EP0025085B1 - Control device for internal-combustion engines - Google Patents

Control device for internal-combustion engines Download PDF

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Publication number
EP0025085B1
EP0025085B1 EP80103113A EP80103113A EP0025085B1 EP 0025085 B1 EP0025085 B1 EP 0025085B1 EP 80103113 A EP80103113 A EP 80103113A EP 80103113 A EP80103113 A EP 80103113A EP 0025085 B1 EP0025085 B1 EP 0025085B1
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EP
European Patent Office
Prior art keywords
pressure
air pressure
control
control apparatus
diaphragm
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Expired
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EP80103113A
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German (de)
French (fr)
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EP0025085A1 (en
Inventor
Manfred Dipl.-Ing. Krämer
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Robert Bosch GmbH
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Robert Bosch GmbH
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Priority to AT80103113T priority Critical patent/ATE3734T1/en
Publication of EP0025085A1 publication Critical patent/EP0025085A1/en
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    • 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 is based on a control device according to the generic preamble of patent claim 1.
  • control devices of this type work in dependence on the absolute pressure of the intake air in the intake manifold of the engine, specifically in aspirated engines in dependence on the atmospheric air pressure and in supercharged engines in dependence on the charge air pressure.
  • 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 cell in the control device according to DE-A No.
  • a control device for internal combustion engines known from FR-A No. 2102730 with a movable wall, which is controlled as a function of the intake air pressure in the intake manifold of the engine and can be displaced by a servo pressure medium, of an actuator changing the setting range of a delivery quantity adjustment element of the fuel metering device
  • compressed air is already used as the servo pressure medium.
  • This servo air pressure is reduced by a control device formed by a two-stage fluidic amplifier to a control air pressure proportional to the dynamic pressure of the intake air.
  • This control device which is only intended for naturally aspirated engines, uses the dynamic pressure in the intake manifold instead of the absolute pressure of the intake air required for accurate air mass measurement.As a result, in the event of differences in air pressure, such as occur particularly when driving at great heights, an incorrect quantity correction is controlled, which then leads to impermissibly high exhaust gas emission values leads.
  • a control device for internal combustion engines known from FR-A No. 223885 with a movable wall of an actuator and with a control device for controlling the servo pressure medium
  • air under negative pressure is used as the servo pressure medium and by means of a pneumatic pressure transducer depending on the suction pressure in the intake manifold of the engine regulated accordingly increased control air pressure.
  • the adjustment range of a delivery quantity adjustment element of the fuel metering device for an internal combustion engine operating in suction mode is corrected as a function of the negative pressure in the intake manifold. No absolute pressure signal is processed in this control device either, so that the same disadvantages as in the aforementioned control device occur.
  • 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 directly acted upon by the charge air pressure, on the other hand, 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 adjust the control characteristic curve in accordance with the changing absolute pressure of the intake air or limit the respective permissible full load setting of a delivery rate adjustment element of the fuel metering device as a full load stop.
  • control device with the combination of features specified in independent claim 1 enables the use of an actuator working against the ambient or atmospheric air pressure, and yet an exact correction of the adjustment range or the full load position of the delivery rate adjustment element of the fuel metering device, which is proportional to the absolute pressure of the intake air, can be controlled without great effort .
  • the use of compressed air as a servo pressure medium means that there are no sealing problems, 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 translated to a high pressure level to generate the necessary work capacity.
  • the known 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 practically implemented control device
  • FIGS. 3 and 4 each show a partial section through the one shown in FIG. 2 pneumatic pressure transducer, but with the function of the baffle valve modified for the third and fourth exemplary embodiments
