EP0029019B1 - Control system for internal-combustion engines - Google Patents

Control system for internal-combustion engines Download PDF

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Publication number
EP0029019B1
EP0029019B1 EP80890122A EP80890122A EP0029019B1 EP 0029019 B1 EP0029019 B1 EP 0029019B1 EP 80890122 A EP80890122 A EP 80890122A EP 80890122 A EP80890122 A EP 80890122A EP 0029019 B1 EP0029019 B1 EP 0029019B1
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EP
European Patent Office
Prior art keywords
force
servomotor
control
support
control system
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Expired
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EP80890122A
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German (de)
French (fr)
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EP0029019A1 (en
Inventor
Max Haubenhofer
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Friedmann and Maier AG
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Friedmann and Maier AG
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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
    • F02D1/08—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
    • 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
    • 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

Definitions

  • the invention relates to a control system for internal combustion engines with fuel injection, with a mechanical centrifugal regulator for regulating the injection quantity, the spring mechanism absorbing the speed-dependent force of the centrifugal weights has an abutment, the bearing force of which controls a control device of a servo motor for an auxiliary device.
  • a control system of this type is e.g. in SU-A-273 954.
  • This known control system has the disadvantage that the additional speed-dependent control of the auxiliary device via the axially movable abutment of the spring mechanism is closely linked to the actual function of the speed controller and thus has an undesirable influence on the speed control itself.
  • the object of the present invention is to design a control system of the type mentioned so that it is possible to derive additional speed-dependent signals for controlling a separate servo motor for an auxiliary device from the centrifugal governor without the control characteristic of the centrifugal governor for adjusting the control rod of the injection pump practically influenced and thus the operational reliability of the controller would be reduced.
  • the injection timing of the injection pump should be adjusted or a complicated adjustment process should be controlled.
  • the abutment is connected to an arm of a two-arm lever fixed to the housing, the other arm of which acts on the control device which is connected to the servo motor for feedback via at least one spring, and in that the axial mobility the abutment is limited to a very small stroke by stops or by the switching contacts of the control device which act as a stop itself, or that the servomotor is electrically actuated, that the control device of the servo motor has a force transducer which is arranged between the abutment and the housing of the control system and thus forms a stop for the abutment, and that the force transducer is connected to an electronic control unit of the control device and actuates it by means of an electrical signal which is dependent on the force exerted by the abutment.
  • the free mobility of the abutment is therefore either limited to a very small stroke - which, in connection with the constant feedback of the control device by the servo motor itself, limits the intervention in the function of the speed controller - or else by the force transducer acting as a stop, which is arranged between the abutment and the housing of the control system and in a very sensitive and reliable manner, which generates an electrical signal corresponding to the speed-dependent force on the spring mechanism, impeding from the outset, so that the actual function of the speed controller by deriving the axial movement of the abutment for the Spring mechanism is practically not affected, which increases the operational safety of the entire control system.
  • the spring mechanism of the mechanical centrifugal governor can be designed as in known idle end regulators and can also contain a so-called adjustment device, so that an additional adjustment device driven by the servo motor is not necessary.
  • the servo motor can be operated hydraulically, which enables large adjustment forces and a relatively simple control, and return its control device via spring forces.
  • the electronic control unit provided with the force transducer in the embodiment can be formed, for example, by a microprocessor to which further operating parameters of the internal combustion engine, such as e.g. Boost pressure, outside temperature, position of the ignition lock, throttle or control rod etc. supplied and taken into account by this when controlling the servo motor.
  • the microprocessor allows, in a very advantageous manner, all factors influencing the operating behavior of the internal combustion engine to be taken into account according to a preselected program, with which the optimal setting of the auxiliary devices is possible for the respective operating state.
  • the electrically operated servo motors can e.g. be designed as stepper motors, which simplifies and improves an accurate and reproducible setting of the auxiliary devices.
  • the centrifugal weights 1 of the centrifugal governor 2 which are attached to the two-armed angle levers 1 'and are mounted on the carrier 2' and are driven by the shaft 3, actuate the sleeve 5 via the track ball bearing 4.
  • the spring mechanism 6 of the regulator is of the way it is used in known idle end controllers.
  • an idling spring 6 ' is provided, which is supported on the sleeve 5 on the one hand and the bottom 7' of the cartridge 7 on the other hand.
  • the cartridge 7 also contains the main ring spring 8, as well as a spring plate 9 and a matching spring 10.
  • the force generated by the centrifugal weights 1 is introduced into the cartridge 7 via the two-armed angle lever 1 ′ and the sleeve 5 and is not received by the housing 11 of the regulator, as is customary in known regulators, but rather via the shoulder 12 ′ by the two-armed lever 12 , which is mounted in the bearing 13 attached to the housing 11, received and passed on to the control slide 14, which controls a servo motor 14 '.
  • the lever 12 is limited in its freedom of movement by means of a double stop 15 'which can be adjusted by means of a screw 15, so that the free axial movement of the cartridge 7 relative to the housing 11 is limited to a small stroke and the intervention in the control behavior of the centrifugal governor 2 is therefore very slight.
  • the control slide 14 is actuated by a support 12 "from the two-armed lever 12 and is axially displaceable in the bush 16, which is provided with a pressure medium inflow 16 'and control openings 17' for the pressure medium line 17 to the cylinder 21 of the hydraulic servo motor 14 '.
  • the control slide 14 is provided with control edges 19 and 20, which cooperate with the control openings 17 'and thus enable the speed-dependent actuation of the working piston 18.
  • the working piston 18 is guided in the cylinder 21, which has a vent hole 21' at its right end in the picture.
  • the speed-dependent force generated by the centrifugal weights 1 on the sleeve 5 is transmitted to the lever 12 and from there passed on to the control slide 14 via the support 12 ".
  • the control slide 14 is loaded by springs 23, which generate a force component in the axial direction of the control slide and absorb the force transmitted to the control slide.
  • the springs 23 are suspended at one end on a bead 24 of the cup 24 'and at the other end on an inner bead 24 "of the control slide 14, the cup 24' being located opposite one another over the springs 23 centrally fastened pin 25 is freely supported in a bore 26 of the working piston 18.
