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EP1005608A1 - Load setting device - Google Patents

Load setting device

Info

Publication number
EP1005608A1
EP1005608A1 EP98946329A EP98946329A EP1005608A1 EP 1005608 A1 EP1005608 A1 EP 1005608A1 EP 98946329 A EP98946329 A EP 98946329A EP 98946329 A EP98946329 A EP 98946329A EP 1005608 A1 EP1005608 A1 EP 1005608A1
Authority
EP
European Patent Office
Prior art keywords
load
gear
actuating
torsion spring
emergency running
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
EP98946329A
Other languages
German (de)
French (fr)
Other versions
EP1005608B1 (en
Inventor
Herbert Wicker
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.)
Siemens AG
Original Assignee
Mannesmann VDO AG
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 Mannesmann VDO AG filed Critical Mannesmann VDO AG
Publication of EP1005608A1 publication Critical patent/EP1005608A1/en
Application granted granted Critical
Publication of EP1005608B1 publication Critical patent/EP1005608B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
    • 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
    • F02D11/10—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 electric type
    • F02D11/107—Safety-related aspects
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
    • F02D2009/0201—Arrangements; Control features; Details thereof
    • F02D2009/0277—Fail-safe mechanisms, e.g. with limp-home feature, to close throttle if actuator fails, or if control cable sticks or breaks