  • FIG. 5 a pneumatic pressure transducer for the fifth exemplary embodiment with a baffle valve operating differently from FIG. 2.
  • FIG. 1 serves to explain the basic function of the control device according to the invention, which serves 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 compensator 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 11, which consists of two partial chambers 13a and 13b connected by means of a line 13c existing pressure chamber 13 a servo air line 14 is connected.
  • a servo air line 14 compressed air serving as a servo pressure medium, e.g. from an air pressure brake system, into the partial chamber 13a, from which a part of this compressed air continuously flows out via a discharge opening 17 designed as a discharge throttle.
  • the first pressure chamber 11 there is an evacuated diaphragm pressure socket 18 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 subchamber 13b of the second pressure chamber 13 and which, from a third pressure chamber 23 arranged between the two subchambers 13a and 13b, from the atmospheric air pressure p A coming into this pressure chamber 23 via an opening 24 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.
  • roller membrane 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 31 a in a known manner in the control linkage of a speed controller, not shown, or a pivotable or displaceable one Full load stop actuated to limit the position of a delivery quantity adjusting element of the fuel metering device.
  • the evacuated diaphragm pressure cell 18 acted upon by the intake air pressure PL 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 member 21 and thus the valve member 15 that regulates the control air pressure p St 17 constantly flows out of the second pressure chamber 13, 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, the control air pressure p s prevailing in the pressure chamber 13 is proportional to the absolute pressure in the first pressure chamber 11 via the Charge air line 10 controlled intake air controlled, namely by the valve member 15, the inflow cross section of the inflow opening 16 is adjusted according to the control air pressure p st to be controlled.
  • FIGS. 2 to 5 the same or equivalent components taken from FIG. 1 are given the same designation 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 practically implemented control device with a pneumatic pressure converter 12 'and a membrane 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 s 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 p A prevailing outside the control device 12'.
  • the actuating member 21 ' is fastened between these two diaphragm pressure sockets 18 and 34 and carries a baffle plate 15' of a baffle plate valve 37 which serves as a valve member.
  • This baffle plate 15 ' controls the flow cross-section on a nozzle-shaped valve and, via the servo air line 14, the one with the servo air pressure p s Compressed air supplied inlet opening 16 ', while the play formed by the difference in diameter between the sliding guide 32 and the actuator 21' serves as the outlet opening.
  • this outflow opening 17 ' has a constant throttle cross section, and the pressure change required for controlling the control air pressure p s is controlled by the change in cross section at the inflow opening 16'.
  • control of the pressure level of the control air pressure p st can 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 outlet-shaped outflow opening 38 which is arranged in the partition 33 and is opposite the nozzle-shaped inflow opening 16 '.
  • the bore of the sliding 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 when the inflow cross-section increases, the outflow cross-section decreases and vice versa.
  • the fourth exemplary embodiment shown in FIG. 4 corresponds essentially 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 "has an oblique control surface 39 which controls a discharge cross-section of the discharge opening 17 "which is variable via the stroke of the actuator 21" with the slide guide 32.
  • the inflow opening 16 'and the discharge opening 17 also work against each other with respect to the cross-sectional control, with the baffle plate 15' the inflow cross-section at the inlet opening 16 'and the oblique control surface 39 of the actuator 21 "controls the outlet cross section at the outlet opening 17".
  • the inflow opening supplied with compressed air via the servo air line 14 is designed as a throttle and is designated 16 ".
  • the control air pressure p s prevailing in the pressure chamber 13 ' only the outflow cross section of the baffle plate 15' is used the - as in Fig. 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 pretensioning force of which leads to a parallel displacement of the control air pressure range, as a result of which 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 a pressure screw 43 which is accessible from the outside and which also serves as an axial and radial bearing for the pressure cell 18.

