EP0298964B1 - Actuating cylinder - Google Patents

Actuating cylinder Download PDF

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Publication number
EP0298964B1
EP0298964B1 EP87901355A EP87901355A EP0298964B1 EP 0298964 B1 EP0298964 B1 EP 0298964B1 EP 87901355 A EP87901355 A EP 87901355A EP 87901355 A EP87901355 A EP 87901355A EP 0298964 B1 EP0298964 B1 EP 0298964B1
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EP
European Patent Office
Prior art keywords
actuating cylinder
piston
stop
compression spring
spring
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP87901355A
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German (de)
French (fr)
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EP0298964A1 (en
Inventor
Ortwin Engfer
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D17/00Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/04Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling rendering engines inoperative or idling, e.g. caused by abnormal conditions
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02DCONTROLLING COMBUSTION ENGINES
    • F02D11/00Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/06Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance
    • F02D11/08Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the pneumatic type
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00Engines characterised by air compression and subsequent fuel addition
    • F02B3/06Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to an actuating cylinder for changing amounts of fuel supplied to a vehicle drive motor.
  • An actuator is known from the magazine “Ingenieurs de l'Automobile", Octobre 1984, page 115, which is built into a linkage which is located between a pedal and an adjusting lever of a diesel injection pump.
  • a piston of the actuating cylinder is then automatically pressurized with compressed air, for example, against the force of a prestressed compression spring when an impermissible traction slip is achieved on the drive wheels of an assigned motor vehicle.
  • the compression spring is partially compressed, so that the length of the linkage changes, with the result of a reduction in the injection quantities that the diesel injection pump supplies to a drive motor of the motor vehicle.
  • a control device for limiting the speed and speed of a drive motor of a motor vehicle.
  • This control device also adjusts a diesel injection pump by means of an actuating cylinder, which contains a piston and a preloaded compression spring, and a linkage in order to reduce the fuel injection quantities.
  • This actuating cylinder is also used to switch off the diesel injection pump.
  • the actuating cylinder and a valve arrangement arranged upstream of it, which is part of the control device, can also be used to reduce the fuel supply and thus drive slip.
  • an actuating cylinder arrangement built into a linkage which has an outer cylinder with an annular piston, an inner cylinder arranged in this annular piston and a second piston which can be displaced therein.
  • the outer cylinder has two control ports for two pressurized chambers, one of which is assigned to the ring piston and the other to the inner second piston. Applying pressure to the ring piston shortens the linkage and thereby switches off the injection pump.
  • Actuation of the piston located in the inner cylinder via a valve which can be controlled by means of an accelerator pedal and a downstream throttle causes the associated compression spring to be gradually compressed and, as a result, only gradually increases the injection quantities for quietly accelerating the vehicle. Accordingly, DE-A-3 122 666 teaches how two independently working combinations of one cylinder, one piston and one compression spring can be integrated into one construction unit.
  • the actuating cylinder according to the invention with the features of claim 1 has the advantage that, on the one hand, it enables fine speed control, for example in the event of traction slip, and, on the other hand, requires only an insignificantly greater action on its piston for switching off the diesel injection pump.
  • the piston diameter can be selected to be relatively small at a predetermined maximum possible application pressure, which is predetermined by a pump installed in the motor vehicle, as a result of which installation in the motor vehicle is facilitated and causes less costs.
  • the measures listed in the subclaims enable advantageous developments and improvements of the actuating cylinder specified in the main claim.
  • the characterizing features of claim 2 indicate an advantageous embodiment for the movable stop.
  • the characterizing features of claim 3 give an advantageous embodiment for the stop firmly combined with the actuating cylinder.
  • the characterizing features of claim 4 have the advantage that the compression springs are protected against inadmissible compression and damage.
  • FIG. 1 shows a longitudinal section through the actuating cylinder according to the invention and
  • FIG. 2 shows a displacement-force characteristic curve of a spring combination installed in the actuating cylinder according to FIG. 1.
  • the actuating cylinder 2 according to the invention according to FIG. 1 is connected to a valve combination 3, which is supplied from a store 5 which can be loaded by a pump 4.
  • the pump 4 can be the pump that is used for the supply a compressed air brake system is determined.
  • the valve combination 3 can be designed in a manner disclosed in the journal "Engineers de l'Automobile", 1984, page 115 and can be controlled by a traction controller 6 described there. Instead of the 3/2-way valve disclosed in this magazine, a valve combination described in DE-PS 33 23 563 can also be used, by means of which the pressure medium consumption can be reduced.
  • the actuating cylinder 2 has two bores 7 and 8, which are aligned with one another and are aligned on the same axis, a piston 9, a piston rod 10, a first compression spring 11 intended for traction control operation, a second compression spring 12, an axially displaceable stop 13 and a cylinder base 14.
  • the bore 7 is designed as a blind bore and forms the actual cylinder bore, which is connected to the valve combination 3 via a connection bore 15 and a flexible line 16.
  • a threaded hole 18 is drilled from the outside at a closed end 17.
  • the piston 9 is matched to the diameter of the bore 7 and has a sealing ring 19 for sealing relative to this bore 7.
  • the bore 7 is adjoined by a jump in diameter 20 in the direction of an open end 21 of the actuating cylinder 2.
  • the bore 8 has a larger diameter than the bore 7.
  • a locking ring 22 is arranged, which holds the cylinder base 14 in the actuating cylinder 2.
  • the cylinder base 14 has, coaxially with the actuating cylinder 2, a guide bush 23 for the piston rod 10, which protrudes from the actuating cylinder 2 and has, for example, a connecting thread 24.
  • the jump in diameter 20 forms an annular surface which, in the context of the invention, serves as an axial stop rigidly connected to the actuating cylinder 2.
  • the axially displaceable stop 13 is assigned to this rigid axial stop 20 and has a diameter which is larger than that of the bore 7, but smaller than that of the bore 8.
  • the axially displaceable stop 13 is designed, for example, essentially in the manner of an annular disk and has a molded bush 25 in the direction of the piston 9.
  • the compression spring 12 is inserted between the axially movable stop 13 and the cylinder base 14. It presses the axially displaceable stop 13 against the axial stop 20.
  • the compression spring 11 is inserted between the axially displaceable stop 13 and the piston 9 and surrounds the piston rod 10 and also the bush 25 with radial play.
  • a shoulder 26 of the piston 9 abuts the end 17 of the actuating cylinder 2
  • a distance A between this piston 9 and the bush 25.
  • the piston position 10 is an arrow W pointing away assigned.
  • Wires from which the compression springs 11 and 12 are wound have, for example, the same wire diameter. However, the winding radii of the two compression springs 11 and 12 are different.
  • the compression spring 12 has, for example, approximately twice as many turns as the compression spring 11. Both compression springs 11 and 12 are installed in the actuating cylinder 2 in the prestressed state.
  • the path-force diagram according to FIG. 2 shows the course of the forces F of the two compression springs 11 and 12 over the web W.
  • the compression spring 11 has a preload V1. When the piston 9 is subjected to a very low pressure, for example air pressure, the piston 9 initially remains in the basic position shown.
  • the compression spring 12 is preloaded with a force V2, which in the diagram according to FIG. 2 lies at a point P2, which is perpendicular to the point P1.
  • V2 a force required in order to overcome the force V2 of the spring 12.
  • the piston 9 moves the axially displaceable stop 13 against the force of the compression spring 12 via the bush 25.
  • the increase in the force of the compression spring 12 as a function of the path W is also shown in the form of a straight line with the designation C2 .
  • the slope of the straight line C2 is less than that of the straight line C1.
  • the distance A is preferably chosen so that a displacement of the piston rod 10 relative to the actuating cylinder 2 is reduced to substantially a reduction in full-load injection quantities Idle injection quantities results in the event that the actuating cylinder 2 is located between a fully depressed pedal and an associated diesel injection pump.
  • the .Adjustment option up to size A is available for limiting or reducing drive slip. Therefore, the compression spring 11 can also be referred to as a speed regulating spring. As already indicated at the beginning, for the purpose of sensitive regulation of traction slip, this speed regulating spring 11 is designed to be relatively stiff.
  • the actuating cylinder 2 also serves to regulate a drive torque of a drive motor of a vehicle to such a size that an optimal drive slip is not exceeded or is not significantly exceeded.
  • the greatest possible acceleration can be achieved with sufficient tracking of the driven vehicle.
  • the use of the actuating cylinder 2 according to the invention in connection with gasoline injection pumps or carburettors is suitable for light vehicles such as small trucks, minibuses and passenger cars. Because a hydraulic pump is occasionally available in such vehicles instead of a compressed air pump, the diameter of the piston 9 can, if necessary, be chosen to be smaller than when pressurized with compressed air.

