EP0167697A1 - Mécanisme d'avance de l'injection pour des pompes à injection de moteurs à combustion - Google Patents

Mécanisme d'avance de l'injection pour des pompes à injection de moteurs à combustion Download PDF

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Publication number
EP0167697A1
EP0167697A1 EP85100357A EP85100357A EP0167697A1 EP 0167697 A1 EP0167697 A1 EP 0167697A1 EP 85100357 A EP85100357 A EP 85100357A EP 85100357 A EP85100357 A EP 85100357A EP 0167697 A1 EP0167697 A1 EP 0167697A1
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EP
European Patent Office
Prior art keywords
injection timing
timing adjuster
adjuster according
secondary part
pressure
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.)
Granted
Application number
EP85100357A
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German (de)
English (en)
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EP0167697B1 (fr
Inventor
Albert Nolte
Joachim Altdorf
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
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Publication of EP0167697A1 publication Critical patent/EP0167697A1/fr
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Publication of EP0167697B1 publication Critical patent/EP0167697B1/fr
Anticipated expiration legal-status Critical
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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
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • 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
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic

Definitions

  • the invention relates to a fuel injection device for in particular air-compressing, self-igniting internal combustion engines with an injection timing adjuster arranged on the drive side, consisting of a drive device, the primary part, an A b drive device, the secondary part connected to the injection pump camshaft, and a primary and Secondary part angularly movably connecting transmission element, which provides the torque transmission with a variable angular position of the primary to the secondary part controlled by the motor parameters.
  • Such a generic fuel injection device with injection timing adjuster is known and has long been used for. B. built by the company Bosch (Bosch technical information injection equipment for diesel engines injection pumps PE and PS).
  • Bosch Bosch technical information injection equipment for diesel engines injection pumps PE and PS.
  • an injection timing adjuster with flyweights is described.
  • Such injection timing adjusters should only change the injection timing depending on the speed of the internal combustion engine or the speed of the injection pump camshaft.
  • the injection timing adjuster is placed on the end of the injection pump camshaft and is driven via its outer housing.
  • the primary part is therefore the driven housing, while the secondary part is embodied by the inner hub and a so-called adjusting disk.
  • Two flyweights which are supported by springs on the adjusting disc, form the transmission element.
  • a torque initiated to drive the injection pump is passed on from the housing via the centrifugal weights attached to it and via the springs to the adjusting disk and thus finally to the hub.
  • the centrifugal weights move outwards and rotate the adjusting disk against the housing against the force of the springs via rollers.
  • a disadvantage of this injection timing adjuster has turned out that the injection timing is not clearly dependent on the speed of the injection pump camshaft.
  • the attacking drive torques change the position of the centrifugal weights and thus the adjustment of the injection timing via the position of the primary to the secondary part. The angle adjustment is therefore still dependent on the direction and size of the drive torques.
  • an injection timing adjuster which can be influenced by several operating parameters of the internal combustion engine. So not only a clear speed dependency of the adjustment is required, but z. B. also a load dependency of the start of delivery or a change in the injection timing when cold starting.
  • Modern internal combustion engines are often equipped with an electrical control device, for example control electronics, which is able to record a large number of these operating parameters and to control all auxiliary units.
  • a new type of injection timing adjuster should therefore be controllable in a simple manner by control electronics.
  • the object of the present invention is therefore to propose a separate injection timing, the V orgabeluta the injection timing of an electrical control device in a simple manner without affecting or from the attacking drive torque in a real rotation angle of the injection pump cam shaft relative to the drive part, which in the case considered here, in Bottom line is the crankshaft of the internal combustion engine.
  • a controlling electrical control device namely control electronics
  • the control electronics receive at least the actual value of the speed of the primary part and is able to calculate a target value of the angle of rotation position of the driving part to the driven part of the injection timing adjuster.