Definitions

  • the invention relates to a load adjusting device for an actuator determining the performance of an internal combustion engine, in particular in the form of a throttle valve, arranged on an actuating shaft, the actuating shaft being pivotably drivable between a minimum load position and a full load position by means of a reversible actuating part by means of a reversible actuating gear.
  • a pre-tensioned return spring designed as a torsion spring, which acts on the actuating shaft in the minimum load direction and an emergency running spring, by means of which the actuating shaft can be moved in the full load direction up to an emergency running position.
  • Load adjustment devices of the above type are generally known under the name E-gas for power adjustment of the internal combustion engine of motor vehicles.
  • the minimum load position is designed so that the internal combustion engine runs just as smoothly when idling.
  • this may be necessary if the motor vehicle has to be driven out of a danger area, but the load adjustment device can no longer be adjusted by actuating the accelerator pedal as a result of a failure of the control electronics or the actuating gear.
  • an emergency running spring is provided, which ensures that the actuator, in the event of failure of the control electronics or the actuating gear, inevitably moves from the minimum load setting into an emergency running position in which the internal combustion engine generates a sufficiently large torque, to move the motor vehicle at low speed.
  • This emergency running position is determined by a stop which is displaceable against the force of the return spring, against which the actuating part is tensioned by means of the emergency running spring and which is actuated by the actuating part against the force of the return spring can be moved when the actuator moves from the emergency running position in the direction of the volatile position.
  • the emergency running spring required to reach the emergency running position requires - apart from the costs - a corresponding installation space and leads to an increase in weight compared to a load adjustment device without inevitable movement into an emergency running position in the event of a defect.
  • the invention is based on the problem of designing a load adjustment device of the type mentioned at the outset in such a way that it is as compact as possible and can be produced cost-effectively.
  • the return spring and the emergency running spring are formed by a single torsion spring, the first end of which is connected to the actuating shaft and the other end between the emergency running position and the minimal load position by means of a minimal load gear coupled to the actuating gear against the force of the torsion spring is movable.
  • the single torsion spring is used twice as a return spring and as an emergency running spring and, depending on the actuating angle of the actuating shaft, is tensioned either directly via the actuating gear or the minimal load gear coupled to the actuating gear.
  • the actuating shaft therefore swings automatically from any position into the emergency running position if no forces act on the actuating gear.
  • the load adjustment device according to the invention is particularly compact and can therefore be produced very inexpensively.
  • the load adjustment device according to the invention requires only a particularly simple minimal load gear in addition to the actuating gear.
  • the torsion spring can be pretensioned by the minimal load gear, for example, in that the second end of the torsion spring is fastened on a holding part which can be adjusted by the minimal load gear.
  • the pretensioning of the torsion spring by the minimal load gear requires a Particularly low construction costs if the second end of the torsion spring rests against a stop between the emergency running position and the full load position and can be moved away from the stop between the emergency running position and the minimum load position.
  • the actuating gear can be arranged in a space-saving manner in the load adjusting device if the actuating part has a toothed segment designed for meshing with a gear wheel of the actuating gear.
  • the actuating gear has a particularly low overall height if the actuating gear has a large-diameter intermediate gear driven by a drive pinion, which is non-rotatably and coaxially connected to a small-diameter gear pivoting the actuating part.
  • This design also has the advantage that the actuating shaft is pivoted by the actuating gear if the torsion spring breaks. A defect in a single component of the load adjustment device according to the invention therefore does not lead to a complete failure of the internal combustion engine controlled thereby.
  • the minimal load gearbox requires a particularly low structural outlay if a cam for moving the second end of the torsion spring is arranged on the intermediate gearwheel.
  • the cam can be designed in many different ways.
  • the cam can be designed as a pin made in one piece with the intermediate gear wheel, or it can be formed by a freely rotatable roller.
  • the torsion spring takes up particularly little space if it is a spiral spring. If a particularly high level of security against spring breakage is required, two identical spiral springs arranged one above the other can simply be used as the torsion spring. According to another advantageous development of the invention, the torsion spring is reliably held in its position when a guide part which is laterally in contact with the torsion spring is fastened in the housing supporting the idler gear.
  • a limitation of the adjustment range of the adjustment shaft requires a particularly low construction effort if a stop plate which reaches the housing shaft in the minimum load position and in the full load position is fastened in a rotationally fixed manner.
  • the stops for adjusting a standing gas or a full load limitation can be designed to be adjustable.
  • FIG. 1 shows a section through a load adjustment device according to the invention
  • FIG. 2 shows a partially sectioned side view of the load adjustment device from FIG. 1 in full load position
  • FIG. 3 shows a partially sectioned side view of the load adjustment device from FIG. 1 in the emergency running position
  • Figure 4 is a partially sectioned side view of the load adjustment device of Figure 1 in the minimum load position.
  • Figure 1 shows a portion of a housing 1 of a throttle valve assembly.
  • An actuating shaft 2 is mounted in the housing 1, which can be a throttle valve shaft on which a throttle valve, not shown, is arranged.
  • the actuating gear 5 has a servomotor 6 which drives a large-diameter intermediate gear 8 via a drive pinion 7.
  • This intermediate gear 8 is made in one piece with a small-diameter gear 9 and a radially protruding cam 10 and is mounted on an axis 11.
  • the actuating part 4 having the toothed segment 3 is permanently in engagement with the gear 9 arranged on the intermediate gear 8.
  • the throttle valve assembly has a torsion spring 18 which is fastened at one end to the actuating shaft 2 and at the other end 12 to a stop 13 fixed to the housing is present.
  • a stop plate 14 is arranged in a rotationally fixed manner on the actuating shaft 2.
  • the housing 1 has a stop 15 in the region of the stop plate 14.
  • FIGS 2 to 4 show the operation of the throttle valve assembly of Figure 1 in a view from above in different positions.
  • the stop plate 14 has a full load arm 16 and a minimum load arm 17.
  • the second end 12 of the torsion spring 18 is angled and projects beyond the stop 13 into the movement path of the cam 10 arranged on the intermediate gear 8.
  • a guide part 19 designed as a bolt is integrated in the housing 1 of the throttle valve connector (in particular pressed in, fastened to it or by the housing 1 itself formed), which holds the torsion spring 18 in a lateral area.
  • this guide part 19 can also be used as a stop for the minimum load position.
  • Figure 2 shows the load adjustment device in full load.
  • the intermediate gear 8 is deflected clockwise by means of the servomotor 6 shown in FIG.
  • the gear 9 of the actuating gear 5 pivots the toothed segment 3 of the actuating part 4 counterclockwise until the full load arm 16 of the stop plate 14 comes against the stop 15 of the housing 1.
  • the actuating part 4 and the one end of the torsion spring 18 are connected in a rotationally fixed manner to the actuating shaft 2, the actuating shaft 2 is deflected and the torsion spring 18 is tensioned.
  • the second end 12 of the torsion spring 18 bears against the stop 13.
  • FIG. 4 shows the throttle valve connector in the minimum load position, in which the minimum load arm 17 of the stop plate 14 bears against the stop 15 fixed to the housing.
  • This minimum load position is achieved from the emergency running position in that the drive pinion 7 of the servomotor 6 shown in FIG. 1 adjusts the intermediate gear 8 counterclockwise.
  • the actuating shaft 2 is deflected via the actuating gear 5.
  • the cam 10 lifts the second end 12 of the torsion spring 18 from the stop 13.
  • the cam 10 and the second end 12 of the torsion spring 18 thus form a minimum load transmission 20.
  • the second end 12 of the torsion spring 18 moves the cam 10 into the emergency running position shown in FIG.
  • the emergency running position is therefore inevitably reached by the force of the torsion spring 18 when the servomotor 6 shown in FIG. 1 is no longer energized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Transmission Devices (AREA)
  • Gear Transmission (AREA)

Abstract

A load setting device for a setting member (4) which is arranged on a setting shaft (2) and determines the power supplied by an internal combustion engine has a torsion spring (18) stressed between a minimum load position and an emergency running position of a minimum load gearbox and between a full load position and the emergency running position of a setting gear box (5). The minimum load gearbox has a cam (10) which can be swivelled in the same direction as a toothed wheel (9) arranged on an intermediate toothed wheel (8) for displacing an end (12) of the torsion spring (18) which, in the emergency running position, lies on a stop (13). The torsion spring (18) preloads the setting member (4) and therefore the setting shaft (2) permanently in the emergency running position.