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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)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)

Abstract

Actuating cylinder (2) which is a component of a system for limiting drive slippage and also serves to shut off a fuel feed system (28), which can be controlled by the drive slippage limiting system, and can for example be a diesel injection pump of a vehicle engine. The actuating cylinder (2) is provided with a pressurizable piston (9), a piston rod (10), two pressure springs (11, 12) incorporated in the pre-loaded state and between these an axially displaceable stop (13). The more strongly pre-loaded spring (12) presses the axially displaceable stop (13) against a stop (20) which is rigidly connected to the actuating cylinder (2). The less strongly pre-loaded pressure spring (11) presses against the axially displaceable stop (13) and presses against the piston (9). This pressure spring (11) is designed to be relatively stiff and during operation of the drive slippage limiting system is more or less strongly compressed by actuation of the piston (9). To achieve total switching off of the fuel feed system the piston (9) is actuated more strongly so that also the second strongly pre-loaded pressure spring (12), which is provided with a lower stiffness than the first pressure spring (11), is also compressed. The arrangement of the two pressure springs (11, 12) provides a fine adjustment of the drive slippage and simplifies the switching-off of the fuel feed system.

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Stellzylinder zum Verändern von einem Fahrzeugantriebsmotor zugeführten Brennstoffmengen.The invention relates to an actuating cylinder for changing amounts of fuel supplied to a vehicle drive motor.