  • the control slide 14 If the balance of the forces on the control slide 14 is disturbed by a change in the position of the lever caused by the centrifugal regulator 2, the control slide 14 is deflected within the path delimited by the double stop 15 ', as a result of which the control edges 19 and 20 the pressure medium line 17 and the control openings Connect 17 'either to the pressure medium inlet 16' or to the outlet 16 ". As a result, the working piston 18 moves in such a way that the springs 23 restore the balance of the forces on the control slide 14 when the control openings 17 'are covered by the control slide 14 becomes.
  • the adjustment force is derived from the working piston 18 of the servo motor 14 'via a two-armed lever 27 which engages in a groove 28 of the working piston, is pivotably mounted on a bearing 29 attached to the housing and displaces an adjusting rod 30 in its longitudinal direction.
  • the direct derivation of the regulating force from the centrifugal regulator 2 takes place in the usual way via a two-armed regulator lever 32 which engages in the annular groove 31 of the sleeve 5.
  • This is mounted on an eccentric shaft 33 and transmits the speed-dependent movements of the regulator sleeve 5 via the regulator linkage 34 to the regulating rod 35 Injection pump, not shown.
  • the operating lever 36 for controlling the desired injection pump is also arranged on the eccentric shaft 33.
  • FIG. 2 differs from that of FIG. 1 in that the spring mechanism 37 of the centrifugal controller 38 does not have its own adjustment device, but the servo motor 39 actuates a so-called plus-minus adjustment via its own cam 70. Furthermore, the servo motor 39 is electrically driven here.
  • the centrifugal weights 40 of the centrifugal governor 38 are mounted on the bracket 41 via angle levers 40 ′ and are driven by the internal combustion engine via the shaft 42.
  • the movement of the flyweights 40 is transmitted via the angle levers and the track ball bearing 43 to a sleeve 44 which has a spring plate 45 fastened by means of a pin 46 at the end opposite the ball bearing 43.
  • An idle spring 47 loads the spring plate 45 and is supported at the other end on the cartridge 48 forming an abutment, which also contains the main control spring 49 resting on the spring plate 50.
  • the cartridge 48 is in turn movably mounted in the housing 51 in the axial direction and transmits the speed-dependent force introduced by the sleeve 44 into the spring mechanism 37 to a two-armed lever 52 which is pivotably mounted in the bearing 53 arranged on the housing 51.
  • the lever 52 carries at its other end a switch cap 55 which is connected to the lever in an insulated manner and connects the electrical supply line 58 to the respective connections on the electric motor 59 via the switch contacts 56 and 57.
  • the electric motor 59 moves the spindle 61 via a gear 60, on which a nut 62 is arranged, which is secured against rotation by a pin 63 running in an axial groove 64 on the housing.
  • the two-armed lever 52 which interacts with the switching contacts 56 and 57 is moved by a spring plate 54 on the support 52 ', which is axially displaceably mounted in the housing 51' Springs 65 and 66, which come into contact with one another on the spring plate 54 depending on the adjustment path of the nut 62, are loaded.
  • the control force is derived from the servo motor 39 via a lever 68 which engages in the recess 67 of the nut 62 and which transmits the movement of the nut 62 to a shaft 69.
  • This shaft has a control cam 70 which is used to control the alignment process.
  • the speed-dependent movement of the regulator sleeve 44 of the centrifugal governor 38 in FIG. 2 is absorbed by the auxiliary sleeve 71, which has an annular groove 72, via which a regulator lever 73 is actuated. At its other end 74, the latter is supported on the control cam '70 when the injection pump (not shown) is full and actuates the control rod 76 via a rod 75 to adjust the injection quantity.
  • the auxiliary sleeve 71 is loaded by a spring 77, which is supported at the other end on the side of the spring plate 45 opposite the idle spring 47 and the auxiliary sleeve 71 at those injection quantities in which there is still no contact between the end 74 of the control lever 73 and the control cam 70 is against the shoulder 78 of the sleeve 44.
  • the arrangement of the actual centrifugal governor 79 again corresponds to that already discussed for FIG. 1.
  • the centrifugal weights 82 which are pivotably mounted on the carrier 83 via the angle levers 83 'are driven via a shaft 84 by the internal combustion engine (not shown in more detail) and actuate the sleeve 86 via a track ball bearing 85.
  • the idle spring 87 and the main regulating spring 89 are described in that Abutment forming, relative to the housing 91 axially movable cartridge 88 arranged and resilient by the sleeve 86.
  • no matching device is provided in the cartridge here; the main bearing spring 89 is supported directly on the spring plate 90.
  • the speed-dependent force introduced into the cartridge 88 is delivered to the housing part 93 of the housing 91 via an electrical force transducer 92.
  • the force transducer 92 can e.g. a suitably arranged strain gauge, a piezoelectric quartz or a similar device and at the same time also represents a stop which allows only a slight axial movement of the cartridge 88.
  • the speed-dependent electrical signal of the force transducer 92 is fed via leads 81 to a microprocessor 94 which has further inputs 80, by means of which additional parameters for controlling the servomotor 94 'can be taken into account.
  • Such parameters are, for example, the charge air pressure, the outside temperature, the temperature of the internal combustion engine or its combustion chamber wall, the position of the ignition lock or the control linkage, the position of the control rod of the injection pump, etc.
  • the microprocessor 94 assembles these parameters according to a predetermined program and controls the electrical Current for the servomotor 95. This actuates a worm wheel 98 via a shaft 96 and a worm 97, which can shift the position of the control rod 100 of the injection pump (not shown) by means of a thread 99.
  • the sleeve 86 of the centrifugal governor 79 has an annular groove 101, in which the two-armed control lever 102, which is mounted on the eccentric shaft 103, engages and which, via a control linkage 104 ', establishes the connection between the speed-dependent sleeve 86 and the worm wheel 98 and thus the control rod 100 .
  • the microprocessor 94 can of course easily have additional outputs for controlling further servomotors, which means e.g. the injection timing of the internal combustion engine can be adjusted.
  • FIG. 4 differs from that in FIG. 3 only in that the sleeve 105 of the centrifugal governor 104 is secured against rotation with respect to the housing 105 'and the worm 106 of the servomotor, not shown, on a worm wheel 107 acting as an auxiliary sleeve acts, which is rotatable on a threaded rod 108 of the sleeve 105.
  • the speed-dependent force is introduced into the spring mechanism via the spring plate 111, which is fastened to the threaded rod 108 with the pin 112.
  • the two-armed control lever 110 interacts with the annular groove 109 of the worm wheel 107, which also results in a microprocessor-controlled adjustment.

Description

Die Erfindung bezieht sich auf eine Regelanlage für Brennkraftmaschinen mit Kraftstoffeinspritzung, mit einem mechanischen Fliehkraftregler zur Regelung der Einspritzmenge, dessen die drehzahlabhängige Kraft der Fliehgewichte aufnehmendes Federwerk ein Widerlager besitzt, von dessen Auflagerkraft eine Steuereinrichtung eines Servomotors für eine Hilfseinrichtung betätigbar ist.The invention relates to a control system for internal combustion engines with fuel injection, with a mechanical centrifugal regulator for regulating the injection quantity, the spring mechanism absorbing the speed-dependent force of the centrifugal weights has an abutment, the bearing force of which controls a control device of a servo motor for an auxiliary device.