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  • 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 Patentanspruchs 1.The invention is based on a control device according to the generic preamble of patent claim 1.

Bekannte Steuereinrichtungen dieser Art (DE-A Nrn. 2448656 und 2532830) 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 bei der Steuereinrichtung nach der DE-A Nr. 2448656 einen dem notwendigen Stellgliedweg zur Verdrehung eines Verstellexzenters entsprechenden oder im Falle der DE-A Nr. 2532830 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-A Nos. 2448656 and 2532830) work in dependence on the absolute pressure of the intake air in the intake manifold of the engine, specifically in aspirated engines in dependence on the atmospheric air pressure and in supercharged engines in dependence on the 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 cell in the control device according to DE-A No. 2448656 must generate a control path corresponding to the necessary actuator path for rotating an adjusting eccentric or, in the case of DE-A No. 2532830, a control path required to displace a space cam . For this purpose, relatively large adjustment paths, which are sometimes subject to friction, and therefore correspondingly large diaphragm box sets are necessary. In addition, the supply and sealing of the components acted upon by the hydraulic medium are relatively expensive.

Bei einer aus der FR-A Nr. 2102730 bekannten Steuereinrichtung für Brennkraftmaschinen mit einer in Abhängigkeit vom Ansaugluftdruck im Saugrohr des Motors gesteuerten und von einem Servodruckmedium verschiebbaren beweglichen Wand eines den Stellbereich eines Fördermengenverstellgliedes der Kraftstoffzumesseinrichtung verändernden Stellgliedes wird bereits Druckluft als Servodruckmedium verwendet. Dieser Servoluftdruck wird durch eine von einem zweistufigen Fluidikverstärker gebildete Steuervorrichtung auf einen dem dynamischen Druck der Ansaugluft proportionalen Steuerluftdruck reduziert. Diese nur für Saugmotoren vorgesehene Steuereinrichtung benutzt anstelle des für eine genaue Luftmassenmessung erforderlichen Absolutdrucks der Ansaugluft den dynamischen Druck im Ansaugrohr, wodurch bei Luftdruckunterschieden, wie sie vor allem bei Fahrten in grossen Höhen auftreten, eine fehlerhafte Mengenkorrektur gesteuert wird, die dann zu unzulässig hohen Abgasemissionswerten führt.In a control device for internal combustion engines known from FR-A No. 2102730 with a movable wall, which is controlled as a function of the intake air pressure in the intake manifold of the engine and can be displaced by a servo pressure medium, of an actuator changing the setting range of a delivery quantity adjustment element of the fuel metering device, compressed air is already used as the servo pressure medium. This servo air pressure is reduced by a control device formed by a two-stage fluidic amplifier to a control air pressure proportional to the dynamic pressure of the intake air. This control device, which is only intended for naturally aspirated engines, uses the dynamic pressure in the intake manifold instead of the absolute pressure of the intake air required for accurate air mass measurement.As a result, in the event of differences in air pressure, such as occur particularly when driving at great heights, an incorrect quantity correction is controlled, which then leads to impermissibly high exhaust gas emission values leads.

Bei einer aus der FR-A Nr. 223885 bekannten Steuereinrichtung für Brennkraftmaschinen mit einer beweglichen Wand eines Stellgliedes und mit einer Steuervorrichtung zur Steuerung des Servodruckmediums wird Luft unter Unterdruck als Servodruckmedium verwendet und mittels eines pneumatischen Druckwandlers in Abhängigkeit vom Ausaugdruck im Saugrohr des Motors auf einen entsprechend erhöhten Steuerluftdruck reguliert. Durch diese Einrichtung wird der Stellbereich eines Fördermengenverstellgliedes der Kraftstoffzumesseinrichtung für eine im Saugbetrieb arbeitende Brennkraftmaschine in Abhängigkeit vom Unterdruck im Saugrohr korrigiert. Auch bei dieser Steuereinrichtung wird kein Absolutdrucksignal verarbeitet, so dass die gleichen Nachteile wie bei der zuvorgenannten Steuereinrichtung auftreten.In a control device for internal combustion engines known from FR-A No. 223885 with a movable wall of an actuator and with a control device for controlling the servo pressure medium, air under negative pressure is used as the servo pressure medium and by means of a pneumatic pressure transducer depending on the suction pressure in the intake manifold of the engine regulated accordingly increased control air pressure. By means of this device, the adjustment range of a delivery quantity adjustment element of the fuel metering device for an internal combustion engine operating in suction mode is corrected as a function of the negative pressure in the intake manifold. No absolute pressure signal is processed in this control device either, so that the same disadvantages as in the aforementioned control device occur.

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 directly acted upon by the charge air pressure, on the other hand, 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 Vollaststel lung eines Fördermengenverstellgliedes der Kraftstoffzumesseinrichtung.The actuators of the known control devices either intervene in the control linkage in order to adjust the control characteristic curve in accordance with the changing absolute pressure of the intake air or limit the respective permissible full load setting of a delivery rate adjustment element of the fuel metering device as a full load stop.