Durch die Zeitschrift "Ingenieurs de l'Automobile", Octobre 1984, Seite 115 ist ein Stellzylinder bekannt, der in ein Gestänge eingebaut ist, das sich zwischen einem Pedal und einem Verstellhebel einer Dieseleinspritzpumpe befindet. Ein Kolben des Stellzylinders wird entgegen der Kraft einer vorgespannten Druckfeder dann automatisch beispielsweise mit Druckluft beaufschlagt, wenn an Antriebsrädern eines zugeordneten Kraftfahrzeugs ein unzulässiger Antriebsschlupf erreicht wird. Durch die Beaufschlagung des Kolbens wird die Druckfeder teilweise zusammengedrückt, so daß sich die Länge des Gestänges ändert mit der Folge einer Verringerung der Einspritzmengen, die die Dieseleinspritzpumpe einem Antriebsmotor des Kraftfahrzeugs zuführt. Wird die Beaufschlagung des Kolbens so erhöht, daß die Druckfeder nahezu vollständig zusammengedrückt wird, so schaltet der Kolben die Dieseleinspritzpumpe ab und stoppt die Brennstoffzufuhr zum Antriebsmotor. Es wurde erkannt, daß zur feinfühligen Regulierung von Antriebsschlupf eine harte Druckfeder günstig ist. Diese hat aber den Nachteil, daß sie das Abstellen der Dieseleinspritzpumpe unnötig erschwert, weswegen entweder ein hoher Beaufschlagungsdruck für den Kolben oder aber ein großer Kolbendurchmesser benötigt wird, der mehr Bauraum beansprucht und höhere Herstellungskosten verursacht.An actuator is known from the magazine "Ingenieurs de l'Automobile", Octobre 1984, page 115, which is built into a linkage which is located between a pedal and an adjusting lever of a diesel injection pump. A piston of the actuating cylinder is then automatically pressurized with compressed air, for example, against the force of a prestressed compression spring when an impermissible traction slip is achieved on the drive wheels of an assigned motor vehicle. By acting on the piston, the compression spring is partially compressed, so that the length of the linkage changes, with the result of a reduction in the injection quantities that the diesel injection pump supplies to a drive motor of the motor vehicle. If the pressure on the piston is increased so that the compression spring is almost completely compressed, the piston switches off the diesel injection pump and stops the fuel supply to the drive motor. It was recognized that a hard compression spring is favorable for the sensitive regulation of drive slip. However, this has the disadvantage that it makes it unnecessarily difficult to switch off the diesel injection pump, which is why either a high pressure for the piston or a large piston diameter is required, which takes up more installation space and causes higher manufacturing costs.

Durch die DE-PS 33 23 563 ist eine Steuereinrichtung bekannt zur Drehzahl- und Geschwindigkeitsbegrenzung eines Antriebsmotors eines Kraftfahrzeugs. Diese Steuereinrichtung verstellt ebenfalls über einen Stellzylinder, der einen Kolben und eine vorgespannte Druckfeder enthält, und eine Gestänge eine Dieseleinspritzpumpe im Sinne einer Verminderung der Kraftstoffeinspritzmengen. Auch dieser Stellzylinder wird zum Abschalten der Dieseleinspritzpumpe eingesetzt. Der Stellzylinder und eine ihm vorgeordnete Ventilanordnung, die Bestandteil der Steuereinrichtung ist, kann ebenfalls zur Verminderung der Brennstoffzufuhr und damit von Antriebsschlupf verwendet werden.From DE-PS 33 23 563 a control device is known for limiting the speed and speed of a drive motor of a motor vehicle. This control device also adjusts a diesel injection pump by means of an actuating cylinder, which contains a piston and a preloaded compression spring, and a linkage in order to reduce the fuel injection quantities. This actuating cylinder is also used to switch off the diesel injection pump. The actuating cylinder and a valve arrangement arranged upstream of it, which is part of the control device, can also be used to reduce the fuel supply and thus drive slip.

