EP0373383B1 - Drehzahlregler für Einspritzbrennkraftmaschinen - Google Patents

Drehzahlregler für Einspritzbrennkraftmaschinen Download PDF

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Publication number
EP0373383B1
EP0373383B1 EP89121364A EP89121364A EP0373383B1 EP 0373383 B1 EP0373383 B1 EP 0373383B1 EP 89121364 A EP89121364 A EP 89121364A EP 89121364 A EP89121364 A EP 89121364A EP 0373383 B1 EP0373383 B1 EP 0373383B1
Authority
EP
European Patent Office
Prior art keywords
magnet
rotational speed
speed governor
adjusting sleeve
screw
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
EP89121364A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0373383A1 (de
Inventor
Siegfried Dipl.-Ing.(Fh) Ruthardt
Ngoc-Thach Dipl.-Ing. Nguyen
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 EP0373383A1 publication Critical patent/EP0373383A1/de
Application granted granted Critical
Publication of EP0373383B1 publication Critical patent/EP0373383B1/de
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
    • 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
    • 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
    • F02D1/10—Transmission of control impulse to pump control, e.g. with power drive or power assistance mechanical

Definitions

  • the invention relates to a speed controller according to the preamble of the main claim.
  • a sudden adjustment of the controller in the direction of a higher load - i.e. when the vehicle is accelerating - causes a sudden increase in engine torque, as a result of which the engine-drive-vehicle mass system is excited to vibrate, i.e. starts to jerk.
  • This bucking affects driving quality and driving comfort and can lead to damage to the drive elements.
  • Another disadvantage is that a relatively large amount of installation space is required for the articulation of the magnet armature and that, after installation, the actuator is no longer accessible for adjustment of the controller.
  • the speed controller according to the invention with the characterizing features of the main claim has the advantage that the setting of the speed controller is easier and safer to carry out or even possible and that components and thus weight and space are saved.
  • the arrangement of the swivel bearing on the driving pin with adjusting thread which can be screwed into an adjusting sleeve guided axially in the controller housing and can be countered by the magnet armature, creates a non-positive and adjustable connection between the actuator and control lever, so that a compensating tappet is not required.
  • Another component is saved by using the magnet armature as a lock nut.
  • the driver pin with the adjusting sleeve is arranged inside the speed regulator housing, while only the lifting magnet itself with magnet armature is arranged outside the speed regulator housing on its end face. This arrangement saves installation space and reduces the lever arm of the weight acting on the housing and control lever.
  • a screw-in connector which is arranged in a corresponding threaded hole in the controller housing, is used to guide the adjusting sleeve in the controller housing. This considerably simplifies the assembly of the driver pin with the adjusting sleeve.
  • the invention consists of an excitation coil and components Magnet made of magnetic material for guiding the magnetic field is designed so that the magnet can be slid on the one hand via the magnetic armature attached to the driving pin and, on the other hand, when the coil current is switched on, maximum and virtually unchanged lifting force is exerted on the magnetic armature over the entire stroke.
  • the configuration of the magnetic components for guiding the magnetic field also has the advantage that there is a very small air gap between them and the armature, thereby a very low leakage flux, and a high magnetic field line density through the magnet armature.
  • the lifting force acting on the magnet armature is quickly responsive and almost unchanged along the stroke, which prevents excessive acceleration and hard impact of the armature.
  • the pull-in and pull-out characteristics of the magnet according to the invention allow very high control frequencies.
  • the magnetic armature is coated on its outer surface opposite the lifting magnet with a non-magnetic sliding material.
  • a non-magnetic sliding material This has the advantage that good guidance and accurate at the same time defined air gap can be achieved. Particularly low friction is achieved by only partially, preferably annularly applying the sliding layer around the magnet armature.
  • the non-magnetic sliding layer consists of Teflon.
  • Teflon has the advantage of low friction values and at the same time good suitability for coating surfaces.
  • a thin brass ring is provided on the magnet armature as a non-magnetic sliding guide. This has the advantage that the desired sliding guidance and the air gap to be maintained are achieved in a particularly simple and inexpensive manner.
  • the combination part comprising the magnet armature, adjusting sleeve and driving pin together has only two narrow sliding guides, which are also arranged at the longest possible distance from one another.
  • One slide guide is formed by a ring taper of the screw-in connector on the side facing away from the magnet armature, the second slide guide forms the non-magnetic coating or the thin brass ring on the screw-in connector opposite side are provided on the surface of the magnet armature.
  • the combination part consisting of the adjusting sleeve, driver pin and magnet armature receives an auxiliary guide through the screw socket.
  • the play between the screw-in connector and the adjusting sleeve on the side facing the magnet armature is greater than that between the lifting magnet and the armature guide, so that after the lifting magnet has been applied, the combination part is only on the armature through the sliding layer and on the side of the screw-in connector facing away from this through the ring taper is led.
  • the screw-in connector has an anti-rotation device for the adjusting sleeve, which at the same time serves as a return spring holder during the assembly of the adjusting sleeve, screw-in connector and snap ring.
  • the adjusting sleeve on the side facing the control rod has a snap ring which is arranged outside the screw-in socket and serves as a stop. This results in a simple and space-saving stop.
  • the end face of the screw-in connector facing the magnet armature is designed as a second stop for the combination part comprising a driving pin, adjusting sleeve and magnet armature. Without an additional component, an anchor point in the opposite direction is obtained.
  • control lever is designed as an articulated lever. This has the advantage that, when the adjusting sleeve lies against the screw-in socket against the stop, the sustained load on the control lever that occurs in corresponding driving situations, namely overrun operation, is absorbed by the same being bent.
  • FIG. 1 shows a speed controller according to the invention
  • FIG. 2 shows an enlarged detail of the actuating device according to the invention
  • FIGS. 3 and 4 show a bendable control lever from two different perspectives, each in a simplified representation
