ist, und daß die zweite Druckkammer (13, 13') mit einem dem von der beweglichen Wand (26) begrenzten Arbeitsraum (27) des gegen Atmosphärenluftdruck (PA) arbeitenden Stellgliedes (28, 28') verbunden ist.2. Control device according to claim 1, characterized in that the pneumatic pressure transducer (12, 12 ') in addition to the evacuated membrane pressure cell (18) containing and acted upon by the intake air pressure (p L ) first pressure chamber (11) acted upon by the control air pressure (p St ) has a second pressure chamber (13, 13 '), which has a control membrane (22) which is acted upon by the control air pressure (p St ) and works against the atmospheric air pressure (P A ), and an inflow opening (16, 16', 16 ") which serves to supply the compressed air and a drain port (17, 17 ', 17 "38) provided is that the flow area at least one of these openings two (16, 16', 17", 38) for determining the S t euerl uftdrucks (p St) from the valve member (15 , 15 ') can be changed, and that the second pressure chamber (13, 13') is connected to a working space (27) of the actuator (28, 28 ') working against atmospheric air pressure (P A ) and delimited by the movable wall (26) . 3. Steuereinrichtung nach Anspruch 2, deren evakuierte Membrandruckdose mit einem Betätigungsglied für das Ventilglied verbunden ist, dadurch gekennzeichnet, daß die Steuermembran (22, 22') ebenfalls mit dem Betätigungsglied (21, 21') verbunden ist, daß der vom Ansaugluftdruck (pL) betätigbaren evakuierten Membrandruckdose (18) die vom Steuerluftdruck (pSt) beaufschlagte Steuermembran (22, 22') entgegenwirkt und daß beide die den Steuerluftdruck (pst) regelnde Stellung des Betätigungsgliedes (21, 21') und des Ventilgliedes (15, 15') bestimmen.3. Control device according to claim 2, the evacuated diaphragm pressure cell is connected to an actuator for the valve member, characterized in that the control membrane (22, 22 ') is also connected to the actuator (21, 21') that the intake air pressure (p L ) actuatable evacuated diaphragm pressure cell (18) counteracts the control diaphragm (22, 22 ') acted upon by the control air pressure (p St ) and that both the position of the actuating member (21, 21') and the valve member (regulating the control air pressure (p st )) 15, 15 '). 4. Steuereinrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß die Steuermembran von der Wand (22') einer zweiten Membrandruckdose (34) gebildet ist, deren Innenraum (35) über eine Öffnung (36) vom Atmosphärenluftdruck (PA) beaufschlagt ist, und die innerhalb der zweiten Druckkammer (13') von der unter Steuerluftdruck (pSt) stehenden Druckluft umflossen ist (Fig. 2).4. Control device according to claim 2 or 3, characterized in that the control membrane is formed by the wall (22 ') of a second membrane pressure can (34), the interior (35) of which is acted upon by an opening (36) from the atmospheric air pressure ( PA ), and the compressed air under control air pressure (p St ) flows around it within the second pressure chamber (13 ') (FIG. 2). 5. Steuereinrichtung nach Anspruch 4, dadurch gekennzeichnet, daß das Betätigungsglied (21') zwischen den beiden Membrandruckdosen (18, 34) befestigt ist und eine als Ventilglied dienende Prallplatte (15') eines Prallplattenventils (37) trägt.5. Control device according to claim 4, characterized in that the actuating member (21 ') between the two diaphragm pressure cans (18, 34) is fixed and a baffle plate (15') serving as a valve member carries a baffle valve (37). 6. Steuereinrichtung nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, daß die Zuflußöffnung (16, 16') einen vom Ventilglied (15, 37) gesteuerten veränderlichen Zuflußquerschnitt aufweist und die Abflußöffnung (17, 17', 17", 38) als Abströmdrossel ausgebildet ist. (Fig. 1 bis 4).6. Control device according to one of claims 2 to 5, characterized in that the inflow opening (16, 16 ') has a controlled by the valve member (15, 37) variable inflow cross section and the outflow opening (17, 17', 17 ", 38) as Outflow throttle is formed (Fig. 1 to 4). 