Durch die DE-A-3 122 666 ist eine in eine Gestänge eingebaute Stellzylinderanordnung bekannt, die einen äußeren Zylinder mit einem Ringkolben, einen in diesem Ringkolben angeordneten inneren Zylinder und einen in diesem verschiebbaren zweiten Kolben aufweist. Es sind zwei Druckfedern in vorgespanntem Zustand so eingebaut, daß die eine Druckfeder den Ringkolben relativ zum außeren Zylinder in Richtung einer Ausgangsstellung und die andere Druckfeder den Kolben zweiten in Richtung einer Ausgangsstellung relativ zum inneren Zylinder belastet. Der äußere Zylinder hat zwei Steueranschlüsse für zwei gegeneinander abgedichtete Beaufschlagungskammern, von denen die eine dem Ringkolben und die andere dem innenliegenden zweiten Kolben zugeordnet ist. Eine Beaufschlagung des Ringkolbens verkürzt das Gestänge und schaltet dadurch die Einspritzpumpe ab. Eine Beaufschlagung des im inneren Zylinder befindlichen Kolbens über ein mittels eines Fahrpedals steuerbares Ventil und eine nachgeordnete Drossel bewirkt eine allmähliche Zusammendrückung der zugeordneten Druckfeder und dadurch eine nur allmählich ansteigende Vergrößerung von Einspritzmengen zum geräuscharmen Beschleunigen des Fahrzeugs. Demgemäß lehrt die DE-A-3 122 666, wie man zwei unabhängig voneinander arbeitende Kombinationen aus je einem Zylinder, einem Kolben und einer Druckfeder zu einer Bauerinheit integrieren kann.From DE-A-3 122 666 an actuating cylinder arrangement built into a linkage is known which has an outer cylinder with an annular piston, an inner cylinder arranged in this annular piston and a second piston which can be displaced therein. There are two compression springs installed in the prestressed state so that one compression spring loads the annular piston relative to the outer cylinder in the direction of an initial position and the other compression spring loads the piston second in the direction of an initial position relative to the inner cylinder. The outer cylinder has two control ports for two pressurized chambers, one of which is assigned to the ring piston and the other to the inner second piston. Applying pressure to the ring piston shortens the linkage and thereby switches off the injection pump. Actuation of the piston located in the inner cylinder via a valve which can be controlled by means of an accelerator pedal and a downstream throttle causes the associated compression spring to be gradually compressed and, as a result, only gradually increases the injection quantities for quietly accelerating the vehicle. Accordingly, DE-A-3 122 666 teaches how two independently working combinations of one cylinder, one piston and one compression spring can be integrated into one construction unit.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße Stellzylinder mit den Merkmalen des Anspruchs 1 hat den Vorteil, daß er einerseits eine feine Drehzahlregelierung beispielsweise im Antriebsschlupfschutzfall ermöglicht und andererseits für das Abschalten der Dieseleinspritzpumpe eine nur unwesentlich stärkere Beaufschlagung seines Kolbens erfordert. Dadurch kann bei einem vorgegebenen höchstmöglichen Beaufschlagungsdruck, der durch eine in das Kraftfahrzeug eingebaute Pumpe vorgegeben ist, der Kolbendurchmesser relativ klein gewählt werden, wodurch der Einbau in das Kraftfahrzeug erleichtert wird und weniger Kosten verursacht.The actuating cylinder according to the invention with the features of claim 1 has the advantage that, on the one hand, it enables fine speed control, for example in the event of traction slip, and, on the other hand, requires only an insignificantly greater action on its piston for switching off the diesel injection pump. As a result, the piston diameter can be selected to be relatively small at a predetermined maximum possible application pressure, which is predetermined by a pump installed in the motor vehicle, as a result of which installation in the motor vehicle is facilitated and causes less costs.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Hauptanspruch angegebenen Stellzylinders möglich. Die kennzeichnenden Merkmale des Anspruchs 2 geben ein vorteilhaftes Ausführungsbeispiel für den beweglichen Anschlag an. Die kennzeichnenden Merkmale des Anspruchs 3 geben ein vorteilhaftes Ausführungsbeispiel an für den fest mit dem Stellzylinder vereinigten Anschlag. Die kennzeichnenden Merkmale des Anspruchs 4 haben den Vorteil, daß die Druckfedern vor unzulässiger Zusammendrückung und Beschädigung geschützt werden.The measures listed in the subclaims enable advantageous developments and improvements of the actuating cylinder specified in the main claim. The characterizing features of claim 2 indicate an advantageous embodiment for the movable stop. The characterizing features of claim 3 give an advantageous embodiment for the stop firmly combined with the actuating cylinder. The characterizing features of claim 4 have the advantage that the compression springs are protected against inadmissible compression and damage.

Zeichnungdrawing

Ein Ausführungsbeispiel der erfindungsgemäßen Stellzylinders ist in der Zeichung dargestellt und nachfolgend näher beschrieben. Es zeigen Figur 1 eine Längsschnitt durch den erfindungsgemäßen Stellzylinder und Figur 2 eine Weg-Kraft-Kennlinie einer in den Stellzylinder gemäß der Figur 1 eingebauten Federkombination.An embodiment of the actuating cylinder according to the invention is shown in the drawing and described in more detail below. FIG. 1 shows a longitudinal section through the actuating cylinder according to the invention and FIG. 2 shows a displacement-force characteristic curve of a spring combination installed in the actuating cylinder according to FIG. 1.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Der erfindungsgemäße Stellzylinder 2 gemäß der Figur 1 ist an eine Ventilkombination 3 angeschlossen, die aus einem von einer Pumpe 4 ladbaren Speicher 5 versorgt wird. Dabei kann die Pumpe 4 diejenige Pumpe sein, die zur Versorgung einer Druckluftbremsanlage bestimmt ist. Die Ventilkombination 3 kann in einer in der Zeitschrift "Ingenieurs de l'Automobile", 1984, Seite 115 offenbarten Weise ausgebildet und von einem dort beschriebenen Antriebsschlupfregler 6 gesteuert werden. Anstelle des in dieser Zeitschrift offenbarten 3/2-Wegeventils kann auch eine in der DE-PS 33 23 563 beschriebene Ventilkombination verwendet werden, mittels der der Druckmittelverbrauch vermindert werden kann.The actuating cylinder 2 according to the invention according to FIG. 1 is connected to a valve combination 3, which is supplied from a store 5 which can be loaded by a pump 4. The pump 4 can be the pump that is used for the supply a compressed air brake system is determined. The valve combination 3 can be designed in a manner disclosed in the journal "Engineers de l'Automobile", 1984, page 115 and can be controlled by a traction controller 6 described there. Instead of the 3/2-way valve disclosed in this magazine, a valve combination described in DE-PS 33 23 563 can also be used, by means of which the pressure medium consumption can be reduced.