Durch die erfindungsgemässe Steuereinrichtung mit der im unabhängigen Patentanspruch 1 angegebenen Merkmalskombination ist die Verwendung eines gegen den Umgebungs- bzw. Atmosphärenluftdruck arbeitenden Stellgliedes möglich und trotzdem ohne grossen Aufwand eine genaue, dem Absolutdruck der Ansaugluft proportionale Korrektur des Stellbereichs oder der Volllaststellung des Fördermengenverstellglieds der Kraftstoffzumesseinrichtung steuerbar. Des weiteren treten durch die Verwendung von Druckluft als Servodruckmedium keine Abdichtprobleme auf, 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 combination of features specified in independent claim 1 enables the use of an actuator working against the ambient or atmospheric air pressure, and yet an exact correction of the adjustment range or the full load position of the delivery rate adjustment element of the fuel metering device, which is proportional to the absolute pressure of the intake air, can be controlled without great effort . Furthermore, the use of compressed air as a servo pressure medium means that there are no sealing problems, 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 translated to a high pressure level to generate the necessary work capacity. 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 abhängigen Patentansprüchen aufgeführten Merkmale sind vorteilhafte Verbesserungen und weitere Ausgestaltungen der im Patentanspruch 1 angegebenen Steuereinrichtung möglich. So ergibt sich durch die Verwendung zweier Membrandruckdosen gemäss den Merkmalen des Patentanspruchs 2 ein sehr einfacher Aufbau des pneumatischen Druckwandlers, und die zu wählende Druckübersetzung kann ohne Änderung anderer Bauteile durch Auswahl der 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 dependent claims allow advantageous improvements and further refinements of the control device specified in claim 1. 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 without Changes in other components can be determined by selecting the size of the diaphragm pressure can, which can either increase the working capacity while the actuator remains the same or reduce the actuator while maintaining the same working capacity.

Durch die Verwendung des im Patentanspruch 3 angegebenen Prallplattenventils und auch durch die Merkmale einer der Patentansprüche 4 bis 8 ist bei sehr kleinen Betätigungswegen des Ventilgliedes eine sehr exakte Steuerung des Steuerluftdruckes erreichbar, und durch die Merkmale eines der Patentansprüche 6 oder 7 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. Wegen des starken Druckabfalls und der geringen Menge der in die erste Druckkammer überströmenden Luft sowie des extrem grossen Volumens aller an diese erste Druckkammer angeschlossenen Räume, wie Ladeluftleitung und Ansaugrohr des Motors, tritt keine messbare und somit keine störende Beeinflussung des in der ersten Druckkammer herrschenden Ladeluftdruckes auf. Durch die Merkmale der Patentansprüche 9 und 10 ist auf einfache Weise eine Verschiebung des wirksamen Steuerluftdruckbereichs auf einen erwünschten Druckbereich möglich, und im Patentanspruch 11 ist die Verwendung eines bekannten Membranstellgliedes festgelegt.Through the use of the baffle valve specified in claim 3 and also through the features of one of claims 4 to 8, very precise control of the control air pressure can be achieved with very small actuation paths of the valve member, and through the features of one of claims 6 or 7, the control passes the amount of air flowing out of the control air pressure into the first pressure chamber connected to the intake pipe, thereby avoiding blowing off the control air into the engine compartment, or an additional outflow line becomes superfluous. Because of the strong pressure drop and the small amount of air flowing into the first pressure chamber, as well as the extremely large volume of all rooms connected to this first pressure chamber, such as the charge air line and intake pipe of the engine, there is no measurable and therefore no disturbing influence on the charge air pressure in the first pressure chamber on. Due to the features of claims 9 and 10, a displacement of the effective control air pressure range to a desired pressure range is possible in a simple manner, and the use of a known diaphragm actuator is defined in claim 11.

Fünf Ausführungsbeispiele werden nachstehend anhand der Zeichnung beschrieben. Es zeigen in vereinfachter Darstellung: Fig. 1 ein erstes, der Erläuterung der Grundfunktion dienendes Ausführungsbeispiel, Fig. 2 ein zweites, die wesentlichen Merkmale einer praktisch ausgeführten Steuereinrichtung enthaltendes Beispiel, Fig. 3 und 4 je einen Teilschnitt durch den in Fig. 2 dargestellten pneumatischen Druckwandler, jedoch mit für das dritte und vierte Ausführungsbeispiel veränderter Funktion des Prallplattenventils, und Fig. 5 einen pneumatischen Druckwandler für das fünfte Ausführungsbeispiel mit einem abweichend von Fig. 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 practically implemented control device, FIGS. 3 and 4 each show a partial section through the one shown in FIG. 2 pneumatic pressure transducer, but with the function of the baffle valve modified for the third and fourth exemplary embodiments, and FIG. 5 a pneumatic pressure transducer for the fifth exemplary embodiment with a baffle valve operating differently from FIG. 2.