7. Steuereinrichtung nach einem der Ansprüche 2 bis 6, dadurch gekennzeichnet, daß beide Druckkammern (11 und 13') aneinander angrenzend durch eine, eine Gleitführung (32) für das Betätigungsglied (21') enthaltende Trennwand (33) getrennt sind (Fig. 2 bis 5).7. Control device according to one of claims 2 to 6, characterized in that the two pressure chambers (11 and 13 ') adjacent to each other by a, a sliding guide (32) for the actuator (21') containing partition (33) are separated (Fig. 2 to 5). 8. Steuereinrichtung nach Anspruch 7, dadurch gekennzeichnt, daß ein Spiel zwischen Gleitführung (32) und Betätigungsglied (21') die Abflußöffnung (17') bildet (Fig. 2 und 4).8. Control device according to claim 7, characterized in that a game between the slide guide (32) and the actuator (21 ') forms the drain opening (17') (Fig. 2 and 4). 9. Steuereinrichtung nach Anspruch 8, dadurch gekennzeichnet, daß das Betätigungsglied (21") mit einer Steuerfläche (39) versehen ist, die mit der Gleitführung (32) einen über den Hub des Betätigungsgliedes (21") veränderlichen Abflußquerschnitt der Abflußöffnung (17") steuert (Fig. 4).9. Control device according to claim 8, characterized in that the actuating member (21 ") is provided with a control surface (39) which with the slide guide (32) via the stroke of the actuating member (21") variable drain cross-section of the drain opening (17 " ) controls (Fig. 4). 10. Steuereinrichtung nach einem der Ansprüche 2 bis 7, dadurch gekennzeichnet, daß die Durchflußquerschnitte der Zufluß- und der Abflußöffnung (16' und 17", 38) wechselweise durch das Ventilglied (15') derart steuerbar sind, daß bei sich vergrößerndem Zuflußquerschnitt sich der Abflußquerschnitt verkleinert und umgekehrt (Fig. 3 und 4).10. Control device according to one of claims 2 to 7, characterized in that the flow cross sections of the inflow and the outflow opening (16 'and 17 ", 38) can be controlled alternately by the valve member (15') such that with increasing inflow cross section the discharge cross-section is reduced and vice versa (Fig. 3 and 4). 11. Steuereinrichtung nach Anspruch 1 bis 10, dadurch gekennzeichnet, daß eine das Ventilglied (15') in dessen Schließrichtung belastende Ventilfeder (41) vorgesehen ist, deren Vorspannkraft durch Einstellmittel (42) zur Verschiebung des wirksamen Steuerluftdruckbereichs änderbar ist (Fig. 2).11. Control device according to claim 1 to 10, characterized in that a valve spring (41) is provided which loads the valve member (15 ') in its closing direction, the pretensioning force of which can be changed by adjusting means (42) for shifting the effective control air pressure range (Fig. 2) . 12. Steuereinrichtung nach Anspruch 4 oder 5, dadurch gekennzeichnet, daß die Einbaulage'mindestens einer der beiden Membrandruckdosen (18) zur Verschiebung des wirksamen Steuerluftdruckbereichs durch ein von außen zugängliches Einstellmittel (43) verstellbar ist (Fig. 2).12. Control device according to claim 4 or 5, characterized in that the installation position 'at least one of the two diaphragm pressure sockets (18) for displacing the effective control air pressure range is adjustable by an externally accessible adjusting means (43) (Fig. 2). 13. Steuereinrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß als Stellglied ein an sich bekanntes Membranstellglied (28, 28') verwendbar ist, das als bewegliche Wand eine entgegen dem Atmosphärenluftdruck (PA) und gegen eine Rückstellfeder (29) arbeitende Stellmembran (26) aufweist (Fig. 1 und 2).13. Control device according to one of the preceding claims, characterized in that a known membrane actuator (28, 28 ') can be used as the actuator, which acts as a movable wall against the atmospheric air pressure ( PA ) and against a return spring (29) actuating membrane ( 26) has (Fig. 1 and 2).
EP80103113A 1979-09-07 1980-06-04 Control device for internal-combustion engines Expired EP0025085B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80103113T ATE3734T1 (en) 1979-09-07 1980-06-04 CONTROL DEVICE FOR INTERNAL ENGINES.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19792936162 DE2936162A1 (en) 1979-09-07 1979-09-07 CONTROL DEVICE FOR INTERNAL COMBUSTION ENGINES, IN PARTICULAR CHARGE PRESSURE-DEPENDENT CORRECTION DEVICE FOR CHARGED VEHICLE DIESE ENGINES
DE2936162 1979-09-07