Description

Beschreibung description
LastverstellvorrichtungLoad adjustment device
Die Erfindung betrifft eine Lastverstellvorrichtung für ein die Leistung einer Brennkraftmaschine bestimmendes, insbesondere als Drosselklappe ausgebildetes, auf einer Stellwelle angeordnetes Stellglied, wobei die Stellwelle über ein drehfest mit ihr verbundenes Stellteil mittels eines rever- sierbaren Steligetriebes zwischen einer Minimallaststellung und einer Vollaststellung schwenkbar antreibbar ist, mit einer als Drehfeder ausgebildeten, vorgespannten Rückstellfeder, die die Stellwelle in Minimallastrichtung beaufschlagt und einer Notlauffeder, durch die die Stellwelle in Vollastrichtung bis zu einer Notlaufstellung bewegbar ist.The invention relates to a load adjusting device for an actuator determining the performance of an internal combustion engine, in particular in the form of a throttle valve, arranged on an actuating shaft, the actuating shaft being pivotably drivable between a minimum load position and a full load position by means of a reversible actuating part by means of a reversible actuating gear. with a pre-tensioned return spring designed as a torsion spring, which acts on the actuating shaft in the minimum load direction and an emergency running spring, by means of which the actuating shaft can be moved in the full load direction up to an emergency running position.
Lastverstellvorrichtungen der vorstehenden Art sind allgemein unter der Bezeichnung E-Gas zur Leistungsverstellung der Brennkraftmaschine von Kraftfahrzeugen bekannt. Bei ihnen ist zur Minimierung des Kraftstoffverbrauchs die Minimallaststellung so ausgelegt, daß die Brennkraftmaschine dabei im Leerlauf noch so eben gleichmäßig läuft. Das führt dazu, daß es in Minimallaststellung nicht möglich ist, ein ausreichendes Drehmoment zu erzeugen, um das Kraftfahrzeug zu bewegen. Das kann jedoch erforderlich werden, wenn das Kraftfahrzeug aus einem Gefahrenbereich gefahren werden muß, die Lastverstellvorrichtung jedoch infolge eines Ausfalls der Steuerelektronik oder des Stellgetriebes nicht mehr durch Betätigung des Fahrpedals verstellt werden kann. Aus diesem Grunde sieht man bei den bekannten Lastverstellvorrichtungen zusätzlich zur Rückstellfeder eine Notlauffeder vor, welche dafür sorgt, daß das Stellglied bei Ausfall der Steuerelektronik oder des Stellgetriebes sich aus der Minimallaststeliung zwangsläufig in eine Notlaufstellung bewegt, in der die Brennkraftmaschine ein ausreichend großes Drehmoment erzeugt, um das Kraftfahrzeug mit geringer Geschwindigkeit zu bewegen. Diese Notlaufstellung wird durch einen gegen die Kraft der Rückstellfeder verschieblichen Anschlag festgelegt, gegen den das Stellteil mittels der Notlauffeder gespannt ist und der von dem Stellteil gegen die Kraft der Rückstellfeder verschoben werden kann, wenn sich das Stellteil aus der Notlaufstellung in Richtung der Voliaststellung bewegt.Load adjustment devices of the above type are generally known under the name E-gas for power adjustment of the internal combustion engine of motor vehicles. In order to minimize fuel consumption, the minimum load position is designed so that the internal combustion engine runs just as smoothly when idling. As a result, it is not possible to generate sufficient torque in order to move the motor vehicle in the minimum load position. However, this may be necessary if the motor vehicle has to be driven out of a danger area, but the load adjustment device can no longer be adjusted by actuating the accelerator pedal as a result of a failure of the control electronics or the actuating gear. For this reason, in the known load adjustment devices, in addition to the return spring, an emergency running spring is provided, which ensures that the actuator, in the event of failure of the control electronics or the actuating gear, inevitably moves from the minimum load setting into an emergency running position in which the internal combustion engine generates a sufficiently large torque, to move the motor vehicle at low speed. This emergency running position is determined by a stop which is displaceable against the force of the return spring, against which the actuating part is tensioned by means of the emergency running spring and which is actuated by the actuating part against the force of the return spring can be moved when the actuator moves from the emergency running position in the direction of the volatile position.
Die für das Erreichen der Notlaufstellung erforderliche Notlauffeder erfordert - abgesehen von den Kosten - einen entsprechenden Bauraum und führt zu einer Erhöhung des Gewichtes im Vergleich zu einer Lastverstellvorrichtung ohne zwangsläufige Bewegung in eine Notlaufstellung bei einem Defekt.The emergency running spring required to reach the emergency running position requires - apart from the costs - a corresponding installation space and leads to an increase in weight compared to a load adjustment device without inevitable movement into an emergency running position in the event of a defect.
Der Erfindung liegt das Problem zugrunde, eine Lastverstellvorrichtung der eingangs genannten Art so zu gestalten, daß sie möglichst kompakt aufgebaut und kostengünstig herstellbar ist.The invention is based on the problem of designing a load adjustment device of the type mentioned at the outset in such a way that it is as compact as possible and can be produced cost-effectively.