  • a centrifugal weight carrier 11 is attached to the camshaft 10 of an injection pump, not shown, on which centrifugal weights 12 are pivotally mounted. These centrifugal weights 12 engage with pressure arms 13, only one of which is shown, on a regulator sleeve 14 serving as a control element, which transmits the sleeve stroke caused by the centrifugal weights 12 to a sleeve bolt 16.
  • the socket bolt 16 is articulated by means of a bearing pin 17 on a guide lever 18 of a control linkage 20, which can be pivoted on a bearing pin 21 fastened in the control housing denoted by 19, and thus the Regulator sleeve 14 leads in their lifting movements.
  • a bell crank 22 of the control linkage 20 is articulated to the socket bolt 16, while the other end of this bell crank 22 has an elongated hole guide 23 into which a pin 24 of an adjusting lever 25 engages.
  • the bell crank 22 has a common pivot bearing 28 with a control lever 29, which is articulated on the one hand via a resilient tab 31 to a control rod 32 serving as a delivery rate adjusting element of the injection pump and on the other hand in a on the driving pin 33 which is explained in more detail with reference to FIG Lifting magnet formed actuator is arranged pivot bearing 26 is mounted.
  • the regulator sleeve 14 abuts above the idle speeds due to the force of the flyweights 12 displaced against an adjustment capsule 34 serving as a stroke stop.
  • the adjustment capsule 34 is arranged on a force transmission lever 35 serving as a support member, which can be pivoted about the bearing pin 21 and by a main regulating spring 36 with its free one End is pressed against a stop 37 fixed to the housing.
  • the biasing force of this main control spring 36 which serves as the final speed control spring, is determined by the installation position and can be adjusted via a screwed-in abutment 38.
  • the idle position of the adjusting lever 25 is limited by a stop 39, which is adjustable in the housing 19 and can be determined by means of a nut 40.
  • FIG. 2 shows the embodiment of the actuating device according to the invention, the current supply to the solenoid 41 of the lifting magnet not being shown.
  • the magnetic coil 41 is accommodated in a magnetic housing 42 made of magnetic material, which is open towards the control lever 29 and on the opposite side has a magnetic cover 43 which is also made of magnetic material and partially extends into the coil ring in the form of a nozzle.
  • the controller housing 19 is provided with a non-magnetic end cover 44 which has a countersink 45 and a recess 46 for receiving the magnet housing 42 with a magnet coil 41 and magnet cover 43.
  • the magnet housing 42 is connected to the regulator housing 19 and the end cover 44 by fastening elements 47 and 48.
  • the driving pin 33 which is articulated to the control lever 29 via the pivot bearing 26, is provided with an adjusting thread 33a, which engages on the one hand with the internal thread of an adjusting sleeve 49 and on the other hand with the internal thread of a blind hole 51 provided in a magnet armature 50.
  • the adjusting sleeve 49 is mounted in a screw-in socket 52 connected via an external thread to the regulator housing 19, which is sleeve-like in this area and provided with a threaded bore 27, and on the one hand, on the one facing the control lever 29 Side, guided by a ring taper 53 and on the other hand secured by pressing pins 54 and 55 against rotation.
  • the pins 54 and 55 engage in longitudinal slots in an area 56 of an enlarged circumference of the adjusting sleeve 49.
  • the magnet armature 50 which is essentially cylindrical, has an annular, non-magnetic coating serving as a sliding guide 69 on the side of its lateral surface facing the magnetic cover 43.
  • annular space 57 is formed between the adjusting sleeve 49 and the screw-in socket 52, in which a return spring 30 biased in the immersion direction of the magnet armature 50 works.
  • the adjusting sleeve 49 also has an annular groove 58 on its side facing the control lever 29, into which a snap ring 59 is inserted, which is located outside the screw-in socket 52 and serves as a stop.
  • the end face 70 of the screw-in socket 52 facing the magnet armature 50 acts as a second stop for the combination part comprising the driving pin 33, the adjusting sleeve 49 and the magnet armature 50.
  • the configuration of the control lever 29 as an articulated lever can be seen in FIGS. 3 and 4.
  • the control lever 29 as an articulated lever consists of two mutually rotatable lever arms 60 and 61.
  • the lever arm 60 is at its angled lower end 62 to the driver pin 33 articulated.
  • the pivot bearing 28 can be seen, via which the lever arm 60 is connected to the bell crank 22.
  • the lever arm 60 and the lever arm 61 are connected to one another in a partially overlapping manner by a rotary bearing 63 which is arranged in the upper half of the lever arm 60 and at the same time serves as a receptacle for a torsion spring 64 having two spring arms 65 and 66.
  • the two spring arms 65 and 66 are crossed against the spring force and angled at their free end so that they are pressed against a lever arm 60, 61 by the spring force.
  • the lever arm 61 In its area of overlap with the lever arm 60, the lever arm 61 has a stop plate 67 which prevents the lever arm 61 from kinking against the lever arm 60 in the relaxation direction of the torsion spring 64.
  • the linkage 68 to the control rod 32 is also shown via the tab 31.
  • the actuating device works as follows:
  • the signals of an acceleration sensor, which are delayed by a phase shifter, are transmitted to the magnetic coil 41 as control signals in a specific switching frequency and duty cycle.
  • a magnetic field is generated which exerts a force on the magnet armature 50 in the direction of the screw-in socket 52.
  • the magnet armature 50 together with the driving pin 33 and the adjusting sleeve 49 is placed on the end face 70 of the screw-in connector serving as a stop 52 pulled against the force of the return spring 30.
  • the movement of the driving pin 33 is transmitted via the swivel bearing 26 to the control lever 29, which in turn moves the control rod 32 serving as the delivery quantity adjusting member.
  • the longitudinal vibrations are dampened by this phase-shifted change in the delivery rate.
  • a particularly important feature of the actuating device according to the invention is that the basic setting of the pivot bearing 26 and thus the control lever 29 (full load setting) can be carried out by the screw-in depth of the driving pin 33 in the adjusting sleeve 49 and this setting by locking with the magnet armature likewise screwed onto the driving pin 33 50 is secured.
  • This setting is made before installing the magnet housing 42 with the magnet coil 41 and cover 43, so that all parts are easily accessible.
  • the combination part consisting of adjusting sleeve 49, driving pin 33 and magnetic armature 50 is guided through the enlarged area 56 of the adjusting sleeve 49 in the screw-in socket 52.
  • the combination part on the slide 69 of the Magnet armature 50 is guided through the magnet cover 43, which is drawn into the magnet ring in the form of a socket, since the play between the sliding guide 69 and the magnet cover 43 is smaller than between the enlarged region 56 of the adjusting sleeve 49 and the screw-in socket 52.