Eine Regelanlage dieser Art ist z.B. in der SU-A-273 954 beschrieben. Bei dieser bekannten Regelanlage ist der Nachteil gegeben, daß die zusätzliche drehzahlabhängige Steuerung der Hilfseinrichtung über das axial beweglich ausgebildete Widerlager des Federwerks eng mit der eigentlichen Funktion des Drehzahlreglers verknüpft ist und damit in unerwünschter Weise auf die Drehzahlregelung selbst einen Einfluß ausübt.A control system of this type is e.g. in SU-A-273 954. This known control system has the disadvantage that the additional speed-dependent control of the auxiliary device via the axially movable abutment of the spring mechanism is closely linked to the actual function of the speed controller and thus has an undesirable influence on the speed control itself.

Aufgabe der vorliegenden Erfindung ist es, eine Regelanlage der genannten Art so auszubilden, daß es mit ihr möglich ist, vom Fliehkraftregler zusätzliche drehzahlabhängige Signale für die Steuerung eines separaten Servomotors für eine Hilfseinrichtung abzuleiten, ohne daß die Regelcharakteristik des Fliehkraftreglers zur Verstellung der Regelstange der Einspritzpumpe praktisch beeinflußt und somit die Betriebssicherheit des Reglers herabgesetzt würde. Beispielsweise soll der Einspritzzeitpunkt der Einspritzpumpe verstellt oder ein komplizierter Angleichvorgang gesteuert werden.The object of the present invention is to design a control system of the type mentioned so that it is possible to derive additional speed-dependent signals for controlling a separate servo motor for an auxiliary device from the centrifugal governor without the control characteristic of the centrifugal governor for adjusting the control rod of the injection pump practically influenced and thus the operational reliability of the controller would be reduced. For example, the injection timing of the injection pump should be adjusted or a complicated adjustment process should be controlled.

Dies wird gemäß der Erfindung dadurch erreicht, daß das Widerlager mit einem Arm eines gehäusefest gelagerten, zweiarmigen Hebels in Verbindung steht, dessen anderer Arm auf die Steuereinrichtung wirkt, welche zur Rückführung über zumindest eine Feder mit dem Servomotor in Verbindung ist und daß die axiale Beweglichkeit des Widerlagers durch Anschläge oder durch die selbst als Anschlag wirkenden Schaltkontakte der Steuereinrichtung auf einen sehr kleinen Hub begrenzt ist, oder aber, daß der Servomotor elektrisch betätigt ist, daß die Steuereinrichtung des Servomotors einen Kraftaufnehmer aufweist, der zwischen Widerlager und Gehäuse der Regelanlage angeordnet ist und so einen Anschlag für das Widerlager bildet, und daß der Kraftaufnehmer mit einer elektronischen Steuereinheit der Steuereinrichtung verbunden ist und diese mittels eines elektrischen Signals, welches abhängig von der vom Widerlager ausgeübten Kraft ist, betätigt.This is achieved according to the invention in that the abutment is connected to an arm of a two-arm lever fixed to the housing, the other arm of which acts on the control device which is connected to the servo motor for feedback via at least one spring, and in that the axial mobility the abutment is limited to a very small stroke by stops or by the switching contacts of the control device which act as a stop itself, or that the servomotor is electrically actuated, that the control device of the servo motor has a force transducer which is arranged between the abutment and the housing of the control system and thus forms a stop for the abutment, and that the force transducer is connected to an electronic control unit of the control device and actuates it by means of an electrical signal which is dependent on the force exerted by the abutment.

Die freie Beweglichkeit des Widerlagers ist also entweder auf einen sehr kleinen Hub begrenzt - womit im Zusammenhang mit der ständigen Rückführung der Steuereinrichtung durch den Servomotor selbst der Eingriff in die Funktion des , Drehzahlreglers eng begrenzt ist - oder aber durch den als Anschlag wirkenden Kraftaufnehmer, der zwischen Widerlager und Gehäuse der Regelanlage angeordnet ist und auf sehr empfindliche und betriebssichere Weise ein, der drehzahlabhängigen Kraft auf das Federwerk entsprechendes, elektrisches Signal erzeugt, von vorne herein behindert, sodaß die eigentliche Funktion des Drehzahlreglers durch die Ableitung der axialen Bewegung des Widerlagers für das Federwerk praktisch nicht beeinflußt wird, was die Betriebssicherheit der gesamten Regelanlage erhöht.The free mobility of the abutment is therefore either limited to a very small stroke - which, in connection with the constant feedback of the control device by the servo motor itself, limits the intervention in the function of the speed controller - or else by the force transducer acting as a stop, which is arranged between the abutment and the housing of the control system and in a very sensitive and reliable manner, which generates an electrical signal corresponding to the speed-dependent force on the spring mechanism, impeding from the outset, so that the actual function of the speed controller by deriving the axial movement of the abutment for the Spring mechanism is practically not affected, which increases the operational safety of the entire control system.

Das Federwerk des mechanischen Fliehkraftreglers kann dabei wie bei bekannten Leerlauf-Endreglern ausgebildet sein, und auch eine sogenannte Angleichvorrichtung enthalten, wodurch eine zusätzliche, vom Servomotor angetriebene Angleichvorrichtung nicht notwendig ist.The spring mechanism of the mechanical centrifugal governor can be designed as in known idle end regulators and can also contain a so-called adjustment device, so that an additional adjustment device driven by the servo motor is not necessary.

Nach einem weiteren Vorschlag der Erfindung kann, wie insbesonders im Anspruch 3 angeführt, der Servomotor hydraulisch betätigt sein, was große Verstellkräfte und eine relativ einfache Steuerung ermöglicht, und seine Steuereinrichtung über Federkräfte rückführen.According to a further proposal of the invention, as stated in particular in claim 3, the servo motor can be operated hydraulically, which enables large adjustment forces and a relatively simple control, and return its control device via spring forces.

Im weiteren ist es besonders vorteilhaft, wenn, wie im Anspruch 4 dargelegt, bei einem elektrisch betätigten Servomotor dieser seine Steuereinrichtung über Federkräfte rückführt, da damit eine ebenfalls mögliche Steuerung jeder drehzahlabhängigen Hilfseinrichtung der Brennkraftmaschine über einen eigenen Servomotor sehr vereinfacht wird.Furthermore, it is particularly advantageous if, as set out in claim 4, in the case of an electrically operated servo motor, this returns its control device via spring forces, since this also greatly simplifies the control of each speed-dependent auxiliary device of the internal combustion engine via its own servo motor.