  • the embodiment of the invention according to claim 2 provides that the angle of rotation position of the secondary to the primary part is detected by two electrical pulse generators and that these pulses are used by the control electronics for the angle of rotation setting size.
  • This feature leads to a feedback control loop, wherein the R egelelektronik now is able to constantly compare the setpoint value with the actual value of the rotational angular position.
  • Such a feedback of the controlled variable which is not absolutely necessary for all conceivable types of regulation, improves the quality of the controlled variable in any case.
  • An injection timing adjuster according to the invention has the further advantage that it can in principle be accommodated somewhere in a suitable location in the engine compartment, separately from the injection pump. Only requirement is the form-fitting rehmomenten undergraduatetragung D between the secondary part and the injection pump cam shaft.
  • the direct arrangement on the injection pump camshaft, or the design of the end of the injection pump camshaft as a secondary part, is particularly simple and therefore also inexpensive.
  • Claims 12 to 18 describe a possible type of displacement of the primary part on the secondary part with an electric motor as the drive.
  • the shift is essentially achieved by a threaded sleeve or a threaded spindle, which is provided with two opposing threads.
  • This sleeve or threaded spindle is screwed with one thread into a connecting part which is firmly connected to the primary part, while the other thread is in operative connection with the secondary part.
  • this threaded spindle or sleeve even driven by the primary part, drives the electric motor in a rotationally rigid manner.
  • the electric motor is controlled by the control electronics in such a way that it rotates faster than the primary part, the primary part on the secondary part becomes axially opposite due to the two Thread shifted on the sleeve or the threaded spindle.
  • the electric motor runs slower and the axial displacement is exactly the opposite.
  • the D rehmomenten undergraduatetragung from the primary section to the electric motor is mainly ensured only by the friction in the threads.
  • the armature of the electric motor must therefore have a sufficiently small mass to be able to follow dynamic speed changes.
  • the electric motor can not act as a generator, because the D resulting deer moment surely overcome the friction in the threads and a relative rotation of the primary part relative to the armature of the electric motor, that is a change in the injection timing results.
  • the control electronics detect the current angle of rotation position of the secondary part to the primary part according to claim 2 and controls the electric motor according to the speed of the primary part.
  • Claims 12, 13 and 19 to 24 describe a further embodiment of the invention, in which an axial displacement of the primary part on the secondary part by a threaded spindle, which can be braked by an electromagnetic brake in two ways, namely once directly and once via a reversing gear , is reached.
  • the basic structure is fundamental the same as in the first embodiment of this invention.
  • the threaded spindle is now rotationally rigidly connected to two rotors of an electromagnetic brake, the threaded spindle and thus also the rotors of the electromagnetic brake rotating at the same speed as the primary part due to the friction in the threads.
  • the electrical control of the electromagnetic brake can be made particularly simple. Because both rotor brakes basically only need the electrical switching states "on" or w off w . Although a more detailed control of the braking effect according to their size can be carried out without adverse influence, but it is unnecessary for the normal case of application in an advantageous manner, since the V réellellvier, that is, the rotation angle, is fed back through the pulse generator.
  • a third and last embodiment of the invention according to claims 25 to 39 provides for the displacement of the primary part on the secondary part by means of a pressure piston which is acted upon by a pressure medium.
  • the pressure piston is firmly connected to the primary part and forms in the Secondary section two pressure rooms, the outflows of which are controlled by a hydraulic control bolt.
  • the hydraulic control pin is controlled directly and without feedback by the control electronics.
  • the pressure medium which can in particular be engine oil or fuel of the internal combustion engine, is supplied to the two pressure chambers via two check valves.
  • a hydraulic transmission element is particularly useful in connection with the drive of an injection pump.
  • the injection pump strong alternating torques, btriebsteil generate an A rt pulsating movement between the drive and the A Einspritzzeithuiverstellers arise throughout the drive train during operation. If the drive part (primary part) is now to be rotated relative to the output part (secondary part), it is not necessary, if these alternating torques are used appropriately, to adjust against the output torque of the injection pump, i.e. if a hydraulic system is used, it is sufficient to provide a comparative one low hydraulic fluid pressure to carry out the adjustment.
  • the injection timing adjuster does not take the force required for the adjustment from the hydraulics, but advantageously adjusts itself self-energizing with the energy of the alternating torques.