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)
  • Electromagnets (AREA)
EP89121364A 1988-12-16 1989-11-18 Drehzahlregler für Einspritzbrennkraftmaschinen Expired - Lifetime EP0373383B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3842308 1988-12-16
DE3842308A DE3842308C1 (enrdf_load_stackoverflow) 1988-12-16 1988-12-16

Publications (2)

Publication Number Publication Date
EP0373383A1 EP0373383A1 (de) 1990-06-20
EP0373383B1 true EP0373383B1 (de) 1994-02-16

Family

ID=6369267

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89121364A Expired - Lifetime EP0373383B1 (de) 1988-12-16 1989-11-18 Drehzahlregler für Einspritzbrennkraftmaschinen

Country Status (4)

Country Link
EP (1) EP0373383B1 (enrdf_load_stackoverflow)
JP (1) JP2904831B2 (enrdf_load_stackoverflow)
DE (2) DE3842308C1 (enrdf_load_stackoverflow)
ES (1) ES2049303T3 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015121707A1 (de) * 2015-12-14 2017-06-14 Eto Magnetic Gmbh Elektromagnetische Stellvorrichtung sowie Stellsystem

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3425105A1 (de) * 1984-07-07 1986-01-16 Daimler-Benz Ag, 7000 Stuttgart Verfahren und vorrichtung zum daempfen von fahrlaengsschwingungen an einem kraftfahrzeug
DE3644155C1 (de) * 1986-12-23 1988-07-21 Daimler Benz Ag Vorrichtung zum Daempfen von Fahrlaengsschwingungen an einem Kraftfahrzeug
EP0284634A1 (de) * 1987-03-31 1988-10-05 MOOG GmbH Elektromechanisches Stellglied

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015121707A1 (de) * 2015-12-14 2017-06-14 Eto Magnetic Gmbh Elektromagnetische Stellvorrichtung sowie Stellsystem

Also Published As

Publication number Publication date
DE3842308C1 (enrdf_load_stackoverflow) 1990-06-13
DE58906994D1 (de) 1994-03-24
EP0373383A1 (de) 1990-06-20
ES2049303T3 (es) 1994-04-16
JPH02196141A (ja) 1990-08-02
JP2904831B2 (ja) 1999-06-14

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