Die bei der Ausführungsform mit dem Kraftaufnehmer vorgesehene elektronische Steuereinheit kann beispielsweise von einem Mikroprozessor gebildet sein, dem weitere Betriebskenngrößen der Brennkraftmaschine, wie z.B. Ladedruck, Außentemperatur, Stellung von Zündschloß, Gashebel oder Regelstange usw. zugeführt und von diesem bei der Steuerung des Servomotors berücksichtigt sind. Der Mikroprozessor erlaubt auf sehr vorteilhafte Weise die Berücksichtigung aller das Betriebsverhalten der Brennkraftmaschine beinflussenden Faktoren nach einem vorgewählten Programm, womit die für den jeweiligen Betriebszustand optimale Einstellung der Hilfseinrichtungen möglich ist.The electronic control unit provided with the force transducer in the embodiment can be formed, for example, by a microprocessor to which further operating parameters of the internal combustion engine, such as e.g. Boost pressure, outside temperature, position of the ignition lock, throttle or control rod etc. supplied and taken into account by this when controlling the servo motor. The microprocessor allows, in a very advantageous manner, all factors influencing the operating behavior of the internal combustion engine to be taken into account according to a preselected program, with which the optimal setting of the auxiliary devices is possible for the respective operating state.

Die elektrisch betätigten Servomotoren können z.B. als Schrittmotoren ausgebildet sein, womit eine genaue und jederzeit reproduzierbare Einstellung der Hilfseinrichtungen vereinfacht und verbessert ist.The electrically operated servo motors can e.g. be designed as stepper motors, which simplifies and improves an accurate and reproducible setting of the auxiliary devices.

Die Erfindung wird im folgenden anhand der in der Zeichnung schematisch dargestellten Ausführungsbeispiele näher erläutert.

  • Fig. 1 zeigt eine erfindungsgemäße Regelanlage mit hydraulisch betätigtem Servomotor,
  • Fig. 2 ein Ausführungsbeispiel mit einem elektrisch betätigten Servomotor,
  • Fig. 3 ein Ausführungsbeispiel mit einem elektronisch gesteuerten Servomotor, und
  • Fig. 4 ein weiteres Ausführungsbeispiel gemäß der Erfindung, ebenfalls mit elektronisch gesteuertem Servomotor.
The invention is explained in more detail below with reference to the exemplary embodiments shown schematically in the drawing.
  • 1 shows a control system according to the invention with a hydraulically operated servo motor,
  • 2 shows an embodiment with an electrically operated servo motor,
  • Fig. 3 shows an embodiment with an electronically controlled servo motor, and
  • Fig. 4 shows another embodiment according to the invention, also with an electronically controlled servo motor.

Gemäß Fig. 1 betätigen die Fliehgewichte 1 des Fliehkraftreglers 2, die an den zweiarmigen Winkelhebeln l' angebracht und auf dem Träger 2' gelagert sind und von der Welle 3 angetrieben werden, über das Spurkugellager 4 die Muffe 5. Das Federwerk 6 des Reglers ist von der Art, wie es bei bekannten Leerlauf-Endreglern Verwendung findet. In einem Widerlager, welches als Patrone 7 ausgebildet und gegenüber dem Gehäuse 11 des Reglers in axialer Richtung beweglich ist, ist eine Leerlauffeder 6' vorgesehen, die sich auf der Muffe 5 einerseits und dem Boden 7' der Patrone 7 andererseits abstützt. Die Patrone 7 enthält auch die Hauptregeifeder 8, sowie einen Federteller 9 und eine Angleichfeder 10.1, the centrifugal weights 1 of the centrifugal governor 2, which are attached to the two-armed angle levers 1 'and are mounted on the carrier 2' and are driven by the shaft 3, actuate the sleeve 5 via the track ball bearing 4. The spring mechanism 6 of the regulator is of the way it is used in known idle end controllers. In an abutment, which is designed as a cartridge 7 and is movable in the axial direction with respect to the housing 11 of the regulator, an idling spring 6 'is provided, which is supported on the sleeve 5 on the one hand and the bottom 7' of the cartridge 7 on the other hand. The cartridge 7 also contains the main ring spring 8, as well as a spring plate 9 and a matching spring 10.

Die von den Fliehgewichten 1 erzeugte Kraft wird über die zweiarmigen Winkelhebel 1' und die Muffe 5 in die Patrone 7 eingeleitet und nicht, wie bei bekannten Reglern üblich, vom Gehäuse 11 des Reglers aufgenommen, sondern über den Ansatz 12' von dem zweiarmigen Hebel 12, der in dem am Gehäuse 11 befestigten Lager 13 gelagert ist, aufgenommen und an den Steuerschieber 14, welcher einen Servomotor 14' steuert, weitergeleitet. Der Hebel 12 ist mit einem über eine Schraube 15 verstellbaren Doppelanschlag 15' in seiner Bewegungsfreiheit begrenzt, womit die freie axiale Bewegung der Patrone 7 gegenüber dem Gehäuse 11 auf einen kleinen Hub beschränkt und damit der Eingriff in das Regelverhalten des Fliehkraftreglers 2 sehr gering ist.The force generated by the centrifugal weights 1 is introduced into the cartridge 7 via the two-armed angle lever 1 ′ and the sleeve 5 and is not received by the housing 11 of the regulator, as is customary in known regulators, but rather via the shoulder 12 ′ by the two-armed lever 12 , which is mounted in the bearing 13 attached to the housing 11, received and passed on to the control slide 14, which controls a servo motor 14 '. The lever 12 is limited in its freedom of movement by means of a double stop 15 'which can be adjusted by means of a screw 15, so that the free axial movement of the cartridge 7 relative to the housing 11 is limited to a small stroke and the intervention in the control behavior of the centrifugal governor 2 is therefore very slight.