  • This makes an expensive high-pressure hydraulic pump superfluous and in particular suggests the use of the pressurized engine oil of the internal combustion engine as hydraulic pressure medium.
  • all known hydraulic fluids are possible if they are brought to a low hydraulic pressure by a separate pump, in comparison to the usual hydraulic hydraulic values.
  • the control electronics determine the axial position of the pressure piston, and thus also the axial position of the primary part on the secondary part, by opening the discharge opening of the pressure chambers via the hydraulic control pin.
  • An axial displacement of the hydraulic control pin always follows the axial displacement of the primary part and thus the adjustment of the injection timing.
  • a s displacement of the hydraulic control bolt advantageously corresponds exactly to the shift of the primary part, a return of the crizgröBe, namely the V er loftwinkels the secondary part to the primary part is not necessary, but can also positive influences have on the quality of the control variable.
  • FIG. 1 the individual components of an injection timing adjuster according to the invention are shown schematically, arrows indicating the operative connection between them.
  • the injection timing adjuster is arranged directly on the injection pump camshaft 5 with a secondary part 4.
  • the hub-shaped secondary part 4 is provided with a ring gear-like primary part 3, which is angularly movable and axially displaceable with the secondary part 4 in engagement with a helical toothing 9.
  • the primary part 3 can be driven by a driving gear 49 via its external toothing and in turn drives the injection pump camshaft 5 via the secondary part 4.
  • a toothed disk 8 is in turn firmly connected to the secondary part 4.
  • a mark is made both on the ring gear of the primary part 3 and on the toothed disk 8.
  • Two electrical pulse generators 6 and 7 register each passage of the markings and in each case send an electrical pulse to control electronics 1. These pulses give control electronics 1 both information about the speed of the injection pump camshaft 5 and information about the exact instantaneous angle of rotation of the secondary to the primary part of the injection timing adjuster.
  • the two further arrows leading into the control electronics 1 are intended to indicate further operating parameters of the internal combustion engine, which have been converted to electrical quantities by suitable sensors and / or sensors.
  • the electronic control unit 1 processes all incoming sizes to an electrical nominal value of the twist angle of the secondary to the primary part, ie inspritzzeitfounds to a target value of the E. This electrical signal must be converted into a displacement path of a connecting part 10 with the aid of a converter 2.
  • a hydraulic control pin has to be displaced axially, for which purpose the electrical signal from the control electronics 1 is converted into a feedback-free displacement path, which actuates the hydraulic control pin largely without force, using a known electrical auxiliary device.
  • the axial displacement of the connecting part 10 leads through the helical teeth 9 to a change in the rotational angle position of the secondary to the primary part, whereby the control loop of the injection point adjuster is closed via the feedback at the pulse generators 6 and 7.
  • the secondary part is the Einspritzpumpnenockenwelle 5 and a nut 19 fixedly connected here to a cone 16, a threaded pin 17 with the E inspritzpumpennockenwelle 5 itself.
  • the injection pump is driven from the outside via the primary part 3, which is arranged in the form of a ring gear on the secondary part 4 in the axial direction, via the helical toothing 9 and via the secondary part 4.
  • a toothed disc 8 is furthermore fixed to the secondary part in a rotationally rigid manner.
  • the pulse generators 6 and 7 mentioned are arranged in a stationary manner in a housing part and emit a pulse to the control electronics 1 per revolution of the primary part 3 and the secondary part 4 exactly at the point in time at which the marking passes them. Furthermore, the primary part is still screwed to a connecting part 10.
  • a threaded pin 20 of the nut 19 is screwed into the internal thread of the sleeve 13, the armature 15 of an electric motor 12 is arranged in a stationary manner on the sleeve 13 and the associated stator 14 is furthermore firmly connected to a housing 11.
  • the rotational angle position of the secondary part 4 relative to the primary part 3 is not fixed in any axial displacement of the primary part 3 onto the secondary part 4.
  • the primary part 3 drives the armature 15 of the electric motor 12 via the connecting part 10.
  • the inertia of the armature 15 must be chosen so that the friction in the thread of the sleeve 13 is able to transmit the torque safely.
  • the electric motor must not act as a generator, since in this case the friction would certainly not be large enough and the armature 15 would rotate relative to the primary part 3.
  • the control electronics 1 knows from the pulse generators 6 and 7 the angular position of the secondary part 4 to the primary part. If the control electronics 1 now specifies a change in the rotational angle position, the stator 14 of the electric motor 12 is controlled accordingly.
