EP0298964B1 - Cylindre d'actionnement - Google Patents

Cylindre d'actionnement 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
Authority
EP
European Patent Office
Prior art keywords
actuating cylinder
piston
stop
compression spring
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP87901355A
Other languages
German (de)
English (en)
Other versions
EP0298964A1 (fr
Inventor
Ortwin Engfer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0298964A1 publication Critical patent/EP0298964A1/fr
Application granted granted Critical
Publication of EP0298964B1 publication Critical patent/EP0298964B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
    • F02D17/04—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling rendering engines inoperative or idling, e.g. caused by abnormal conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/06—Arrangements 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
    • F02D11/08—Arrangements 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)

Abstract

Le cylindre d'actionnement (2) est un composant d'un système de limitation de la perte par glissement dans une transmission et sert également à arrêter un système d'alimentation en carburant (28) qui peut être commandé par le système de limitation de la perte par glissement de la transmission et peut par exemple être une pompe d'injection diesel d'un moteur de véhicule. Le cylindre d'actionnement (2) est pourvu d'un piston pressurisable (9), une bielle de piston (10), de deux ressorts de compression (11, 12) incorporés à l'état préchargé et, entre ceux-ci, une butée déplaçable axialement (13). Le ressort de plus forte précharge (12) comprime la butée déplaçable axialement (13) contre une butée (20) qui est reliée de manière rigide au cylindre d'actionnement (2). Le ressort de compression de précharge la moins forte (11) est comprimé contre la butée déplaçable axialement (13) et est comprimé contre le piston (9). Ce ressort de compression (11) est conçu relativement raide et, pendant le fonctionnement du système de limitation de la perte par glissement de la transmission, il est plus ou moins fortement comprimé par l'actionnement du piston (9). Pour couper totalement le système d'alimentation en carburant, le piston (9) est actionné plus vigoureusement de sorte que le second ressort de compression à forte précharge (12), qui est d'une rigidité moindre que celle du premier ressort de compression (11), est également comprimé. L'agencement des deux ressorts de compression (11, 12) assure un réglage précis du système de limitation de la perte par glissement de la transmission et simplifie la coupure du système d'alimentation en carburant.

Claims (4)

1. Cylindre d'actionnement pour modifier les quantités de carburant alimentant un moteur de véhicule, comportant un piston (9) coulissant qui délimite une chambre de sollicitation à l'intérieur de cylindre d'actionnement (2) et un dispositif à ressort monté avec précontrainte et qui est prévu en regard du piston (9) par rapport à la chambre de sollicitation, et charge ce piston vers la position de sortie ainsi qu'un premier ressort de compression (11) poussant contre le piston (9), qui forme un ressort de régulation de vitesse de rotation, une butée (13) coulissant dan la direction longitudinale du cylindre d'actionnement (2) et contre laquelle s'appuie le premier ressort de compression (11), un second ressort de compression (12) qui attaque à son tour une butée (13) coulissante sur celui-ci et d'autre part s'appuie contre une pièce (14) solidaire du cylindre d'actionnement (2), ressort qui peut être comprimé pour couper l'alimentation en carburant ainsi qu'une butée (20) rigide sur le cylindre d'actionnement (2), qui peut s'appliquer contre la butée mobile (13) par l'intermédiaire d'un second ressort de compression (12), le second ressort de compression (12) étant moins rigide que le ressort de régulation de vitesse de rotation (11) et le second ressort de compression (12) est monté avec une précontrainte (V2) supérieure à la plus grande force utile du ressort de régulation de vitesse de rotation (11).
2. Cylindre d'actionnement selon la revendication 1, caractérisé en ce que la butée coulissante (13) est un disque annulaire qui entoure radialement et avec du jeu la tige de piston (10).
3. Cylindre d'actionnement selon la revendication 2, caractérisé en ce qu'il (2) comporte deux alésages (7, 8) coaxiaux séparés par un saut de diamètre (20) format une butée (13) mobile axialement.
4. Cylindre d'actionnement selon la revendication 2, caractérisé en ce que la butée (13) coulissante axialement, en forme de disque annulaire porte au moins un manchon (25) qui délimite la possibilité de compression d'au moins l'un des ressorts de compression (11, 12).
EP87901355A 1986-03-22 1987-02-26 Cylindre d'actionnement Expired - Lifetime EP0298964B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3609838 1986-03-22
DE19863609838 DE3609838A1 (de) 1986-03-22 1986-03-22 Stellzylinder