Der Steuerschieber 14 wird über eine Auflage 12" vom zweiarmigen Hebel 12 betätigt und ist in der Büchse 16 axial verschiebbar, die mit einem Druckmittelzufluß 16' und Steueröffnungen 17' für die Druckmittelleitung 17 zum Zylinder 21 des hydraulischen Servomotors 14' versehen ist. Der Steuerschieber 14 ist mit Steuerkanten 19 und 20 versehen, welche mit den Steueröffnungen 17' zusammenarbeiten und somit die drehzahlabhängige Betätigung des Arbeitskolbens 18 ermöglichen. Der Arbeitskolben 18 ist im Zylinder 21 geführt, der an seinem im Bilde rechten Ende eine Entlüftungsbohrung 21' aufweist.The control slide 14 is actuated by a support 12 "from the two-armed lever 12 and is axially displaceable in the bush 16, which is provided with a pressure medium inflow 16 'and control openings 17' for the pressure medium line 17 to the cylinder 21 of the hydraulic servo motor 14 '. The control slide 14 is provided with control edges 19 and 20, which cooperate with the control openings 17 'and thus enable the speed-dependent actuation of the working piston 18. The working piston 18 is guided in the cylinder 21, which has a vent hole 21' at its right end in the picture.

Der Arbeitskolben 18, der einerseits durch die Feder 22 belastet ist und andererseits vom Druckmittel beaufschlagt wird, kann nach beiden Bewegungsrichtungen eine Arbeitskraft abgeben.The working piston 18, which is loaded on the one hand by the spring 22 and on the other hand is acted upon by the pressure medium, can release a worker in both directions of movement.

Die von den Fliehgewichten 1 erzeugte, drehzahlabhängige Kraft auf die Muffe 5 wird auf den Hebel 12 übertragen und von diesem über die Auflage 12" an den Steuerschieber 14 weitergeleitet. Der Steuerschieber 14 wird von Federn 23 belastet, die eine Kraftkomponente in Achsrichtung des Steuerschiebers erzeugen und die auf den Steuerschieber übertragene Kraft aufnehmen. Die Federn 23 sind an einem Ende an einem Wulst 24 des Topfes 24' und am anderen Ende an einem Innenwulst 24" des Steuerschiebers 14 eingehängt, wobei sich der Topf 24' über einen den Federn 23 gegenüberliegenden zentral befestigten Stift 25 in einer Bohrung 26 des Arbeitskolbens 18 frei abstützt.The speed-dependent force generated by the centrifugal weights 1 on the sleeve 5 is transmitted to the lever 12 and from there passed on to the control slide 14 via the support 12 ". The control slide 14 is loaded by springs 23, which generate a force component in the axial direction of the control slide and absorb the force transmitted to the control slide. The springs 23 are suspended at one end on a bead 24 of the cup 24 'and at the other end on an inner bead 24 "of the control slide 14, the cup 24' being located opposite one another over the springs 23 centrally fastened pin 25 is freely supported in a bore 26 of the working piston 18.

Wird das Gleichgewicht der Kräfte am Steuerschieber 14 durch eine vom Fliehkraftregler 2 bedingte Änderung der Position des Hebels gestört, so erfolgt eine Auslenkung des Steuerschiebers 14 innerhalb des vom Doppelanschlag 15' begrenzten Weges, wodurch die Steuerkanten 19 und 20 die Druckmittelleitung 17 bzw. die Steueröffnungen 17' entweder mit dem Druckmittelzufluß 16' oder mit dem Abfluß 16" verbinden. Dadurch verschiebt sich der Arbeitskolben 18 in der Weise, daß über die Federn 23 das Gleichgewicht der Kräfte am Steuerschieber 14 bei Abdeckung der Steueröffnungen 17' durch den Steuerschieber 14 wieder hergestellt wird.If the balance of the forces on the control slide 14 is disturbed by a change in the position of the lever caused by the centrifugal regulator 2, the control slide 14 is deflected within the path delimited by the double stop 15 ', as a result of which the control edges 19 and 20 the pressure medium line 17 and the control openings Connect 17 'either to the pressure medium inlet 16' or to the outlet 16 ". As a result, the working piston 18 moves in such a way that the springs 23 restore the balance of the forces on the control slide 14 when the control openings 17 'are covered by the control slide 14 becomes.

Die Ableitung der Verstellkraft vom Arbeitskolben 18 des Servomotors 14' erfolgt über einen zweiarmigen Hebel 27, der in eine Nut 28 des Arbeitskolbens eingreift, an einem am Gehäuse angebrachten Lager 29 schwenkbar gelagert ist und eine Verstellstange 30 in deren Längsrichtung verschiebt.The adjustment force is derived from the working piston 18 of the servo motor 14 'via a two-armed lever 27 which engages in a groove 28 of the working piston, is pivotably mounted on a bearing 29 attached to the housing and displaces an adjusting rod 30 in its longitudinal direction.

Die unmittelbare Ableitung der Regelkraft vom Fliehkraftregler 2 geschieht in üblicher Weise über einen in der Ringnut 31 der Muffe 5 eingreifenden zweiarmigen Reglerhebel 32. Dieser ist auf einer Exzenterwelle 33 gelagert und überträgt die drehzahlabhängigen Bewegungen der Reglermuffe 5 über das Reglergestänge 34 auf die Regelstange 35 einer nicht dargestellten Einspritzpumpe. Ebenfalls auf der Exzenterwelle 33 ist der Bedienungshebel 36 für die Steuerung der gewünschten Einspritzpumpe angeordnet.The direct derivation of the regulating force from the centrifugal regulator 2 takes place in the usual way via a two-armed regulator lever 32 which engages in the annular groove 31 of the sleeve 5. This is mounted on an eccentric shaft 33 and transmits the speed-dependent movements of the regulator sleeve 5 via the regulator linkage 34 to the regulating rod 35 Injection pump, not shown. The operating lever 36 for controlling the desired injection pump is also arranged on the eccentric shaft 33.

Das Ausführungsbeispiel nach der Fig. 2 unterscheidet sich von dem nach der Fig. 1 dadurch, daß das Federwerk 37 des Fliehkraftreglers 38 keine eigene Angleichvorrichtung besitzt, sondern der Servomotor 39 über eine eigene Nocke 70 eine sogenannte Plus-Minus-Angleichung betätigt. Weiters wird hier der Servomotor 39 elektrisch angetrieben. Die Fliehgewichte 40 des Fliehkraftreglers 38 sind über Winkelhebel 40' am Trager 41 gelagert und werden über die Welle 42 von der Brennkraftmaschine angetrieben. Die Bewegung der Fliehgewichte 40 wird über die Winkelhebel und das Spurkugellager 43 auf eine Muffe 44 übertragen, welche an dem dem Kugellager 43 gegenüberliegenden Ende einen mittels eines Stiftes 46 befestigten Federteller 45 aufweist. Eine Leerlauffeder 47 belastet einerseits den Federteller 45 und ist am anderen Ende an der ein Widerlager bildenden Patrone 48, welche auch die am Federteller 50 anliegende Hauptregelfeder 49 enthält, abgestützt.The embodiment of FIG. 2 differs from that of FIG. 1 in that the spring mechanism 37 of the centrifugal controller 38 does not have its own adjustment device, but the servo motor 39 actuates a so-called plus-minus adjustment via its own cam 70. Furthermore, the servo motor 39 is electrically driven here. The centrifugal weights 40 of the centrifugal governor 38 are mounted on the bracket 41 via angle levers 40 ′ and are driven by the internal combustion engine via the shaft 42. The movement of the flyweights 40 is transmitted via the angle levers and the track ball bearing 43 to a sleeve 44 which has a spring plate 45 fastened by means of a pin 46 at the end opposite the ball bearing 43. An idle spring 47, on the one hand, loads the spring plate 45 and is supported at the other end on the cartridge 48 forming an abutment, which also contains the main control spring 49 resting on the spring plate 50.