Dieses Problem wird erfindungsgemäß dadurch gelöst, daß die Rücklauffeder und die Notlauffeder durch eine einzige Drehfeder gebildet sind, deren erstes Ende mit der Stellwelle verbunden ist und deren anderes Ende zwischen der Notlaufstellung und der Minimallaststellung mittels eines mit dem Stellgetriebe gekoppelten Minimallastgetriebes entgegen der Kraft der Drehfeder bewegbar ist.This problem is solved according to the invention in that the return spring and the emergency running spring are formed by a single torsion spring, the first end of which is connected to the actuating shaft and the other end between the emergency running position and the minimal load position by means of a minimal load gear coupled to the actuating gear against the force of the torsion spring is movable.
Durch diese Gestaltung wird die einzige Drehfeder als Rücklauffeder und als Notlauffeder doppelt genutzt und in Abhängigkeit von dem Stellwinkel der Stellwelle entweder unmittelbar über das Stellgetriebe oder das mit dem Stellgetriebe gekoppelte Minimallastgetriebe gespannt. Die Stellwelle schwenkt daher aus jeder Position automatisch in die Notlaufstellung, wenn keine Kräfte auf das Stellgetriebe wirken. Durch den Wegfall einer der Federn gestaltet sich die erfindungsgemäße Lastverstellvorrichtung besonders kompakt und ist deshalb sehr kostengünstig herstellbar. Weiterhin benötigt die erfindungsgemäße Lastverstellvorrichtung neben dem Stellgetriebe nur ein besonders einfach aufgebautes Minimallastgetriebe.With this design, the single torsion spring is used twice as a return spring and as an emergency running spring and, depending on the actuating angle of the actuating shaft, is tensioned either directly via the actuating gear or the minimal load gear coupled to the actuating gear. The actuating shaft therefore swings automatically from any position into the emergency running position if no forces act on the actuating gear. By eliminating one of the springs, the load adjustment device according to the invention is particularly compact and can therefore be produced very inexpensively. Furthermore, the load adjustment device according to the invention requires only a particularly simple minimal load gear in addition to the actuating gear.
Die Vorspannung der Drehfeder durch das Minimallastgetriebe könnte beispielsweise dadurch erfolgen, daß das zweite Ende der Drehfeder auf einem von dem Minimallastgetriebe verstellbaren Halteteil befestigt ist. Die Vorspannung der Drehfeder durch das Minimallastgetriebe erfordert jedoch gemäß einer vorteilhaften Weiterbildung der Erfindung einen be- sonders geringen baulichen Aufwand, wenn das zweite Ende der Drehfeder zwischen der Notlaufstellung und der Vollaststellung an einem Anschlag anliegt und zwischen der Notlaufstellung und der Minimallaststellung von dem Anschlag wegbewegbar ist.The torsion spring can be pretensioned by the minimal load gear, for example, in that the second end of the torsion spring is fastened on a holding part which can be adjusted by the minimal load gear. However, according to an advantageous development of the invention, the pretensioning of the torsion spring by the minimal load gear requires a Particularly low construction costs if the second end of the torsion spring rests against a stop between the emergency running position and the full load position and can be moved away from the stop between the emergency running position and the minimum load position.
Das Stellgetriebe läßt sich gemäß einer anderen vorteilhaften Weiterbildung der Erfindung platzsparend in der Lastverstellvorrichtung anordnen, wenn das Stellteil ein zum Kämmen mit einem Zahnrad des Stellgetriebes ausgebildetes Zahnsegment hat.According to another advantageous development of the invention, the actuating gear can be arranged in a space-saving manner in the load adjusting device if the actuating part has a toothed segment designed for meshing with a gear wheel of the actuating gear.
Das Stellgetriebe hat gemäß einer anderen vorteilhaften Weiterbildung der Erfindung eine besonders geringe Bauhöhe, wenn das Stellgetriebe ein von einem Antriebsritzel angetriebenes, durchmessergroßes Zwischenzahnrad hat, welches mit einem das Stellteil verschwenkenden, durchmesserkleinen Zahnrad drehfest und koaxial verbunden ist. Diese Gestaltung hat zudem den Vorteil, daß bei einem Bruch der Drehfeder die Stellwelle von dem Stellgetriebe verschwenkt wird. Ein Defekt an einem einzigen Bauteil der erfindungsgemäßen Lastverstellvorrichtung führt deshalb nicht zu einem vollständigen Ausfall der damit gesteuerten Brennkraftmaschine.According to another advantageous development of the invention, the actuating gear has a particularly low overall height if the actuating gear has a large-diameter intermediate gear driven by a drive pinion, which is non-rotatably and coaxially connected to a small-diameter gear pivoting the actuating part. This design also has the advantage that the actuating shaft is pivoted by the actuating gear if the torsion spring breaks. A defect in a single component of the load adjustment device according to the invention therefore does not lead to a complete failure of the internal combustion engine controlled thereby.
Das Minimallastgetriebe erfordert gemäß einer anderen vorteilhaften Weiterbildung der Erfindung einen besonders geringen baulichen Aufwand, wenn auf dem Zwischenzahnrad ein Nocken zum Bewegen des zweiten Endes der Drehfeder angeordnet ist. Der Nocken kann hierbei auf die verschiedenste Weise ausgebildet sein. Beispielsweise kann der Nokken als einteilig mit dem Zwischenzahnrad gefertigter Zapfen gestaltet oder durch eine freidrehbare Rolle ausgebildet sein.According to another advantageous development of the invention, the minimal load gearbox requires a particularly low structural outlay if a cam for moving the second end of the torsion spring is arranged on the intermediate gearwheel. The cam can be designed in many different ways. For example, the cam can be designed as a pin made in one piece with the intermediate gear wheel, or it can be formed by a freely rotatable roller.