  • the armature 15 then begins to rotate faster or slower than the primary part 3. Due to the two opposite threads of the sleeve 13, the sleeve 13 and the connecting part 10, and consequently also the primary part 3, are now displaced in the axial direction on the secondary part 4. This axial displacement of the primary part 3 on the secondary part 4 leads to helical teeth 9 a change in the angular position of the secondary part 4 to the primary part 3, which in turn is reported back to the control electronics 1 by the pulse generators 6 and 7.
  • FIG. 3 shows an embodiment of the injection timing adjuster with the same mode of operation as in FIG. 2.
  • the difference lies in the use of a commercially available electric motor 12 which is firmly connected to the housing 11. Since the sleeve 13 moves in the axial direction, the shaft 21 of the electric motor 12 is mounted in the inner bore of the sleeve 13 in a rotationally rigid but axially displaceable manner.
  • an embodiment with a continuous threaded spindle 17 of the injection pump camshaft 5 is shown.
  • no separate threaded pin 20 of the nut 19 is provided, but instead a threaded pin 17 passing through the nut 19.
  • the operation of this injection timing adjuster is the same as that of the one shown in FIG. 2.
  • FIG. 4 shows an injection timing adjuster with an electromagnetic brake and a reversing gear.
  • the arrangement of the primary part, secondary part and the connecting part 10, as well as the pulse generator 6 and 7 is the same as in the previous exemplary embodiments.
  • the reversing gear consists of a gear 27 arranged on the threaded spindle 24, a planet-like gear 25, which is rotatably mounted in its position on the connecting part 26 by a pin 26.
  • An internal ring gear 28 is arranged concentrically with the inner gear 27.
  • the gear 25 is both with the gear 27 as also engages with the ring gear 28 and thus achieves the reversal of the direction of rotation of the ring gear 28 with respect to the threaded spindle 24.
  • the ring gear 28 is part of one of the two rotors 23 of the electromagnetic brake 22.
  • the injection timing adjuster is driven from the outside via the primary part 3 and in turn drives the secondary part 4 and thus the injection pump camshaft 5 via the helical teeth 9.
  • the primary part 3 With the primary part 3, the connecting part 10, the threaded spindle 24 and both rotors 23 rotate, but these each in a different direction.
  • the transmission of the torque to the two rotors 23 is again ensured by the friction in the threads of the threaded spindle.
  • the electronic control unit 1 recognizes the rotational angle position of the secondary part 4 relative to the primary part 3 by the two pulse generators 6 and 7. If the rotational angle position of the secondary part 4 relative to the primary part 3 is now to be changed, a rotor 23 of the electromagnetic brake is activated and braked.
  • the threaded spindle 24 rotates relative to the primary and secondary part, whereby the two opposite threads of the threaded spindle 24 achieve an axial displacement of the connecting part 10 and thus of the primary part 3 on the secondary part 4.
  • An adjustment in the other direction can be implemented in a simple manner by activating the other rotor 23 of the electromagnetic brake 22, which acts in the other adjustment direction because of the reversing gear.
  • the size of the aixalen shift corresponds to the change in the rotational angular position of the two Weche I mpulsgebern 6 and 7 back to the control electronics is confirmed.
  • the injection time track described in FIGS. 2 to 4 fulfill their function irrespective of whether they are equipped with a sleeve 13 or a threaded spindle 24.
  • the design of the secondary part as the end of the injection pump camshaft 5 and a resulting threaded spindle 17 is also only one embodiment and can therefore be used in all three of the exemplary embodiments mentioned.
  • the adjustment of the rotational angle position of the secondary part 4 to the primary part 3 is provided with a hydraulic system.
  • the primary part 3 is arranged axially displaceably on the secondary part 4 with helical teeth 9, as in the previous figures.
  • the secondary part 4 is provided with a ring gear 8, two pulse generators 6 and 7 forwarding the angle of rotation position of the secondary part 4 to the primary part 3 to separate control electronics 1 by means of electrical pulses.
  • a pressure piston 29 is arranged centrally in the inner bore. This pressure piston 29 forms, with the end of the injection pump camshaft 5 and an annular extension of the secondary part 4, two pressure chambers 36 and 37.
  • the pressure piston 29 is designed as an ordinary differential piston 48 with a piston rod 39.
  • the pressure piston 29 is led out of the secondary part 4 on the cylindrical sealing surface 38 with its piston rod 39 in a pressure-tight manner and is connected in a stationary manner to the connecting part 10 by screwing a nut 19 in a central bore 18 of the same.
  • an axial displacement of the pressure piston 29 leads to the same displacement of the primary part 3 on the secondary part 4.