Die Patrone 48 ist wiederum in axialer Richtung beweglich im Gehäuse 51 gelagert und überträgt die von der Muffe 44 in das Federwerk 37 eingeleitete drehzahlabhängige Kraft auf einen zweiarmigen Hebel 52, welcher in dem am Gehäuse 51 angeordneten Lager 53 schwenkbar gelagert ist.The cartridge 48 is in turn movably mounted in the housing 51 in the axial direction and transmits the speed-dependent force introduced by the sleeve 44 into the spring mechanism 37 to a two-armed lever 52 which is pivotably mounted in the bearing 53 arranged on the housing 51.

Der Hebel 52 trägt an seinem anderen Ende eine Schaltkappe 55, die mit dem Hebel isoliert verbunden ist und über die Schaltkontakte 56 und 57 die elektrische Versorgungsleitung 58 mit den jeweiligen Anschlüssen am Elektromotor 59 verbindet. Der Elektromotor 59 bewegt über ein Getriebe 60 die Spindel 61, auf welcher eine Mutter 62 angeordnet ist, die durch einen in einer axialen Nut 64 am Gehäuse laufenden Stift 63 drehgesichert ist.The lever 52 carries at its other end a switch cap 55 which is connected to the lever in an insulated manner and connects the electrical supply line 58 to the respective connections on the electric motor 59 via the switch contacts 56 and 57. The electric motor 59 moves the spindle 61 via a gear 60, on which a nut 62 is arranged, which is secured against rotation by a pin 63 running in an axial groove 64 on the housing.

Der mit den Schaltkontakten 56 und 57 zusammenwirkende zweiarmige Hebel 52 wird über einen im Gehäuse 51' axial verschiebbar gelagerten Federteller 54 an der Auflage 52' von den Federn 65 und 66, die abhängig vom Verstellweg der Mutter 62 nacheinander auf dem Federteller 54 zur Anlage kommen, belastet.The two-armed lever 52 which interacts with the switching contacts 56 and 57 is moved by a spring plate 54 on the support 52 ', which is axially displaceably mounted in the housing 51' Springs 65 and 66, which come into contact with one another on the spring plate 54 depending on the adjustment path of the nut 62, are loaded.

Die Ableitung der Regelkraft vom Servomotor 39 geschieht über einen in die Ausnehmung 67 der Mutter 62 eingreifenden Hebel 68, welcher die Bewegung der Mutter 62 auf eine Welle 69 überträgt. Diese Welle weist eine Steuernocke 70 auf, die zur Steuerung des Angleichvorganges dient.The control force is derived from the servo motor 39 via a lever 68 which engages in the recess 67 of the nut 62 and which transmits the movement of the nut 62 to a shaft 69. This shaft has a control cam 70 which is used to control the alignment process.

Da die auf die das Widerlager für das Federwerk bildende Patrone des Drehzahlreglers und damit auf die Steuereinrichtung des Servomotors übertragene drehzahlproportionale Kraft, herrührend von der Masse der Fliehgewichte, vom Quadrat der Drehzahl abhängig ist, erweist es sich als zweckmäßig, entweder eine Federkombination bzw. Anordnung gemäß dem Ausführungsbeispiel nach Fig. 1, welche dieses quadratische Gesetz nahezu volkommen berücksichtigt, vorzusehen, oder aber wenigstens eine Kombination von zwei Federn gemäß dem Ausführungsbeispiel nach Fig. 2 vorzusehen, mit welcher zumindest eine Dehnung der Verstellweg/Drehzahl-Kennlinie des Servomotors bzw. der Mutter 62 im unteren Drehzahlbereich der Brennkraftmaschine möglich ist.Since the force proportional to the speed transmitted to the abutment for the spring mechanism and thus to the control device of the servo motor, resulting from the mass of the centrifugal weights, depends on the square of the speed, it proves to be expedient to use either a spring combination or arrangement 1, which takes this quadratic law into account almost completely, or at least to provide a combination of two springs according to the embodiment according to FIG. 2, with which at least one extension of the adjustment path / speed characteristic of the servo motor or the nut 62 in the lower speed range of the internal combustion engine is possible.

Die drehzahlabhängige Bewegung der Reglermuffe 44 des Fliehkraftreglers 38 in Fig. 2 wird von der Hilfsmuffe 71 aufgenommen, welche eine Ringnut 72 aufweist, über die ein Reglerhebel 73 betätigt wird. Dieser stützt sich an seinem anderen Ende 74 bei voller Einspritzmenge der nicht dargestellten Einspritzpumpe auf die Steuernocke '70 ab und betätigt über eine Stange 75 die Regelstange 76 zur Verstellung der Einspritzmenge.The speed-dependent movement of the regulator sleeve 44 of the centrifugal governor 38 in FIG. 2 is absorbed by the auxiliary sleeve 71, which has an annular groove 72, via which a regulator lever 73 is actuated. At its other end 74, the latter is supported on the control cam '70 when the injection pump (not shown) is full and actuates the control rod 76 via a rod 75 to adjust the injection quantity.

Die Hilfsmuffe 71 wird von einer Feder 77 belastet, welche sich am anderen Ende an der der Leerlauffeder 47 gegenüberliegenden Seite des Federtellers 45 abstützt und die Hilfsmuffe 71 bei denjenigen Einspritzmengen, bei denen noch keine Berührung des Endes 74 des Reglerhebels 73 mit der Steuernocke 70 gegeben ist, gegen die Schulter 78 der Muffe 44 drückt.The auxiliary sleeve 71 is loaded by a spring 77, which is supported at the other end on the side of the spring plate 45 opposite the idle spring 47 and the auxiliary sleeve 71 at those injection quantities in which there is still no contact between the end 74 of the control lever 73 and the control cam 70 is against the shoulder 78 of the sleeve 44.