Die Drehfeder beansprucht gemäß einer anderen vorteilhaften Weiterbildung der Erfindung besonders wenig Platz, wenn sie eine Spiralfeder ist. Wenn eine besonders hohe Sicherheit gegen einen Federbruch gefordert ist, können einfach zwei gleiche, übereinander angeordnete Spiralfedern als Drehfeder eingesetzt werden. Die Drehfeder wird gemäß einer anderen vorteilhaften Weiterbildung der Erfindung zuverlässig in ihrer Position gehalten, wenn in dem das Zwischenzahnrad lagernden Gehäuse ein seitlich an der Drehfeder anliegendes Führungsteil befestigt ist.According to another advantageous development of the invention, the torsion spring takes up particularly little space if it is a spiral spring. If a particularly high level of security against spring breakage is required, two identical spiral springs arranged one above the other can simply be used as the torsion spring. According to another advantageous development of the invention, the torsion spring is reliably held in its position when a guide part which is laterally in contact with the torsion spring is fastened in the housing supporting the idler gear.
Eine Begrenzung des Stellbereichs der Stellwelie erfordert gemäß einer anderen vorteilhaften Weiterbildung der Erfindung einen besonders geringen baulichen Aufwand, wenn eine in Minimallaststellung und in Vollaststellung gegen gehäusefeste Anschläge gelangende Anschlagplatte drehfest auf der Stellwelle befestigt ist. Selbstverständlich können die Anschläge zum Einstellen eines Standgases oder einer Vollastbegrenzung verstellbar gestaltet sein.According to another advantageous development of the invention, a limitation of the adjustment range of the adjustment shaft requires a particularly low construction effort if a stop plate which reaches the housing shaft in the minimum load position and in the full load position is fastened in a rotationally fixed manner. Of course, the stops for adjusting a standing gas or a full load limitation can be designed to be adjustable.
Zur weiteren Verringerung der Fertigungskosten der erfindungsgemäßen Lastverstellvorrichtung trägt es bei, wenn das Stellteil und die Anschlagplatte einteilig gefertigt sind.It helps to further reduce the manufacturing costs of the load adjustment device according to the invention if the actuating part and the stop plate are made in one piece.
Die Erfindung läßt zahlreiche Ausführungsformen zu. Zur weiteren Verdeutlichung ihres Grundprinzips ist eine davon in der Zeichnung dargestellt und wird nachfolgend beschrieben.The invention permits numerous embodiments. To further clarify its basic principle, one of these is shown in the drawing and is described below.
Diese zeigt inThis shows in
Figur 1 einen Schnitt durch eine erfindungsgemäße Lastverstellvorrichtung,FIG. 1 shows a section through a load adjustment device according to the invention,
Figur 2 eine teilweise geschnittene Seitenansicht der Lastverstellvorrichtung aus Figur 1 in Vollaststellung,FIG. 2 shows a partially sectioned side view of the load adjustment device from FIG. 1 in full load position,
Figur 3 eine teilweise geschnittene Seitenansicht der Lastverstellvorrichtung aus Figur 1 in Notlaufstellung,FIG. 3 shows a partially sectioned side view of the load adjustment device from FIG. 1 in the emergency running position,
Figur 4 eine teilweise geschnittene Seitenansicht der Lastverstellvorrichtung aus Figur 1 in Minimallaststellung. Die Figur 1 zeigt einen Teilbereich eines Gehäuses 1 eines Drosselklappenstutzens. In dem Gehäuse 1 ist eine Stellwelle 2 gelagert, bei der es sich um eine Drosselklappenwelle handeln kann, auf der eine nicht dargestellte Drosselklappe angeordnet ist. Drehfest auf der Stellwelle 2 sitzt ein ein Zahnsegment 3 aufweisendes Stellteil 4, welches mittels eines Stellgetriebes 5 verschwenkbar ist.Figure 4 is a partially sectioned side view of the load adjustment device of Figure 1 in the minimum load position. Figure 1 shows a portion of a housing 1 of a throttle valve assembly. An actuating shaft 2 is mounted in the housing 1, which can be a throttle valve shaft on which a throttle valve, not shown, is arranged. An actuating part 4, which has a toothed segment 3 and is pivotable on the actuating shaft 2, can be pivoted by means of an actuating gear 5.
Das Stellgetriebe 5 hat einen Stellmotor 6, der über ein Antriebsritzel 7 ein durchmessergroßes Zwischenzahnrad 8 antreibt. Dieses Zwischenzahnrad 8 ist einteilig mit einem durchmesserkleinen Zahnrad 9 und einem radial hervorstehenden Nocken 10 gefertigt und auf einer Achse 11 gelagert. Das das Zahnsegment 3 aufweisende Stellteil 4 steht permanent im Eingriff mit dem auf dem Zwischenzahnrad 8 angeordneten Zahnrad 9. Weiterhin hat der Drosselklappenstutzen eine Drehfeder 18, welche mit einem Ende an der Stellwelle 2 befestigt ist und mit dem anderen Ende 12 an einem gehäusefesten Anschlag 13 anliegt. Weiterhin ist auf der Stellwelle 2 eine Anschlagplatte 14 drehfest angeordnet. Das Gehäuse 1 weist im Bereich der Anschlagplatte 14 einen Anschlag 15 auf.The actuating gear 5 has a servomotor 6 which drives a large-diameter intermediate gear 8 via a drive pinion 7. This intermediate gear 8 is made in one piece with a small-diameter gear 9 and a radially protruding cam 10 and is mounted on an axis 11. The actuating part 4 having the toothed segment 3 is permanently in engagement with the gear 9 arranged on the intermediate gear 8. Furthermore, the throttle valve assembly has a torsion spring 18 which is fastened at one end to the actuating shaft 2 and at the other end 12 to a stop 13 fixed to the housing is present. Furthermore, a stop plate 14 is arranged in a rotationally fixed manner on the actuating shaft 2. The housing 1 has a stop 15 in the region of the stop plate 14.