Das in Fig. 1 dargestellte Ausführungsbeispiel dient der Erläuterung der Grundfunktion der erfindungsgemässen Steuereinrichtung, die als ladedruckabhängige Korrektureinrichtung für aufgeladene Fahrzeugdieselmotoren 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 mittels einer Leitung 13c 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, z.B. 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 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 compensator 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 11, which consists of two partial chambers 13a and 13b connected by means of a line 13c existing pressure chamber 13 a servo air line 14 is connected. Via the servo air line 14, compressed air serving as a servo pressure medium, e.g. from an air pressure brake system, into the partial chamber 13a, from which a part of this compressed air continuously flows out via a discharge opening 17 designed as a discharge throttle.

Inderersten Druckkammer11 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 31 a 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 there is an evacuated diaphragm pressure socket 18 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 subchamber 13b of the second pressure chamber 13 and which, from a third pressure chamber 23 arranged between the two subchambers 13a and 13b, from the atmospheric air pressure p A coming into this pressure chamber 23 via an opening 24 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 roller membrane 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 31 a in a known manner in the control linkage of a speed controller, not shown, or a pivotable or displaceable one Full load stop actuated to limit the position of a delivery quantity adjusting element 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 damit des Ventilgliedes 15. Wenn die Druckluft über die fest eingestellte Abströmdrossel 17 ständig aus der zweiten Druckkammer 13 abfliesst, wird bei einem Gleichgewichtszustand zwischen den von der Membrandruckdose 18 und der Steuermembran 22 auf das Betätigungsglied 21 ausgeübten Betätigungskräften der in der Druckkammer 13 herrschende Steuerluftdruck ps, 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 cell 18 acted upon by the intake air pressure PL 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 member 21 and thus the valve member 15 that regulates the control air pressure p St 17 constantly flows out of the second pressure chamber 13, 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, the control air pressure p s prevailing in the pressure chamber 13 is proportional to the absolute pressure in the first pressure chamber 11 via the Charge air line 10 controlled intake air controlled, namely by the valve member 15, the inflow cross section of the inflow opening 16 is adjusted according to the control air pressure p st to be controlled. 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 is always an overpressure above the lowest atmospheric pressure, a commercially available membrane actuator 28 working against atmospheric pressure can be used as the actuator, as shown.

In den in den Fig. 2 bis 5 dargestellten Ausführungsbeispielen sind die aus Fig. 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 taken from FIG. 1 are given the same designation and the parts which differ in their design are provided with an index line.

Das in Fig. 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 ps, 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 Fig. 2 dargestellten Beispiel einen konstanten Drosselquerschnitt auf, und die zur Steuerung des Steuerluftdrucks ps, erforderliche Druckänderung wird durch die Querschnittsänderung an der Zuflussöffnung 16' gesteuert.The second exemplary embodiment shown in FIG. 2 shows the essential features of a practically implemented control device with a pneumatic pressure converter 12 'and a membrane 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 s 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 p A prevailing outside the control device 12'. The actuating member 21 'is fastened between these two diaphragm pressure sockets 18 and 34 and carries a baffle plate 15' of a baffle plate valve 37 which serves as a valve member. This baffle plate 15 'controls the flow cross-section on a nozzle-shaped valve and, via the servo air line 14, the one with the servo air pressure p s Compressed air supplied inlet opening 16 ', while the play formed by the difference in diameter between the sliding guide 32 and the actuator 21' serves as the outlet opening. In the example shown in FIG. 2, this outflow opening 17 'has a constant throttle cross section, and the pressure change required for controlling the control air pressure p s is controlled by the change in cross section at the inflow opening 16'.