Der Stellzylinder 2 besitzt zwei gleichachsig ausgerichtete zueinander abgestufte Bohrungen 7 und 8, einen Kolben 9, eine Kolbenstange 10, eine erste, für den Antriebsschlupfregelbetrieb bestimmte Druckfeder 11, eine zweite Druckfeder 12, einen axial verschiebbaren Anschlag 13 und eine Zylinderboden 14.The actuating cylinder 2 has two bores 7 and 8, which are aligned with one another and are aligned on the same axis, a piston 9, a piston rod 10, a first compression spring 11 intended for traction control operation, a second compression spring 12, an axially displaceable stop 13 and a cylinder base 14.

Die Bohrung 7 ist als eine Sackbohrung ausgebildet und bildet die eigentliche Zylinderbohrung, die über eine Anschlußbohrung 15 und eine flexible Leitung 16 an die Ventilkombination 3 angeschlossen ist. In der Verlängerung der Bohrung 7 ist an einem geschlossenen Ende 17 von außen her ein Gewindeloch 18 eingebohrt. In dieses Gewindeloch 18 wird ein nicht dargestelltes Teil eines Gestänges, das sich zwischen einem Gaspedal 27 und einer Dieseleinspritzpumpe 28 oder einem anderen verstellbaren Brennstoffzuführsystem befindet, eingeschraubt. Der Kolben 9 ist auf den Durchmesser der Bohrung 7 abgestimmt und besitzt zur Abdichtung relativ zu dieser Bohrung 7 einen Dichtring 19. An die Bohrung 7 schließt sich anschließend an einen Durchmessersprung 20 in Richtung eines offenen Endes 21 des Stellzylinders 2 die Bohrung 8 an. Die Bohrung 8 hat einen größeren Durchmesser als die Bohrung 7. Beim offenen Ende 21 ist ein Sicherungsring 22 angeordnet, der den Zylinderboden 14 im Stellzylinder 2 hält. Der Zylinderboden 14 hat koaxial zum Stellzylinder 2 eine Führungsbuchse 23 für die Kolbenstange 10, die aus dem Stellzylinder 2 herausragt und beispielsweise ein Anschlußgewinde 24 besitzt.The bore 7 is designed as a blind bore and forms the actual cylinder bore, which is connected to the valve combination 3 via a connection bore 15 and a flexible line 16. In the extension of the bore 7, a threaded hole 18 is drilled from the outside at a closed end 17. A part of a linkage, not shown, which is located between an accelerator pedal 27 and a diesel injection pump 28 or another adjustable fuel supply system, is screwed into this threaded hole 18. The piston 9 is matched to the diameter of the bore 7 and has a sealing ring 19 for sealing relative to this bore 7. The bore 7 is adjoined by a jump in diameter 20 in the direction of an open end 21 of the actuating cylinder 2. The bore 8 has a larger diameter than the bore 7. At the open end 21, a locking ring 22 is arranged, which holds the cylinder base 14 in the actuating cylinder 2. The cylinder base 14 has, coaxially with the actuating cylinder 2, a guide bush 23 for the piston rod 10, which protrudes from the actuating cylinder 2 and has, for example, a connecting thread 24.

Der Durchmessersprung 20 bildet eine Ringfläche, die im Rahmen der Erfindung als ein starr mit dem Stellzylinder 2 verbundener Axialanschlag dient. Der axial verschiebbare Anschlag 13 ist diesem starren Axialanschlag 20 zugeordnet und hat einen Durchmesser, der größer als derjenige der Bohrung 7, jedoch kleiner als der der Bohrung 8 ist. Der axial verschiebbare Anschlag 13 ist beispielsweise im wesentlichen nach Art einer Ringscheibe ausgebildet und weist in Richtung zum Kolben 9 eine angeformte Buchse 25 auf. Zwischen den axial verscheibbaren Anschlag 13 und den Zylinderboden 14 ist die Druckfeder 12 eingesetzt. Sie drückt den axial verschiebbaren Anschlag 13 gegen den Axialanschlag 20. Dem Druckfeder 11 ist zwischen den axial verschiebbaren Anschlag 13 und den Kolben 9 eingesetzt und umgibt die Kolbenstange 10 und auch die Buchse 25 mit radialem Spiel. In der dargestellten Endstellung des Kolbens 9, in der ein Ansatz 26 des Kolbens 9 an dem Ende 17 des Stellzylinders 2 anliegt, befindet sich zwischen diesem Kolben 9 und der Buchse 25 ein Abstand A. Beim Anschlußgewinde 24 ist der Kolbenstande 10 ein weganzeigender Pfeil W zugeordnet.The jump in diameter 20 forms an annular surface which, in the context of the invention, serves as an axial stop rigidly connected to the actuating cylinder 2. The axially displaceable stop 13 is assigned to this rigid axial stop 20 and has a diameter which is larger than that of the bore 7, but smaller than that of the bore 8. The axially displaceable stop 13 is designed, for example, essentially in the manner of an annular disk and has a molded bush 25 in the direction of the piston 9. The compression spring 12 is inserted between the axially movable stop 13 and the cylinder base 14. It presses the axially displaceable stop 13 against the axial stop 20. The compression spring 11 is inserted between the axially displaceable stop 13 and the piston 9 and surrounds the piston rod 10 and also the bush 25 with radial play. In the illustrated end position of the piston 9, in which a shoulder 26 of the piston 9 abuts the end 17 of the actuating cylinder 2, there is a distance A between this piston 9 and the bush 25. At the connecting thread 24, the piston position 10 is an arrow W pointing away assigned.