Die Figuren 2 bis 4 zeigen die Funktionsweise des Drosselklappenstutzens aus Figur 1 in einer Ansicht von oben in verschiedenen Stellungen. Hierbei ist zu erkennen, daß die Anschlagplatte 14 einen Vollastarm 16 und einen Minimallastarm 17 aufweist. Das zweite Ende 12 der Drehfeder 18 ist abgewinkelt und überragt den Anschlag 13 bis in die Bewegungsbahn des auf dem Zwischenzahnrad 8 angeordneten Nockens 10. Weiterhin ist in dem Gehäuse 1 des Drosselklappenstutzens ein als Bolzen ausgebildetes Führungsteil 19 integriert (insbesondere eingepreßt, daran befestigt oder durch das Gehäuse 1 selbst gebildet), das die Drehfeder 18 in einem seitlichen Bereich hält. Dieses Führungsteil 19 kann bei entsprechender Ausgestaltung der Anschlagplatte 14 auch als Anschlag für die Minimallaststellung genutzt werden.Figures 2 to 4 show the operation of the throttle valve assembly of Figure 1 in a view from above in different positions. It can be seen here that the stop plate 14 has a full load arm 16 and a minimum load arm 17. The second end 12 of the torsion spring 18 is angled and projects beyond the stop 13 into the movement path of the cam 10 arranged on the intermediate gear 8. Furthermore, a guide part 19 designed as a bolt is integrated in the housing 1 of the throttle valve connector (in particular pressed in, fastened to it or by the housing 1 itself formed), which holds the torsion spring 18 in a lateral area. With a corresponding design of the stop plate 14, this guide part 19 can also be used as a stop for the minimum load position.
Die Figur 2 zeigt die Lastverstellvorrichtung in Vollaststellung. Um zu der Vollaststellung zu gelangen, wird das Zwischenzahnrad 8 mittels des in Figur 1 dargestellten Stellmotors 6 im Uhrzeigersinn ausgelenkt. Hierdurch verschwenkt das Zahnrad 9 des Stellgetriebes 5 das Zahnsegment 3 des Stellteils 4 gegen den Uhrzeigersinn, bis der Vollastarm 16 der Anschlagplatte 14 gegen den Anschlag 15 des Gehäuses 1 gelangt. Da das Stellteil 4 und das eine Ende der Drehfeder 18 drehfest mit der Stellwelle 2 verbunden sind, wird die Stellwelle 2 ausgelenkt und die Drehfeder 18 gespannt. Das zweite Ende 12 der Drehfeder 18 liegt hierbei an dem Anschlag 13 an.Figure 2 shows the load adjustment device in full load. In order to reach the full load position, the intermediate gear 8 is deflected clockwise by means of the servomotor 6 shown in FIG. As a result, the gear 9 of the actuating gear 5 pivots the toothed segment 3 of the actuating part 4 counterclockwise until the full load arm 16 of the stop plate 14 comes against the stop 15 of the housing 1. Since the actuating part 4 and the one end of the torsion spring 18 are connected in a rotationally fixed manner to the actuating shaft 2, the actuating shaft 2 is deflected and the torsion spring 18 is tensioned. The second end 12 of the torsion spring 18 bears against the stop 13.
Wenn beispielsweise durch einen Defekt der in Figur 1 dargestellte Stellmotor 6 nicht mehr bestromt wird, wird die Stellwelle 2 und damit das Stellteil 4 und das Zwischenzahnrad 8 durch die Kraft der Drehfeder 18 zurückgeschwenkt, bis der an dem Zwischenzahnrad 8 angeordnete Nokken 10 gegen das zweite Ende 12 der Drehfeder 18 gelangt. Diese Stellung kennzeichnet die Notlaufstellung, die in Figur 3 dargestellt ist. Diese Notlaufstellung zeichnet sich dadurch aus, daß weder der Minimallastarm 17, noch der Vollastarm 16 der Anschlagplatte 14 an dem gehäusefesten Anschlag 15 anliegen.If, for example, the servomotor 6 shown in FIG. 1 is no longer energized due to a defect, the actuating shaft 2 and thus the actuating part 4 and the intermediate gear 8 are pivoted back by the force of the torsion spring 18 until the cam 10 arranged on the intermediate gear 8 against the second End 12 of the torsion spring 18 arrives. This position characterizes the emergency running position, which is shown in FIG. 3. This emergency running position is characterized in that neither the minimum load arm 17 nor the full load arm 16 of the stop plate 14 abut the stop 15 fixed to the housing.
Die Figur 4 zeigt den Drosselklappenstutzen in der Minimallaststellung, bei der der Minimallastarm 17 der Anschlagplatte 14 an dem gehäusefesten Anschlag 15 anliegt. Diese Minimallaststellung wird aus der Notlaufstellung dadurch erreicht, daß das Antriebsritzel 7 des in Figur 1 dargestellten Stellmotors 6 das Zwischenzahnrad 8 gegen den Uhrzeigersinn verstellt. Hierdurch wird die Stellwelle 2 über das Stellgetriebe 5 ausgelenkt. Gleichzeitig hebt der Nocken 10 das zweite Ende 12 der Drehfeder 18 von dem Anschlag 13 ab. Der Nocken 10 und das zweite Ende 12 der Drehfeder 18 bilden damit ein Minimallastgetriebe 20. Wenn der Stellmotor 6 nicht mehr bestromt wird, bewegt das zweite Ende 12 der Drehfeder 18 den Nocken 10 bis in die in Figur 3 dargestellte Notlaufstellung. Die Notlaufstellung wird deshalb durch die Kraft der Drehfeder 18 zwangsläufig erreicht, wenn der in Figur 1 dargestellte Stellmotor 6 nicht mehr bestromt wird. FIG. 4 shows the throttle valve connector in the minimum load position, in which the minimum load arm 17 of the stop plate 14 bears against the stop 15 fixed to the housing. This minimum load position is achieved from the emergency running position in that the drive pinion 7 of the servomotor 6 shown in FIG. 1 adjusts the intermediate gear 8 counterclockwise. As a result, the actuating shaft 2 is deflected via the actuating gear 5. At the same time, the cam 10 lifts the second end 12 of the torsion spring 18 from the stop 13. The cam 10 and the second end 12 of the torsion spring 18 thus form a minimum load transmission 20. When the servomotor 6 is no longer energized, the second end 12 of the torsion spring 18 moves the cam 10 into the emergency running position shown in FIG. The emergency running position is therefore inevitably reached by the force of the torsion spring 18 when the servomotor 6 shown in FIG. 1 is no longer energized.