  • a hydraulic control pin 31 is provided in the pressure piston 29, in a bore 30, which is arranged axially parallel in its center.
  • This hydraulic control pin has a drain hole 32, two control edges 33 and two connecting drain holes 47.
  • the two pressure chambers 36, 37 are connected via holes 34 to the hole 30 of the hydraulic control bolt 31.
  • the two control edges 33 of the hydraulic control bolt 31 control the outflow of the two pressure chambers 36 and 37 via the connecting bores 34.
  • the hydraulic medium is through hollow bores 41 in the housing 11 via a bearing 42 of the injection pump camshaft 5, an annular channel 43 and further bores 44 in the injection pump camshaft 5 fed to the two pressure chambers 36 and 37 via two check valves 45. Furthermore, the pressure piston 29 is still acted upon by a spring force in the axial direction.
  • Such a hydraulic injection timing adjuster is based on the alternating torques acting on the injection pump camshaft.
  • strong alternating torques are generated in the entire drive train of the injection pump, which generate a kind of pulsating movement between the drive and output parts of the injection timing adjuster.
  • the driving part (primary part) relative to the driven part (secondary part) are rotated, it is, if one exploits this alternating torques suitable not necessary, contrary to the A of the injection pump ntriebsmomenten to adjust, ie when using a hydraulic sufficient to provide a comparatively low Hydraulic medium pressure to carry out the adjustment.
  • the injection timing adjuster does not take the force required for the adjustment from the hydraulics, but advantageously adjusts itself self-energizing with the energy of the alternating torques.
  • the primary part 3 is driven from the outside and in turn drives the secondary part 4 via the helical teeth 9.
  • the connecting part 10 and the pressure piston 29 rotate accordingly.
  • the hydraulic control pin closes with its control edges 33 all connecting bores 34 to the two pressure chambers 36 and 37.
  • the pressure piston 29 is thus in its axial position relative to the Secondary part fixed. Is now to the injection timing are changed, the Drehwinkelstellüng of the secondary part 4 that is the primary part 3, so is the R egelelektronik 1 is an axial shift of the hydraulic control bolt 31 in front.
  • the electrical pulses or signals from the control electronics 1 are converted by a known converter into a displacement path which is proportional to the electrical signals and is feedback-free. In particular, no greater force needs to be applied.
  • a control edge 33 releases the connecting bores 34 to one of the pressure spaces, for example 37.
  • the hydraulic pressure medium can thus flow out of the secondary part out of the secondary part via the connection bores 34 and the drain bore 37 through the further drain bore 32 in the hydraulic control bolt 31.
  • a displacement of the plunger 29 in direction D this jerk space 37 can thus take place and is driven by the alternating moments executed.
  • the other pressure chamber 36 fills up Check valve 45 with hydraulic fluid on.
  • the pressure piston 29 cannot move in the direction of the pressure chamber 36, since the check valve 45 only allows hydraulic fluid to flow in and the connecting bore 34 of the pressure ram 36 is closed by the hydraulic control pin 31. This works until the pressure piston has slid over the control edges 33, ie the connecting bores 34 of the pressure chamber 37 are closed again. A renewed stable axial position of the pressure piston is thus achieved, which can no longer move. Due to the axial displacement of the pressure piston, the primary part 3 has also migrated in the same axial direction on the secondary part 4 and has accordingly changed the angle of rotation position of the secondary part 4 relative to the primary part 3.
  • a feedback of the angle of rotation position of the secondary part 4 to the primary part 3 via electrical pulse generators 6 and 7, as in the previous exemplary embodiments, can easily be omitted here, since the axial position of the hydraulic control bolt 31 clearly specifies the size of the change in the angle of rotation position. In some cases, it may be in the I nter- eat the control quality prove advantageous also a feedback of the angular position make.
  • the hydraulic control pin 31 To change the injection timing in the other direction, the hydraulic control pin 31 must be shifted in the opposite direction. The process then takes place accordingly on the second control edge 33 of the hydraulic control pin 31.
  • the pressure piston 29 is still acted upon by a spring force of a spring 35.
  • This spring force is not necessary for the operation of the injection timing adjuster, but it ensures that a well-defined value of the injection timing is reached when the internal combustion engines are switched on.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
EP85100357A 1984-05-17 1985-01-15 Mécanisme d'avance de l'injection pour des pompes à injection de moteurs à combustion Expired - Lifetime EP0167697B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3418321 1984-05-17
DE19843418321 DE3418321A1 (de) 1984-05-17 1984-05-17 Einspritzzeitpunktversteller einer einspritzpumpe fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0167697A1 true EP0167697A1 (fr) 1986-01-15
EP0167697B1 EP0167697B1 (fr) 1990-01-24