Bei der Ausführungsvariante der Erfindung nach Fig. 3 entspricht die Anordnung der eigentlichen Fliehkraftreglers 79 wieder der bereits zu Fig. 1 besprochenen. Die auf dem Träger 83 über die Winkelhebel 83' verschwenkbar gelagerten Fliehgewichte 82 werden über eine Welle 84 von der nicht näher dargestellten Brennkraftmaschine angetrieben und betätigen über ein Spurkugellager 85 die Muffe 86. Die Leerlauffeder 87 und die Hauptregelfeder 89 sind in beschriebener Weise in der das Widerlager bildenden, gegenüber dem Gehäuse 91 axial beweglichen Patrone 88 angeordnet und von der Muffe 86 belastbar. Wie bei der Ausführung nach Fig. 2 ist auch hier keine Angleichvorrichtung in der Patrone vorgesehen; die Hauptlagerfeder 89 stützt sich unmittelbar auf dem Federteller 90 ab.In the embodiment variant of the invention according to FIG. 3, the arrangement of the actual centrifugal governor 79 again corresponds to that already discussed for FIG. 1. The centrifugal weights 82 which are pivotably mounted on the carrier 83 via the angle levers 83 'are driven via a shaft 84 by the internal combustion engine (not shown in more detail) and actuate the sleeve 86 via a track ball bearing 85. The idle spring 87 and the main regulating spring 89 are described in that Abutment forming, relative to the housing 91 axially movable cartridge 88 arranged and resilient by the sleeve 86. As in the embodiment according to FIG. 2, no matching device is provided in the cartridge here; the main bearing spring 89 is supported directly on the spring plate 90.

Die in die Patrone 88 eingeleitete drehzahlabhängige Kraft wird über einen elektrischen Kraftaufnehmer 92 an die Gehäusepartie 93 des Gehäuses 91 abgegeben. Der Kraftaufnehmer 92 kann z.B. ein geeignet angeordneter Dehnmeßstreifen, ein piezoelektrischer Quarz oder eine ähnliche Einrichtung sein und stellt auch gleichzeitig einen Anschlag, welcher eine nur geringfügige axiale Bewegung der Patrone 88 ermöglicht, dar.The speed-dependent force introduced into the cartridge 88 is delivered to the housing part 93 of the housing 91 via an electrical force transducer 92. The force transducer 92 can e.g. a suitably arranged strain gauge, a piezoelectric quartz or a similar device and at the same time also represents a stop which allows only a slight axial movement of the cartridge 88.

Das drehzahlabhängige elektrische Signal des Kraftaufnehmers 92 wird über Ableitungen 81 einem Mikroprozessor 94 zugeführt, welcher weitere Eingänge 80 besitzt, mittels derer zusätzliche Parameter zur Steuerung des Servomotors 94' berücksichtigt werden können. Solche Parameter sind beispielsweise der Ladeluftdruck, die Außentemperatur, die Temperatur der Brennkraftmaschine bzw. ihrer Brennraumwand, die Stellung des Zündschlosses oder des Bedienungsgestänges, die Position der Regelstange der Einspritzpumpe usw. Der Mikroprozessor 94 setzt diese Parameter nach einem vorbestimmten Programm zusammen und regelt den elektrischen Strom für den Stellmotor 95. Dieser betätigt über eine Welle 96 und eine Schnecke 97 ein Schneckenrad 98, welches mittels eines Gewindes 99 die gegen Drehung gesicherte Regelstange 100 der nicht dargestellten Einspritzpumpe in ihrer Position verschieben kann.The speed-dependent electrical signal of the force transducer 92 is fed via leads 81 to a microprocessor 94 which has further inputs 80, by means of which additional parameters for controlling the servomotor 94 'can be taken into account. Such parameters are, for example, the charge air pressure, the outside temperature, the temperature of the internal combustion engine or its combustion chamber wall, the position of the ignition lock or the control linkage, the position of the control rod of the injection pump, etc. The microprocessor 94 assembles these parameters according to a predetermined program and controls the electrical Current for the servomotor 95. This actuates a worm wheel 98 via a shaft 96 and a worm 97, which can shift the position of the control rod 100 of the injection pump (not shown) by means of a thread 99.

Die Muffe 86 des Fliehkraftreglers 79 weist eine Ringnut 101 auf, in welche der auf der Exzenterwelle 103 gelagerte zweiarmige Reglerhebel 102 eingreift, der über ein Reglergestänge 104' die Verbindung zwischen der drehzahlabhängig bewegten Muffe 86 und dem Schneckenrad 98 und damit der Regelstange 100, herstellt.The sleeve 86 of the centrifugal governor 79 has an annular groove 101, in which the two-armed control lever 102, which is mounted on the eccentric shaft 103, engages and which, via a control linkage 104 ', establishes the connection between the speed-dependent sleeve 86 and the worm wheel 98 and thus the control rod 100 .

Der Mikroprozessor 94 kann natürlich ohne weiters zusätzliche Ausgänge zur Steuerung weiterer Stellmotoren besitzen, womit z.B. die Verstellung des Einspritzzeitpunktes der Brennkraftmaschine erfolgen kann.The microprocessor 94 can of course easily have additional outputs for controlling further servomotors, which means e.g. the injection timing of the internal combustion engine can be adjusted.

Das in Fig. 4 dargestellte Ausführungsbeispiel der Erfindung unterscheidet sich von dem in der Fig. 3 nur dadurch, daß die Muffe 105 des Fliehkraftreglers 104 gegenüber dem Gehäuse 105' drehgesichert ist und die Schnecke 106 des nicht dargestellten Stellmotors auf ein als Hilfsmuffe wirkendes Schneckenrad 107 einwirkt, welches auf einer Gewindestange 108 der Muffe 105 verdrehbar ist. Die Einleitung der drehzahiabhängigen Kraft in das Federwerk erfolgt über den Federteller 111, welcher mit dem Stift 112 auf der Gewindestange 108 befestigt ist. Der zweiarmige Reglerhebel 110 wirkt mit der Ringnut 109 des Schneckenrades 107 zusammen, wodurch auch hier eine Mikroprozessor gesteuerte Angleichung gegeben ist.The embodiment of the invention shown in FIG. 4 differs from that in FIG. 3 only in that the sleeve 105 of the centrifugal governor 104 is secured against rotation with respect to the housing 105 'and the worm 106 of the servomotor, not shown, on a worm wheel 107 acting as an auxiliary sleeve acts, which is rotatable on a threaded rod 108 of the sleeve 105. The speed-dependent force is introduced into the spring mechanism via the spring plate 111, which is fastened to the threaded rod 108 with the pin 112. The two-armed control lever 110 interacts with the annular groove 109 of the worm wheel 107, which also results in a microprocessor-controlled adjustment.