Claims

Patentansprüche claims
1. Lastverstellvorrichtung für ein die Leistung einer Brennkraftmaschine bestimmendes, insbesondere als Drosselklappe ausgebildetes, auf einer Stellwelle angeordnetes Stellglied, wobei die Stellwelle über ein drehfest mit ihr verbundenes Stellteil mittels eines reversierbaren Stellgetriebes zwischen einer Minimallaststellung und einer Vollaststellung schwenkbar antreibbar ist, mit einer als Drehfeder ausgebildeten, vorgespannten Rückstellfeder, die die Stellwelle in Minimallastrichtung beaufschlagt und einer Notlauffeder, durch die die Stellwelle in Vollastrichtung bis zu einer Notlaufstellung bewegbar ist, dadurch gekennzeichnet, daß die Rücklauffeder und die Notlauffeder durch eine einzige Drehfeder (18) gebildet sind, deren erstes Ende mit der Stellwelle (2) verbunden ist und deren anderes Ende (12) zwischen der Notlaufstellung und der Minimallaststellung mittels eines mit dem Stellgetriebe (5) gekoppelten Minimallastgetriebes (20) entgegen der Kraft der Drehfeder (18) bewegbar ist.1.Load adjusting device for an actuator determining the performance of an internal combustion engine, in particular in the form of a throttle valve, arranged on an actuating shaft, the actuating shaft being pivotably drivable between a minimum load position and a full load position by means of a reversible actuating part by means of a reversible actuating gear, with a torsion spring trained, preloaded return spring which acts on the actuating shaft in the minimum load direction and an emergency running spring, by means of which the actuating shaft can be moved in full load direction up to an emergency running position, characterized in that the return spring and the emergency running spring are formed by a single torsion spring (18), the first end of which is connected to the control shaft (2) and the other end (12) of which can be moved between the emergency running position and the minimum load position by means of a minimum load gear (20) coupled to the control gear (5) against the force of the torsion spring (18) is.
2. Lastverstellvorrichtung nach Anspruch 1 , dadurch gekennzeichnet, daß das zweite Ende (12) der Drehfeder (18) zwischen der Notlaufstellung und der Vollaststellung an einem Anschlag (13) anliegt und zwischen der Notlaufstellung und der Minimallaststellung von dem Anschlag (13) wegbewegbar ist.2. Load adjusting device according to claim 1, characterized in that the second end (12) of the torsion spring (18) bears against the stop (13) between the emergency running position and the full load position and can be moved away from the stop (13) between the emergency running position and the minimum load position .
3. Lastverstellvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Stellteil (4) ein zum Kämmen mit einem Zahnrad (9) des Stellgetriebes (5) ausgebildetes Zahnsegment (3) hat.3. Load adjusting device according to claim 1 or 2, characterized in that the actuating part (4) has a toothed segment (3) designed for meshing with a gear (9) of the actuating gear (5).
4. Lastverstellvorrichtung nach zumindest einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Stellgetriebe (5) ein von einem Antriebsritzel (7) angetriebenes, durchmessergroßes Zwischenzahnrad (8) hat, welches mit einem das Stellteil (4) verschwenkenden, durchmesserkleinen Zahnrad (9) drehfest und koaxial verbunden ist. 4. Load adjusting device according to at least one of the preceding claims, characterized in that the actuating gear (5) has a large-diameter intermediate gear (8) driven by a drive pinion (7), which has a small-diameter gear (9) which pivots the actuating part (4). is rotatably and coaxially connected.
5. Lastverstellvorrichtung nach zumindest einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß auf dem Zwischenzahnrad (8) ein Nocken (10) zum Bewegen des zweiten Endes (12) der Drehfeder (18) angeordnet ist.5. Load adjusting device according to at least one of the preceding claims, characterized in that a cam (10) for moving the second end (12) of the torsion spring (18) is arranged on the intermediate gear (8).
6. Lastverstellvorrichtung nach zumindest einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Drehfeder (18) eine Spiralfeder ist.6. Load adjusting device according to at least one of the preceding claims, characterized in that the torsion spring (18) is a spiral spring.
7. Lastverstellvorrichtung nach zumindest einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß in dem das Zwischenzahnrad (8) lagernden Gehäuse (1 ) ein seitlich an der Drehfeder anliegendes Führungsteil (19) befestigt ist.7. Load adjusting device according to at least one of the preceding claims, characterized in that in the intermediate gear (8) bearing housing (1) is attached to the side of the torsion spring guide member (19).
8. Lastverstellvorrichtung nach zumindest einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß eine in Minimallaststellung und in Vollaststellung gegen gehäusefeste Anschläge (15) gelangende Anschlagplatte (14) drehfest auf der Stellwelle (2) befestigt ist.8. Load adjusting device according to at least one of the preceding claims, characterized in that a stop plate (14) reaching in minimum load position and in full load position against housing-fixed stops (15) is fixed in a rotationally fixed manner on the adjusting shaft (2).
9. Lastverstellvorrichtung nach zumindest einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Stellteil (4) und die Anschlagplatte (14) einteilig gefertigt sind. 9. Load adjusting device according to at least one of the preceding claims, characterized in that the actuating part (4) and the stop plate (14) are made in one piece.
EP98946329A 1997-08-22 1998-08-13 Load setting device Expired - Lifetime EP1005608B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19736521 1997-08-22
DE19736521A DE19736521A1 (en) 1997-08-22 1997-08-22 Throttle control unit for induction system of internal combustion engine
PCT/EP1998/005148 WO1999010642A1 (en) 1997-08-22 1998-08-13 Load setting device