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 Fig. 3 bis 5 dargestellt und nachfolgend beschrieben ist.However, the control of the pressure level of the control air pressure p st can 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 Fig. 3 steuert die Prallplatte 15' sowohl den Durchflussquerschnitt an derZuflussöffnung 16' als auch den Abflussquerschnitt einer in der Trennwand 33 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 outlet-shaped outflow opening 38 which is arranged in the partition 33 and is opposite the nozzle-shaped inflow opening 16 '. The bore of the sliding 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 when the inflow cross-section increases, the outflow cross-section decreases and vice versa.

Das in Fig. 4 dargestellte vierte Ausführungsbeispiel entspricht im wesentlichen dem in Fig. 2 dargestellten zweiten Ausführungsbeispiel, in seiner Funktion ähnelt es jedoch mehr dem in Fig. 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 Betätigungsgliedes 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 corresponds essentially 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 "has an oblique control surface 39 which controls a discharge cross-section of the discharge opening 17 "which is variable via the stroke of the actuator 21" with the slide guide 32. Thus, in this exemplary embodiment the inflow opening 16 'and the discharge opening 17 "also work against each other with respect to the cross-sectional control, with the baffle plate 15' the inflow cross-section at the inlet opening 16 'and the oblique control surface 39 of the actuator 21 "controls the outlet cross section at the outlet opening 17".

Beim fünften, in Fig. 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 ps, wird von der Prallplatte 15' nur der Abflussquerschnitt der - wie in Fig. 3 - düsenförmig ausgebildeten Abflussöffnung 38 gesteuert, und das Betätigungsglied 21' ist reibungsarm mit engem Spiel in der Gleitführung 32 geführt.In the fifth exemplary embodiment shown in FIG. 5, the inflow opening supplied with compressed air via the servo air line 14 is designed as a throttle and is designated 16 ". To control the control air pressure p s prevailing in the pressure chamber 13 ', only the outflow cross section of the baffle plate 15' is used the - as in Fig. 3 - nozzle-shaped drain opening 38, and the actuator 21 'is low friction with tight play in the slide guide 32.

In den Fig. 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 angepasstwerden kann. Wie in Fig. 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.2 to 5, the valve member 15 'is loaded in its closing direction by a valve spring 41, the pretensioning force of which leads to a parallel displacement of the control air pressure range, as a result of which the control air pressure p st can be adapted to the working pressure of the actuator. As shown in Fig. 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 Fig. 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 embodiment shown in FIG. 2, this setting means is formed by a pressure screw 43 which is accessible from the outside and 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 choice of the diameter differences between the pressure cells 18 and 34, for. B. with an area ratio of 2: 1, is in the embodiments shown in FIGS. 2 to 5, a pressure ratio between the two, prevailing in the pressure chambers 11 and 13 'pressures of p L : p St = 1: 2 and thus a corresponding Increase in work capacity achieved; 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 the safe working of the actuator 28 'required control air pressure p st is implemented.

Claims (11)