Drähte, aus den die Druckfedern 11 und 12 gewickelt sind, haben beispielsweise gleiche Drahtdurchmesser. Unterschiedlich sind jedoch die Wickelradien der beiden Druckfedern 11 und 12. Die Druckfeder 12 hat beispielsweise etwa doppelt so viele Windungen wie die Druckfeder 11. Beide Druckfedern 11 und 12 sind in vorgespanntem Zustand in den Stellzylinder 2 eingebaut. Im Weg-Kraft-Diagramm gemäß der Figur 2 ist über dem Web W der Verlauf der Kräfte F der beiden Druckfedern 11 und 12 dargestellt. Die Druckfeder 11 hat eine Vorspannung V1. Bei einer Beaufschlagung des Kolbens 9 mit einem sehr kleinen Druck, beispielsweise Luftdruck, verbleibt der Kolben 9 zunächst in der dargestellten Grundstellung. Erst wenn die Beaufschlagung eine Stärke erreicht hat, die die Kraft V1 der vorgespannten Druckfeder 11 überwindet, wird diese zusammengedrückt, wobei der Kolben 9 die Kolbenstange 10 in Richtung es Pfeiles W bewegt. Dabei setzt die Druckfeder 11 dem Kolben 9 eine ansteigende Kraft entgegen. Die qualitative Abhängigkeit des Anstiegs der Kraft F bei größer werdendem Weg W der Kolbenstange ist in der Figur 1 mittels einer ansteigenden Geraden C1 dargestellt. Die Gerade C1 endet an einem Punkt P1. Bis dahin hat der Kolben 9 in Richtung der Buchse 25 dem Weg A durchlaufen. Die Büchse 25 begrenzt die Zusammendrückbarkeit der Druckfeder 11.Wires from which the compression springs 11 and 12 are wound have, for example, the same wire diameter. However, the winding radii of the two compression springs 11 and 12 are different. The compression spring 12 has, for example, approximately twice as many turns as the compression spring 11. Both compression springs 11 and 12 are installed in the actuating cylinder 2 in the prestressed state. The path-force diagram according to FIG. 2 shows the course of the forces F of the two compression springs 11 and 12 over the web W. The compression spring 11 has a preload V1. When the piston 9 is subjected to a very low pressure, for example air pressure, the piston 9 initially remains in the basic position shown. Only when the loading has reached a strength that overcomes the force V1 of the prestressed compression spring 11 is it compressed, with the piston 9 moving the piston rod 10 in the direction of the arrow W. The compression spring 11 opposes the piston 9 with an increasing force. The qualitative dependence of the increase in the force F as the distance W of the piston rod increases is shown in FIG. 1 by means of a rising straight line C1. The straight line C1 ends at a point P1. Until then, the piston 9 has traversed path A in the direction of the bushing 25. The sleeve 25 limits the compressibility of the compression spring 11.

Die Druckfeder 12 ist vorgespannt mit einer Kraft V2, die in dem Diagramm gemäß der Figur 2 bei einem Punkt P2 liegt, de sich senkrecht über dem Punkt P1 befindet. Dies hat zur Folge, daß nach dem Anschlagen des Kolbens 9 an der Buchse 25 eine weitere Steigerung der Beaufschlagung des Kolbens 9 notwendig ist, um die Kraft V2 der Feder 12 zu überwinden. Beit weiterer Steigerung der Beaufschlagung verschiebt der Kolben 9 über die Buchse 25 den axial verschiebbaren Anschlag 13 gegen die Kraft der Druckfeder 12. Das dabei erfolgende Anwachsen der Kraft der Druckfeder 12 als Funktion des Weges W ist ebenfalls in Form einer Geraden mit der Bezeichung C2 dargestellt. Die Neigung der Geraden C2 ist geringer als die der Geraden C1. Zeichnet man in einer Verlängerung der Geraden C1 eine Gerade C1 a ein, so schnieden sich die Geraden C2 und C1a in einem Punkt P3. Rechts neben dem Punkt P3 divergieren die Geraden C2 und C1a. Das Diagramm stellt also dar, daß zum Verschieben der Kolbenstange 10 zunächst ein steiler Anstieg der Beaufschlagung des Kolbens 9 notwendig ist, wogegen später eine relativ wenig ansteigende Beaufschlagung des Kolbens 9 relativ große Verschiebungen der Kolbenstange 10 bewirkt.The compression spring 12 is preloaded with a force V2, which in the diagram according to FIG. 2 lies at a point P2, which is perpendicular to the point P1. The consequence of this is that after the piston 9 strikes the bushing 25, a further increase in the action on the piston 9 is necessary in order to overcome the force V2 of the spring 12. When the load is further increased, the piston 9 moves the axially displaceable stop 13 against the force of the compression spring 12 via the bush 25. The increase in the force of the compression spring 12 as a function of the path W is also shown in the form of a straight line with the designation C2 . The slope of the straight line C2 is less than that of the straight line C1. If a straight line C1 a is drawn in an extension of the straight line C1, the straight lines C2 and C1a intersect at a point P3. Straight lines C2 and C1a diverge to the right of point P3. The diagram thus shows that for the displacement of the piston rod 10 a steep increase in the loading of the piston 9 is initially necessary, whereas later a relatively little increasing loading of the piston 9 causes relatively large displacements of the piston rod 10.