Claims (4)

1. A control system for an internal combustion engine with fuel injection, comprising a mechanical centrifugal governor (2; 38) controlling the volume offuel injected, whose spring mechanism (6; 37) balancing the speed-dependent force of the flyweights (1; 40) is provided with an axially movable support (7; 48), the reaction force of which is employed to activate a control mechanism of a servomotor (14'; 39) for an auxiliary assembly, wherein said support (7; 48) is connected to one of the arms of a two-armed lever (12; 52) whose pivot is fixed relative to the engine housing and whose other arm is acting upon said control mechanism which is connected with said servomotor (14'; 39) via one or more restoring springs (23; 65), and wherein axial movability of said support (7; 48) is limited to a very small range by means of stops (15') or by the contacts (55, 56, 57) of said control mechanism themselves acting as stops.
2. A control system for an internal combustion engine with fuel injection, comprising a mechanical centrifugal governor (79; 104) controlling the volume of fuel injected, whose spring mechanism (87, 89) balancing the speed-dependent force of the flyweights (82) is provided with a support (88) the reaction force of which is employed to activate a control mechanism of a servomotor (94') for an auxiliary assembly, wherein said servomotor (94') is actuated electrically, and wherein said control mechanism of said servomotor (94') is provided with a force pick-up (92) which is located between support (88) and housing (93) of said control system, thus acting as a stop for said support (88), and wherein said force pick-up (92) is connected with an electronic control unit (94) of said control system which itwill actuate by means of an electric signal depending on the force exerted by said support (88).
3. A control system as in claim 1, wherein the control mechanism of a hydraulic servomotor (14') has a slide valve (14) for a pressure medium line (17), which valve is actuated by the two-armed lever (12) in addition to being loaded by springs (23) which will generate a force component along the axis of said slide valve (14) and will compensate the force transmitted to said slide valve (14), and which rest against the working piston (18) of said servomotor in order to restore the position of said slide valve (14).
4. A control system as in claim 1, wherein the two-armed lever (52) of an electrically actuated servo unit (39) is loaded by a spring (65) on the side away from the support (48), and is carrying a contact cap (55) connecting via contacts (56, 57) a power supply line (58) with the terminals of an electric motor (59) of said servo unit (39), and wherein, in order to restore the position of said two-armed lever (52), the end of said spring (65) facing away from said lever is supported by a nut (62) which is secured against turning and is axially movable by said electric motor (59).
EP80890122A 1979-10-16 1980-10-15 Control system for internal-combustion engines Expired EP0029019B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0673879A AT381368B (en) 1979-10-16 1979-10-16 CONTROL SYSTEM FOR INTERNAL COMBUSTION ENGINES
AT6738/79 1979-10-16

Publications (2)

Publication Number Publication Date
EP0029019A1 EP0029019A1 (en) 1981-05-20
EP0029019B1 true EP0029019B1 (en) 1985-04-24

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EP80890122A Expired EP0029019B1 (en) 1979-10-16 1980-10-15 Control system for internal-combustion engines

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US (1) US4409941A (en)
EP (1) EP0029019B1 (en)
JP (1) JPS5664123A (en)
AT (1) AT381368B (en)
DE (1) DE3070556D1 (en)
ES (1) ES495941A0 (en)
PL (1) PL125173B1 (en)
WO (1) WO1984004356A1 (en)
YU (1) YU265580A (en)

Families Citing this family (9)

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Publication number Priority date Publication date Assignee Title
US4474156A (en) * 1982-05-01 1984-10-02 Lucas Industries Public Limited Company Governor mechanism for a fuel pumping apparatus
JPS5960038A (en) * 1982-09-30 1984-04-05 Hino Motors Ltd Apparatus for controlling supply rate of fuel
JPS5952143U (en) * 1982-09-30 1984-04-05 日野自動車株式会社 Fuel supply amount control device
JPS5982539A (en) * 1982-10-29 1984-05-12 Hino Motors Ltd Fuel feed amount controller
DE3430797A1 (en) * 1984-08-22 1986-03-06 Robert Bosch Gmbh, 7000 Stuttgart SPEED REGULATOR FOR FUEL INJECTION PUMPS
DE4115301A1 (en) * 1991-05-10 1992-11-12 Bosch Gmbh Robert CONTROL CAPSULE FOR A CENTRIFUGAL SPEED CONTROLLER
DE4129837C2 (en) * 1991-09-07 2002-06-27 Bosch Gmbh Robert Speed controller for fuel injection pumps of internal combustion engines
LV13238B (en) * 2004-08-06 2004-12-20 Arnis Treijs Mechanical device for distribution of gases that automatically changes phases of intake/exhaust depending of workload and speed of engine
KR102465904B1 (en) * 2017-11-28 2022-11-11 현대자동차주식회사 Automatic transmission for vehicle

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Publication number Priority date Publication date Assignee Title
CH171817A (en) * 1932-12-06 1934-09-15 Bosch Robert Ag Injection pump for internal combustion engines.
CH153911A (en) * 1935-07-08 1932-04-15 Sulzer Ag Internal combustion engine coupled to an electric generator on vehicles.
FR836577A (en) * 1938-04-13 1939-01-20 Device for adjusting the flow rate of an injection pump, particularly applicable to automobile engines
FR1052850A (en) * 1951-02-07 1954-01-28 Davey Stabilizer for automatic control and regulation systems, in particular of motors
US3645097A (en) * 1968-10-18 1972-02-29 Diesel Kiki Co Hydraulic governor
JPS52148730A (en) * 1976-06-04 1977-12-10 Komatsu Ltd Governor correction device in fuel injection pump for engine
DE2650246C2 (en) * 1976-11-02 1986-07-10 Robert Bosch Gmbh, 7000 Stuttgart Control device for a fuel injection pump of a diesel engine
US4109628A (en) * 1976-11-08 1978-08-29 Caterpillar Tractor Co. Adjustable regulation governor

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ES8200439A1 (en) 1981-10-16
EP0029019A1 (en) 1981-05-20
DE3070556D1 (en) 1985-05-30
ATA673879A (en) 1986-02-15
US4409941A (en) 1983-10-18
WO1984004356A1 (en) 1984-11-08
JPS5664123A (en) 1981-06-01
ES495941A0 (en) 1981-10-16
YU265580A (en) 1983-01-21
PL227314A1 (en) 1981-06-19
PL125173B1 (en) 1983-04-30
AT381368B (en) 1986-10-10

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