Publications (2)

Publication Number Publication Date
EP0298964A1 EP0298964A1 (fr) 1989-01-18
EP0298964B1 true EP0298964B1 (fr) 1990-11-28

Family

ID=6297111

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87901355A Expired - Lifetime EP0298964B1 (fr) 1986-03-22 1987-02-26 Cylindre d'actionnement

Country Status (5)

Country Link
US (1) US4972819A (fr)
EP (1) EP0298964B1 (fr)
JP (1) JPH01501884A (fr)
DE (2) DE3609838A1 (fr)
WO (1) WO1987005660A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0415128A (ja) * 1990-05-07 1992-01-20 Hino Motors Ltd 差動制限装置および動力装置
US5315977A (en) * 1991-04-22 1994-05-31 Dwayne Fosseen Fuel limiting method and apparatus for an internal combustion vehicle
DE4126695A1 (de) * 1991-08-13 1993-02-18 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4126697A1 (de) * 1991-08-13 1993-02-18 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschine
US5293854A (en) * 1993-05-14 1994-03-15 Deere & Company Injection pump throttle dashpot for transient smoke control
DE4325417A1 (de) * 1993-07-29 1995-02-02 Hydraulik Ring Gmbh Betätigungseinrichtung für die Drosselklappe eines Vergasers bei automatisch schaltenden Getrieben von Kraftfahrzeugen
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

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB508805A (en) * 1938-01-05 1939-07-05 Westinghouse Brake & Signal Improvements relating to fuel supply controlling cylinders for internal combustion engines
US2897809A (en) * 1956-07-31 1959-08-04 Daimler Benz Ag Control system for an internal combustion engine
US2914056A (en) * 1958-08-22 1959-11-24 Studebaker Packard Corp Smoke control mechanism for diesel engines
SE360902B (fr) * 1969-04-08 1973-10-08 Bolider Munktell Ab
DE2322025C2 (de) * 1973-05-02 1975-06-05 Daimler-Benz Ag, 7000 Stuttgart Verstelleinrichtung an einem mit Motorbremse ausgerüsteten Kraftfahrzeug
DE2454061A1 (de) * 1973-11-16 1975-06-26 Allard Verfahren und vorrichtung zum regeln der beschleunigung von motoren
US4262642A (en) * 1977-11-16 1981-04-21 Anatoly Sverdlin Device for reducing fuel consumption in internal combustion engines
DE3021116A1 (de) * 1980-06-04 1981-12-10 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zur vortriebsregelung bei einem kraftfahrzeug mit blockierschutzsystem
DE3122666C2 (de) * 1981-06-06 1983-05-26 Daimler-Benz Ag, 7000 Stuttgart Steuereinrichtung zur zusätzlichen Beeinflussung eines von einem Fahrpedal betätigten Kraftstoffzumeßorgans von Kraftfahrzeug-Brennkraftmaschinen
DE3125127A1 (de) * 1981-06-26 1984-08-30 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Arbeitszylinder
DE3313632C2 (de) * 1983-04-15 1986-01-30 Daimler-Benz Ag, 7000 Stuttgart Leerlauf-Enddrehzahlregler für Einspritzpumpen an Brennkraftmaschinen
SE454905B (sv) * 1984-11-07 1988-06-06 Akermans Verkstad Ab Anordning for varvtalsinstellning av en motor i en arbetsmaskin
DE3713288A1 (de) * 1986-07-25 1988-02-04 Man Nutzfahrzeuge Gmbh Steuereinrichtung fuer die verstellung des einspritzzeitpunktes und/oder der foerdermenge einer kraftstoffeinspritzpumpe

Also Published As

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

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