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EP85100357A Expired - Lifetime EP0167697B1 (fr) 1984-05-17 1985-01-15 Mécanisme d'avance de l'injection pour des pompes à injection de moteurs à combustion

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EP (1) EP0167697B1 (fr)
JP (1) JPS60249629A (fr)
DE (2) DE3418321A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2636108A1 (fr) * 1988-09-07 1990-03-09 Daimler Benz Ag Dispositif pour regler la position angulaire relative de deux arbres relies selon une liaison motrice
CN113738548A (zh) * 2021-07-27 2021-12-03 东风汽车集团股份有限公司 进气相位传感器失效后的高压油轨压力控制方法及系统

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DE3929620A1 (de) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Verstellanordnung fuer eine vorrichtung zur drehwinkelverstellung einer welle relativ zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine

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US3401572A (en) * 1966-09-12 1968-09-17 Caterpillar Tractor Co Compact speed sensitive timing device for internal combustion engines
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EP0122399A1 (fr) * 1983-04-15 1984-10-24 Klöckner-Humboldt-Deutz Aktiengesellschaft Mécanisme d'avance à injection pour des pompes à injection de moteurs alternatifs à combustion interne

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Publication number Priority date Publication date Assignee Title
FR895657A (fr) * 1942-06-17 1945-01-31 Heberlein & Co Ag Dispositif modifiant le calage entre un arbre menant et un arbre mené
US3401572A (en) * 1966-09-12 1968-09-17 Caterpillar Tractor Co Compact speed sensitive timing device for internal combustion engines
GB1242659A (en) * 1968-09-28 1971-08-11 Fiat Spa Fuel injection pump for internal combustion engines
DE2525746A1 (de) * 1974-06-10 1976-01-02 Nissan Motor Selbsteinstellbare nockenwellen- antriebsvorrichtung, insbesondere bei kraftfahrzeug-verbrennungsmotoren
GB2019613A (en) * 1978-04-22 1979-10-31 Bosch Gmbh Robert Improvements in fuel injection pumps
GB2029934A (en) * 1978-05-30 1980-03-26 Sanwa Seiki Mfg Co Ltd Injection timing control system for fuel-injection pump for engine
GB2123493A (en) * 1982-07-15 1984-02-01 Lucas Ind Plc Fuel injection pumping apparatus
EP0122399A1 (fr) * 1983-04-15 1984-10-24 Klöckner-Humboldt-Deutz Aktiengesellschaft Mécanisme d'avance à injection pour des pompes à injection de moteurs alternatifs à combustion interne

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PATENTS ABSTRACTS OF JAPAN, Band 8, Nr. 136, (M-304) (1573), 23. Juni 1984; & JP,A,59 037 232 (YANMAR DIESEL K.K.) 29.02.1984, zusammenfassung. *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2636108A1 (fr) * 1988-09-07 1990-03-09 Daimler Benz Ag Dispositif pour regler la position angulaire relative de deux arbres relies selon une liaison motrice
CN113738548A (zh) * 2021-07-27 2021-12-03 东风汽车集团股份有限公司 进气相位传感器失效后的高压油轨压力控制方法及系统
CN113738548B (zh) * 2021-07-27 2022-06-03 东风汽车集团股份有限公司 进气相位传感器失效后的高压油轨压力控制方法及系统

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EP0167697B1 (fr) 1990-01-24
DE3418321A1 (de) 1986-04-24
DE3575588D1 (de) 1990-03-01
JPS60249629A (ja) 1985-12-10

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