1. Control apparatus for combustion engines comprising a wall (26) of an adjustment member (28, 28') varying the adjustment range or the full load position of a delivery rate adjusting member of the fuel metering device, the wall being displaceably movable by a servo pressure medium and being controlled in accordance with the absolute pressure of the intake air in the inlet manifold of the engine and comprising a control device (12, 12') determining the position of a valve member (15, 15') for controlling the servo pressure medium by means of an evacuated aneroid capsule (18) influenced by the intake air pressure (PL), and the evacuated aneroid capsule of which is connected to an actuating member (21, 21') for the valve member (15, 15'), characterised by the following features:
(a) compressed air is used as a servo pressure medium,
(b) the control device consists of a pneumatic pressure converter (12,12') reducing the servo air pressure (ps) to a control air pressure (pst) proportional to the intake air pressure (PL),
(c) apart from a first pressure chamber (11) including the evacuated aneroid capsule (18) and influenced by the intake air pressure (PL), the pneumatic pressure converter (12, 12') has a second pressure chamber (13, 13') influenced by the control air pressure (pst) and which is provided with a control diaphragm (22) influenced by the control air pressure (pSt), likewise connected to the actuating member (21, 21') and acting against the atmospheric air pressure (PA) as well as an inlet opening (16, 16', 16") serving for the supply of compressed air and an outlet opening (17, 17', 17", 38),
(d) the through flow cross-section of at least one of the said openings (16, 16', 17", 38) is variable by the valve member (15, 15') for establishing the control air pressure (pSt),
(e) the second pressure chamber (13, 13') is connected to a working space (27) of the adjustment member (28, 28') acting against the atmospheric air pressure (PA) and bounded by the movable wall (26),
(f) the evacuated aneroid capsule (18) actu- able by the intake air pressure (pd acts against the control diaphragm (22, 22') influenced by the control air pressure (pSt) and both determine the position of the actuating member (21, 21') and of the valve member (15, 15') regulating the control air pressure (p st).
2. Control apparatus according to claim 1, characterised in that the control diaphragm is formed by the wall (22') of a second aneroid capsule (34), the interior (35) of which is influenced by the atmospheric air pressure (PA) through an opening (36) and which capsule (34) is exposed within the interior of the second pressure chamber (13') to the compressed air prevailing under the control air pressure (pSt) (fig. 2).
3. Control apparatus according to claim 2, characterised in that the actuating member (21') is fixed between the two aneroid capsules (18, 34) and carries a deflection plate (15') of a deflection plate valve (37) serving as a valve member.
4. Control apparatus according to claim 2 or 3, characterised in that the inlet opening (16, 16') has a variable inlet cross-section controlled by the valve member (15,37) and the outlet opening (17, 17', 17", 38) is formed as a discharge throttle (fig. 1 to 4).
5. Control apparatus according to one of claims 2 to 4, characterised in that both pressure chambers (11 and 13') are adjacent one another and are separated by a partition wall (33) including a sliding guide (32) for the actuating member (21') (fig. 2 to 5).
6. Control apparatus according to claim 5, characterised in that a clearance between the sliding guide (32) and the actuating member (21') forms the outlet opening (17') (fig. 2 to 4).
7. Control apparatus according to claim 6, characterised in that the actuating member (21 ") is provided with a control surface (39) which, together with the sliding guide (32), controls an outlet cross-section of the outlet opening (17") variable by the stroke of the actuating member (21") (fig. 4).
8. Control apparatus according to one of claims 2 to 5, characterised in that the through flow cross-section of the inlet opening and of the outlet opening (16' and 17", 38) are controllable selectively by the valve member (15') in such a manner that when the inlet cross-section increases the outlet cross-section reduces and vice versa (fig. 3 and 4).
9. Control apparatus according to claims 1 to 8, characterised in that a valve spring (41 ) is provided biasing the valve member (15') in one of its two actuating directions and the pretension force of which is variable by adjustment means (42) for varying the effective control air pressure range (fig. 2 to 5).
10. Control apparatus according to claim 2 or 3, characterised in that the installation position of at least one of the two aneroid capsules (18, 34) is adjustable by adjustment means (43) accessible from the outside for varying the effective control air pressure range (fig. 2).
11. Control apparatus according to one of the preceding claims, which serves as a correction device for charged vehicle Diesel engines dependent on charging-air pressure, characterised in that a diaphragm adjustment member (28, 28') known per se is usable as an adjustment member and which has an adjusting diaphragm (26) in the form of a movable wall influenced by the control air pressure (pSt), acting against the atmospheric air pressure (PA) and acting against a return spring (29) (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)

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

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JP (1) JPS5644427A (en)
AT (1) ATE3734T1 (en)
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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

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DE2540986A1 (en) * 1975-09-13 1977-03-17 Daimler Benz Ag ARRANGEMENT FOR REGULATING THE INJECTION QUANTITY OF AN INJECTION COMBUSTION ENGINE
FR2361546A2 (en) * 1976-08-09 1978-03-10 Roto Diesel Sa FUEL INJECTION PUMPS FOR INTERNAL COMBUSTION ENGINES
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Also Published As

Publication number Publication date
US4359986A (en) 1982-11-23
ATE3734T1 (en) 1983-06-15
DE2936162A1 (en) 1981-03-19
JPS646329B2 (en) 1989-02-02
JPS5644427A (en) 1981-04-23
DE3063669D1 (en) 1983-07-14
EP0025085A1 (en) 1981-03-18

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