Der Abstand A wird vorzugsweise so gewählt, daß eine Verschiebung der Kolbenstange 10 relativ zum Stellzylinder 2 einer Reduzierung von Vollasteinspritzmengen bis im wesentlichen auf Leerlaufeinspritzmengen ergibt für den Fall, daß der Stellzylinder 2 sich zwischen einem voll durchgetretenen Pedal und einer zugeordneten Dieseleinspritzpumpe befindet. Die .Verstellmöglichkeit bis zur Größe A steht zur Verfügung zum Begrenzen oder Vermindern von Antriebsschlupf. Deshalb kann man die Druckfeder 11 auch als Drehzahlregulierfeder bezeichnen. Wie bereits eingangs angedeutet, ist zum Zwecke einer feinfühligen Regelung von Antriebsschlupf diese Drehzahlregulierfeder 11 relativ steif ausgebildet.The distance A is preferably chosen so that a displacement of the piston rod 10 relative to the actuating cylinder 2 is reduced to substantially a reduction in full-load injection quantities Idle injection quantities results in the event that the actuating cylinder 2 is located between a fully depressed pedal and an associated diesel injection pump. The .Adjustment option up to size A is available for limiting or reducing drive slip. Therefore, the compression spring 11 can also be referred to as a speed regulating spring. As already indicated at the beginning, for the purpose of sensitive regulation of traction slip, this speed regulating spring 11 is designed to be relatively stiff.

Zum Abschalten der Dieseleinspritzpumpe werden, wie bereits angedeutet, Wege W der Kolbenstange benötigt, die größer sind als der Weg A, den der Kolben 9 relativ zur Buchse 25 zurücklegen kann. Zum Abschalten der Dieseleinspritzpumpe muß also die Beaufschlagung des Kolbens 9 so weit gesteigert werden, daß mindestens die infolge von Vorspannung vorhandene Kraft V2 der Druckfeder 12 überwunden wird. Es ist also erkennbar, daß lediglich ein Beaufschlagungsüberschuß, der auf den Kolben 9 wirkt, diejenigen Kräfte an der Kolbenstange 10 erzeugt, die zur Abschaltung der Dieseleinspritzpumpe nutzbar sind. Infolge der Ausgestaltung der Druckfeder 12 mit der Kennlinie C2 sind die zum Abschalten der Dieseleinspritzpumpe zur Verfügung stehenden Kräfte ersichtlich größer als bei Verwendung von nur einer Druckfeder mit einer für die Antriebsschlupfregelung günstigen Kennlinie. Der angesprochene Unterschied ist deutlich erkennbar an dem bereits angesprochenen Divergieren der Geraden C1a, die die Verlängerung der Geraden C1 bildet, und der Geraden C2 der zweiten Druckfeder 12, die zusammen mit der Druckfeder 11 die erfindungsgemäße Federkombination bildet.To switch off the diesel injection pump, as already indicated, distances W of the piston rod are required which are greater than the distance A which the piston 9 can cover relative to the bushing 25. To switch off the diesel injection pump, the action on the piston 9 must be increased to such an extent that at least the force V2 of the compression spring 12 which is present as a result of pretensioning is overcome. It can thus be seen that only an excess of loading, which acts on the piston 9, generates those forces on the piston rod 10 which can be used to switch off the diesel injection pump. As a result of the design of the compression spring 12 with the characteristic curve C2, the forces available for switching off the diesel injection pump are evidently greater than when using only one compression spring with a characteristic curve which is favorable for the traction control system. The difference mentioned is clearly recognizable from the aforementioned divergence of the straight line C1a, which forms the extension of the straight line C1, and the straight line C2 of the second compression spring 12, which together with the compression spring 11 forms the spring combination according to the invention.