Publications (2)

Publication Number Publication Date
EP1005608A1 true EP1005608A1 (en) 2000-06-07
EP1005608B1 EP1005608B1 (en) 2003-04-09

Family

ID=7839807

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98946329A Expired - Lifetime EP1005608B1 (en) 1997-08-22 1998-08-13 Load setting device

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Country Link
US (1) US6360718B1 (en)
EP (1) EP1005608B1 (en)
KR (1) KR20010023052A (en)
BR (1) BR9811347A (en)
DE (2) DE19736521A1 (en)
WO (1) WO1999010642A1 (en)

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Publication number Priority date Publication date Assignee Title
WO2001029382A1 (en) * 1999-10-15 2001-04-26 Siemens Canada Limited Electronic throttle control linkage with limp home mechanism
US20010035508A1 (en) * 2000-04-17 2001-11-01 Zhouxuan Xia Return spring and adjusting mechanism for an automotive throttle body
DE10137026A1 (en) 2001-07-30 2003-02-20 Siemens Ag Drive device for setting drive has intermediate gear composed of pinion and gear wheel
JP3750934B2 (en) * 2002-02-25 2006-03-01 三菱電機株式会社 Inlet throttle device
US6683429B2 (en) * 2002-04-24 2004-01-27 Borgwarner Inc. Electric positional actuator
JP4055547B2 (en) * 2002-10-25 2008-03-05 株式会社デンソー Electronically controlled throttle control device
DE602004021641D1 (en) * 2003-03-07 2009-07-30 Denso Corp Electronic throttle control device
DE10319882A1 (en) * 2003-05-03 2004-11-18 Daimlerchrysler Ag Power controller with fail-safe device
DE102005062467B4 (en) * 2005-12-27 2017-02-09 Robert Bosch Gmbh Actuator for an actuator
DE102008053570B4 (en) * 2008-10-15 2010-07-08 Bühler Motor GmbH Actuator, in particular for actuating an exhaust gas recirculation valve
JP5357105B2 (en) * 2010-05-19 2013-12-04 株式会社デンソー Throttle device

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US5492097A (en) * 1994-09-30 1996-02-20 General Motors Corporation Throttle body default actuation
DE19524941B4 (en) * 1995-07-08 2006-05-18 Siemens Ag load adjusting
DE19612869A1 (en) 1996-03-30 1997-10-02 Bosch Gmbh Robert Control device for controlling a power of an engine

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See references of WO9910642A1 *

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WO1999010642A1 (en) 1999-03-04
DE19736521A1 (en) 1999-02-25
EP1005608B1 (en) 2003-04-09
KR20010023052A (en) 2001-03-26
DE59807892D1 (en) 2003-05-15
US6360718B1 (en) 2002-03-26
BR9811347A (en) 2000-09-12

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