Publications (2)

Publication Number Publication Date
EP0025085A1 true EP0025085A1 (en) 1981-03-18
EP0025085B1 EP0025085B1 (en) 1983-06-08

Family

ID=6080275

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80103113A Expired EP0025085B1 (en) 1979-09-07 1980-06-04 Control device for internal-combustion engines

Country Status (5)

Country Link
US (1) US4359986A (en)
EP (1) EP0025085B1 (en)
JP (1) JPS5644427A (en)
AT (1) ATE3734T1 (en)
DE (2) DE2936162A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3215736A1 (en) * 1982-04-28 1983-11-03 Robert Bosch Gmbh, 7000 Stuttgart CONTROL DEVICE FOR INTERNAL COMBUSTION ENGINES
JPH01105733U (en) * 1988-01-08 1989-07-17
GB2389198A (en) * 2002-06-01 2003-12-03 Seneca Tech Ltd A governor for a diesel engine

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH205291A (en) * 1937-08-14 1939-06-15 Sulzer Ag Internal combustion engine.
DE1064345B (en) * 1956-07-14 1959-08-27 Kloeckner Humboldt Deutz Ag Control device for engines, especially internal combustion engines
US2999488A (en) * 1939-02-03 1961-09-12 Reggio Ferdinando Carlo Fuel control with feedback and force multiplication
FR1347465A (en) * 1963-02-11 1963-12-27 Westinghouse Bremsen Gmbh Pneumatic device and device for adjusting at will, and maintaining at a constant value, the speed of rotation of the motor shaft of driving machines and adjustable transmissions whose power on the motor shaft is variable
FR2102730A5 (en) * 1970-08-12 1972-04-07 Berliet Automobiles
DE2448656A1 (en) * 1973-10-30 1975-05-15 Sigma Diesel DEVICE FOR THE CONTROL OF THE FUEL SUPPLY FOR COMBUSTION ENGINES
DE2532830A1 (en) * 1975-07-23 1977-01-27 Kloeckner Humboldt Deutz Ag IC engine fuel injector pump regulator - has air pressure and temperature dependent three dimensional cam
FR2323885A1 (en) * 1975-09-13 1977-04-08 Daimler Benz Ag INSTALLATION FOR REGULATING THE INJECTION FLOW OF AN INTERNAL COMBUSTION ENGINE WITH INJECTION
DE2718613A1 (en) * 1977-04-27 1978-11-02 Daimler Benz Ag Fuel injection volume limiting valve for supercharged engines - has accelerator pedal with compressed air cylinder to modify valve pressure
FR2392235A1 (en) * 1977-05-28 1978-12-22 Bosch Gmbh Robert IC engine air-fuel ratio regulator - uses differential pressure valve and throttle to regulate flows according to pressure differences at constrictions
US4148289A (en) * 1977-05-31 1979-04-10 Hewitt John T Diesel engine control means

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2031527A (en) * 1935-04-23 1936-02-18 Dodson Edward Controlling means for fuel injection engines
US2374411A (en) * 1938-02-18 1945-04-24 Atlas Diesel Ab Means for controlling the fuel supply in two-stroke internal-combustion engines
US3077873A (en) * 1961-08-04 1963-02-19 Caterpillar Tractor Co Pressure actuated fuel control for supercharged engines
US3435813A (en) * 1967-10-09 1969-04-01 Caterpillar Tractor Co Engine safety controls
US4037575A (en) * 1975-08-25 1977-07-26 Caterpillar Tractor Co. Altitude compensated fuel control system
FR2361546A2 (en) * 1976-08-09 1978-03-10 Roto Diesel Sa FUEL INJECTION PUMPS FOR INTERNAL COMBUSTION ENGINES
DE2731107A1 (en) * 1977-07-09 1979-01-25 Bosch Gmbh Robert CONTROL DEVICE FOR CHARGED INJECTION COMBUSTION ENGINES