Ergänzend wird noch darauf hingewiesen, daß anstelle der angesprochenen Dieseleinspritzpumpe beispielsweise auch eine Benzineinspritzpumpe oder eine Vergaser in Kombination mit dem beschriebenen Stellzylinder verwendet werden kann. Der Stellzylinder 2 dient in diesem Fall ebenfalls dem Einregulieren eines Antriebsmoments eines Antriebsmotors eines Fahrzeugs auf eine solche Größe, daß ein optimaler Antriebsschlupf nicht oder nicht wesentlich überschritten wird. Infolgedessen ist bei ausreichender Spurhaltung des angetriebenen Fahrzeugs eine größtmögliche Beschleunigung erreichbar. Die Verwendung des erfindungsgemäßen Stellzylinder 2 in Verbindung mit Benzineinspritzpumpen oder Vergasern bietet sich an für leichte Fahrzeuge wie Kleinlastwagen, Kleinbusse und Personenkraftwagen. Weil in solchen Fahrzeugen gelegentlich anstelle einer Druckluftpumpe eine Hydraulikpumpe zur Verfügung steht, kann bedarfsweise der Durchmesser des Kolbens 9 kleiner gewählt werden als bei Beaufschlagung mittels Druckluft.In addition, it is pointed out that instead of the diesel injection pump mentioned, for example, a gasoline injection pump or a carburetor can also be used in combination with the actuating cylinder described. In this case, the actuating cylinder 2 also serves to regulate a drive torque of a drive motor of a vehicle to such a size that an optimal drive slip is not exceeded or is not significantly exceeded. As a result, the greatest possible acceleration can be achieved with sufficient tracking of the driven vehicle. The use of the actuating cylinder 2 according to the invention in connection with gasoline injection pumps or carburettors is suitable for light vehicles such as small trucks, minibuses and passenger cars. Because a hydraulic pump is occasionally available in such vehicles instead of a compressed air pump, the diameter of the piston 9 can, if necessary, be chosen to be smaller than when pressurized with compressed air.

Claims (4)

1. Actuating cylinder for altering fuel quantities fed to a vehicle engine, having a displaceable piston (9), which, inside the actuating cylinder (2), delimits an admission space, and having a spring arrangement which is installed under pre-stress and is arranged opposite to the admission space at the piston (9) and loads the latter in the direction of a starting position and comprises a first compression spring (11), which presses against the piston (9) and forms a speed governor spring, a stop (13), which is displaceable in the longitudinal direction of the actuating cylinder (2) and against which the first compression spring (11) is supported, a second compression spring (12), which on the one hand acts on this displaceable stop (13) and on the other hand is supported against a component (14) firmly connected to the actuating cylinder (2) and can be compressed to switch off the fuel supply, and a stop (20), which is rigidly arranged on the actuating cylinder (2) and against which the moveable stop (13) can be laid by means of the second compression spring (12), the second compression spring (12) being of less stiff design than the speed governor spring (11) and the second compression spring (12) being installed with a pre-stress (V2) which is greater than the greatest working force of the speed governor spring (11).
2. Actuating cylinder according to Claim 1, characterized in that the displaceable stop (13) is designed as an annular disc which surrounds a piston rod (10) with radial clearance.
3. Actuating cylinder according to Claim 2, characterized in that the actuating cylinder (2) has two bores (7, 8) in coaxial alignment and in that a diameter jump (20) situated between these bores forms a rigid stop for the axially moveable stop (13).
4. Actuating cylinder according to Claim 2, characterized in that at least one bush (25), which limits the compressibility of at least one of the compression springs (11, 12) is integrally formed on the axially displaceable stop (13) designed as an annular disc.
EP87901355A 1986-03-22 1987-02-26 Actuating cylinder Expired - Lifetime EP0298964B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3609838 1986-03-22
DE19863609838 DE3609838A1 (en) 1986-03-22 1986-03-22 CONTROL CYLINDER

Publications (2)

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EP0298964A1 EP0298964A1 (en) 1989-01-18
EP0298964B1 true EP0298964B1 (en) 1990-11-28

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EP87901355A Expired - Lifetime EP0298964B1 (en) 1986-03-22 1987-02-26 Actuating cylinder

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US (1) US4972819A (en)
EP (1) EP0298964B1 (en)
JP (1) JPH01501884A (en)
DE (2) DE3609838A1 (en)
WO (1) WO1987005660A1 (en)

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DE4126695A1 (en) * 1991-08-13 1993-02-18 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES
DE4126697A1 (en) * 1991-08-13 1993-02-18 Bosch Gmbh Robert FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINE
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DE4325417A1 (en) * 1993-07-29 1995-02-02 Hydraulik Ring Gmbh Actuating device for the throttle valve of a carburetor in automatic transmissions of motor vehicles
US6845314B2 (en) * 2002-12-12 2005-01-18 Mirenco, Inc. Method and apparatus for remote communication of vehicle combustion performance parameters
US10760598B2 (en) * 2017-09-01 2020-09-01 Enerpac Tool Group Corp. Hybrid spring for a hydraulic cylinder

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Also Published As

Publication number Publication date
US4972819A (en) 1990-11-27
EP0298964A1 (en) 1989-01-18
DE3766496D1 (en) 1991-01-10
DE3609838A1 (en) 1987-09-24
JPH01501884A (en) 1989-06-29
WO1987005660A1 (en) 1987-09-24

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