EP0029019B1 - Installation de régulation pour moteurs à combustion interne - Google Patents

Installation de régulation pour moteurs à combustion interne 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
Authority
EP
European Patent Office
Prior art keywords
force
servomotor
control
support
control system
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
Application number
EP80890122A
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German (de)
English (en)
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EP0029019A1 (fr
Inventor
Max Haubenhofer
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.)
Friedmann and Maier AG
Original Assignee
Friedmann and Maier AG
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Filing date
Publication date
Application filed by Friedmann and Maier AG filed Critical Friedmann and Maier AG
Publication of EP0029019A1 publication Critical patent/EP0029019A1/fr
Application granted granted Critical
Publication of EP0029019B1 publication Critical patent/EP0029019B1/fr
Expired 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
    • 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.

Claims (4)

1. Installation de réglage pour moteurs à combustion interne à injection de carburant, comportant un régulateur centrifuge mécanique (2, 38) pour le réglage de la quantité injectée où le mouvement élastique (6, 37) recevant la force, fonction de la vitesse de rotation, des masselottes (1, 40) possède une butée (7, 48) mobile axialement, dont la force de poussée peut actionner un dispositif de commande d'un servo-moteur (14', 39) destiné à un dispositif auxiliaire, caractérisée en ce que la butée (7, 48) est en liaison avec un bras d'un levier à deux bras (12, 52) monté fixe sur le carter dont l'autre bras agit sur un dispositif de commande qui est en communication avec le servo-moteur (14', 39) pour le retour en arrière, par l'intermédiaire d'au moins un ressort (23, 65), et que la mobilité axiale de la butée (7, 48) est limitée par des butées (15') ou par les contacts de commutation eux-mêmes, agissant comme butées, du dispositif de commande (55, 56, 57), à une course très courte.
2. Installation de réglage pour moteurs à combustion interne à injection de carburant comportant un régulateur centrifuge (79, 104) mécanique pour la régulation de la quantité à injecter où le mouvement élastique (87, 89) recevant la force, fonction de la vitesse de rotation des masselottes (82), possède une butée (88) dont la force de poussée peut actionner un dispositif de commande d'un servomoteur (94') destiné à un dispositif auxiliaire, caractérisé en ce que le servo- moteur (94') comporte un transducteur de force (92), qui est disposé entre une butée (88) et un carter (93) de l'installation de réglage, et forme ainsi un arrêt pour la butée (88), et que le transducteur de force (92) est relié avec une unité de commande électronique (94) du dispositif de commande et actionne ce dernier au moyen d'un signal électrique qui dépend de la force exercée par la butée (88).
3. Installation de réglage suivant la revendication 1, caractérisée en ce qu'avec un servo- moteur hydraulique (14') le dispositif de commande comporte un tiroir de commande (14) d'une conduite de fluide sous pression (17) qui est actionné, d'une part, par un levier à deux bras et sur lequel agissent, d'autre part, des ressorts (23), qui produisent une composante de forces dans le sens de l'axe du tiroir de commande (14) et absorbent la force transmise sur ce tiroir (14) de commande et s'appuient sur le piston moteur (18) du servo-moteur pour le retour en arrière de la déviation du tiroir de commande (14).
4. Installation de réglage suivant la revendication 1, caractérisée en ce que, si le servo-moteur est mû électriquement (39), le levier à deux bras (52) est sollicité par un ressort (65) vers le côté qui est à l'opposé de la butée (48), et porte un chapeau de commutation (55) qui relie, au moyen de contacts de commutation (56, 57), un conducteur (58) électrique d'alimentation avec des raccords d'un moteur électrique (59) du servo-moteur (39) et pendant que, pour le retour en arrière de la déviation du levier à deux bras (52), il s'appuie, à cette extrémité du ressort (65) sur un écrou (62) mobile axialement sous l'action du moteur électrique (59) et bloqué contre toute rotation.
EP80890122A 1979-10-16 1980-10-15 Installation de régulation pour moteurs à combustion interne Expired EP0029019B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT6738/79 1979-10-16
AT0673879A AT381368B (de) 1979-10-16 1979-10-16 Regelanlage fuer brennkraftmaschinen

Publications (2)

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

Family

ID=3589283

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80890122A Expired EP0029019B1 (fr) 1979-10-16 1980-10-15 Installation de régulation pour moteurs à combustion interne

Country Status (9)

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

Families Citing this family (9)

* Cited by examiner, † Cited by third party
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
JPS5952143U (ja) * 1982-09-30 1984-04-05 日野自動車株式会社 燃料の供給量制御装置
JPS5960038A (ja) * 1982-09-30 1984-04-05 Hino Motors Ltd 燃料の供給量制御装置
JPS5982539A (ja) * 1982-10-29 1984-05-12 Hino Motors Ltd 燃料の供給量制御装置
DE3430797A1 (de) * 1984-08-22 1986-03-06 Robert Bosch Gmbh, 7000 Stuttgart Drehzahlregler fuer kraftstoffeinspritzpumpen
DE4115301A1 (de) * 1991-05-10 1992-11-12 Bosch Gmbh Robert Steuerkapsel fuer einen fliehkraftdrehzahlregler
DE4129837C2 (de) * 1991-09-07 2002-06-27 Bosch Gmbh Robert Drehzahlregler für Kraftstoffeinspritzpumpen von Brennkraftmaschinen
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 (ko) * 2017-11-28 2022-11-11 현대자동차주식회사 차량용 자동 변속장치

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH171817A (de) * 1932-12-06 1934-09-15 Bosch Robert Ag Einspritzpumpe für Brennkraftmaschinen.
CH153911A (de) * 1935-07-08 1932-04-15 Sulzer Ag Mit elektrischem Stromerzeuger gekuppelte Brennkraftmaschine auf Fahrzeugen.
FR836577A (fr) * 1938-04-13 1939-01-20 Dispositif pour régler le débit d'une pompe d'injection, particulièrement applicable aux moteurs d'automobiles
FR1052850A (fr) * 1951-02-07 1954-01-28 Davey Stabilisateur pour systèmes automatiques de commande et de réglage, notamment de moteurs
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 (de) * 1976-11-02 1986-07-10 Robert Bosch Gmbh, 7000 Stuttgart Steuereinrichtung für eine Kraftstoffeinspritzpumpe eines Dieselmotors
US4109628A (en) * 1976-11-08 1978-08-29 Caterpillar Tractor Co. Adjustable regulation governor

Also Published As

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

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