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH205291A (en) * 1937-08-14 1939-06-15 Sulzer Ag Internal combustion engine.
US2999488A (en) * 1939-02-03 1961-09-12 Reggio Ferdinando Carlo Fuel control with feedback and force multiplication
DE1064345B (en) * 1956-07-14 1959-08-27 Kloeckner Humboldt Deutz Ag Control device for engines, especially internal combustion engines
FR1347465A (en) * 1963-02-11 1963-12-27 Westinghouse Bremsen Gmbh Pneumatic device and device for adjusting at will, and maintaining at a constant value, the speed of rotation of the motor shaft of driving machines and adjustable transmissions whose power on the motor shaft is variable
FR2102730A5 (en) * 1970-08-12 1972-04-07 Berliet Automobiles
DE2448656A1 (en) * 1973-10-30 1975-05-15 Sigma Diesel DEVICE FOR THE CONTROL OF THE FUEL SUPPLY FOR COMBUSTION ENGINES
DE2532830A1 (en) * 1975-07-23 1977-01-27 Kloeckner Humboldt Deutz Ag IC engine fuel injector pump regulator - has air pressure and temperature dependent three dimensional cam
FR2323885A1 (en) * 1975-09-13 1977-04-08 Daimler Benz Ag INSTALLATION FOR REGULATING THE INJECTION FLOW OF AN INTERNAL COMBUSTION ENGINE WITH INJECTION
DE2718613A1 (en) * 1977-04-27 1978-11-02 Daimler Benz Ag Fuel injection volume limiting valve for supercharged engines - has accelerator pedal with compressed air cylinder to modify valve pressure
FR2392235A1 (en) * 1977-05-28 1978-12-22 Bosch Gmbh Robert IC engine air-fuel ratio regulator - uses differential pressure valve and throttle to regulate flows according to pressure differences at constrictions
US4148289A (en) * 1977-05-31 1979-04-10 Hewitt John T Diesel engine control means

Also Published As

Publication number Publication date
JPS5644427A (en) 1981-04-23
DE2936162A1 (en) 1981-03-19
ATE3734T1 (en) 1983-06-15
JPS646329B2 (en) 1989-02-02
EP0025085B1 (en) 1983-06-08
DE3063669D1 (en) 1983-07-14
US4359986A (en) 1982-11-23

Similar Documents

Publication Publication Date Title
DE2326083C2 (en) Device for controlling the fuel-air ratio for a supercharged internal combustion engine
DE3020131C2 (en)
DE2650247A1 (en) PROCESS AND DEVICE FOR LIMITING THE MAXIMUM FUEL FLOW RATE OF THE FUEL INJECTION PUMP OF A DIESEL ENGINE
DE2949884A1 (en) VALVE ARRANGEMENT FOR CONTROLLING THE IDLE SPEED OF OTTO ENGINES, IN PARTICULAR MOTOR VEHICLE ENGINES
DE2658052A1 (en) DEVICE FOR LOAD-DEPENDENT ACTIVATION OF A CONTROL ORGAN
DE2813486A1 (en) CONTROL DEVICE FOR HYDRAULIC PUMPS
DE2448306A1 (en) FUEL INJECTION SYSTEM
DE2054911A1 (en) Control element for a fuel injection system
DE2849508A1 (en) DEVICE FOR CONTROLLING THE EXHAUST RETURN QUANTITIES AND THE INJECTION QUANTITY OF SELF-IGNITIONING INTERNAL COMBUSTION ENGINES
DE2624420C3 (en) Control unit on carburettors for internal combustion engines
DE2941513A1 (en) ENGINE SYSTEM
DE2844350C2 (en) Fuel control device for gas turbine engines
DE2815619C2 (en) Exhaust gas recirculation device in an internal combustion engine driving a motor vehicle
DE2925236A1 (en) Variable output pump with spring loaded servo piston - which is pressure actuated and coupled to idling valve with throttling action
DE2451148C3 (en) Exhaust gas recirculation device in internal combustion engines
DE2729512A1 (en) CONTROL DEVICE FOR A HYDROSTATIC TRANSMISSION
EP0025085A1 (en) Control device for internal-combustion engines
DE2647062C2 (en) Internal combustion engine with exhaust gas recirculation
DE2029075A1 (en) System for controlling the supply of fuel to an internal combustion engine
DE2837692C2 (en) Mixture formation device
DE3428380A1 (en) DEVICE FOR CONTROLLING RECYCLED EXHAUST AMOUNTS IN INTERNAL COMBUSTION ENGINES
EP0076458A1 (en) Fuel injection pump for internal-combustion engines
DE2649099C2 (en) Carburetors for internal combustion engines
DE2625141A1 (en) VACUUM REGULATOR FOR A FUEL INJECTION SYSTEM
EP0198166B1 (en) Diaphragm-actuated pneumatic correcting device for a fuel injection pump of an internal-combustion engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT DE FR GB IT

17P Request for examination filed

Effective date: 19810404

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT DE FR GB IT

REF Corresponds to:

Ref document number: 3734

Country of ref document: AT

Date of ref document: 19830615

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3063669

Country of ref document: DE

Date of ref document: 19830714

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19840702

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19860526

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19890604

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19900228

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19980526

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19980824

Year of fee payment: 19

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990604

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990630

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19990604