EP0989293B1 - Dispositif de commande de charge - Google Patents

Dispositif de commande de charge Download PDF

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Publication number
EP0989293B1
EP0989293B1 EP99118628A EP99118628A EP0989293B1 EP 0989293 B1 EP0989293 B1 EP 0989293B1 EP 99118628 A EP99118628 A EP 99118628A EP 99118628 A EP99118628 A EP 99118628A EP 0989293 B1 EP0989293 B1 EP 0989293B1
Authority
EP
European Patent Office
Prior art keywords
emergency
spring
load
return spring
actuating
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
EP99118628A
Other languages
German (de)
English (en)
Other versions
EP0989293A2 (fr
EP0989293A3 (fr
Inventor
Günther BENDER
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
Siemens 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 Siemens AG filed Critical Siemens AG
Publication of EP0989293A2 publication Critical patent/EP0989293A2/fr
Publication of EP0989293A3 publication Critical patent/EP0989293A3/fr
Application granted granted Critical
Publication of EP0989293B1 publication Critical patent/EP0989293B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • 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

Definitions

  • the invention relates to a load adjustment device according to the preamble of claim 1 for the performance of a Internal combustion engine determining, in particular designed as a throttle valve, actuator arranged on an actuating shaft, the actuating shaft via a non-rotatable actuator connected to it by means of a reversible Actuator between a minimum load position and a full load position is pivotally driven, with a preloaded return spring, which Actuating shaft loaded in the minimum load direction, and an emergency running spring which the control shaft can be moved in the full load direction up to an emergency running position is.
  • a Internal combustion engine determining, in particular designed as a throttle valve, actuator arranged on an actuating shaft, the actuating shaft via a non-rotatable actuator connected to it by means of a reversible Actuator between a minimum load position and a full load position is pivotally driven, with a preloaded return spring, which Actuating shaft loaded in the minimum load direction, and an emergency running spring which the control shaft can be moved in the full load direction up
  • US-A-5 735 243 shows one such Contraption.
  • a similar load adjustment device is known from EP 0 378 737 B1 known.
  • This load adjustment device has to drive the actuating gear an accelerator cable attached to an accelerator pedal and an electric motor.
  • the throttle cable pivots a first control element part connected to the actuating shaft, while the electric motor one with the first control element part coupled second control element part pivoted.
  • the dimensions of the Control element parts form the transmission ratio of the actuating gear.
  • the return spring moves the first control element part to the minimum load position, while the emergency running spring is arranged on the second control element part and the control shaft in the emergency running position when the electric motor is de-energized biases.
  • the return spring and the emergency spring are here as tension or Designed compression springs.
  • the emergency running position enables the motor vehicle drive out of a danger area when the load adjustment device due to a failure of the control electronics or the actuator can be adjusted by pressing the accelerator pedal.
  • the internal combustion engine has a sufficiently large torque to to move the motor vehicle at low speed.
  • a disadvantage of the known load adjustment device is that it is very requires large installation space. In particular by attacking the return spring and the run-flat spring on the control element parts are designed in radial direction of the control shaft very wide.
  • the invention is based on the problem of a load adjustment device type mentioned so that they are particularly inexpensive is to be assembled and requires particularly small radial dimensions.
  • the run-flat spring and the return spring are each designed as torsion springs and on the Actuator arranged opposite side of the actuating shaft.
  • the actuator does not need any vacancies for the Attack points of the two springs.
  • the actuator can be particularly make compact.
  • the design of the emergency running spring and the return spring each as torsion springs also leads to a reduction in Dimensions of the load adjustment device according to the invention in radial Direction of the control shaft.
  • the separation of the two springs from the actuator also leads to a particularly simple assembly of the invention Load adjusting.
  • the type of actuator drive is irrelevant here.
  • the actuating gear can, for example, also exclusively are driven by an electric motor.
  • the emergency running spring and the return spring could each be used, for example Spiral spring can be designed.
  • Spiral spring can be designed.
  • Load adjustment device carries an adjusting lever for the transmission of forces the return spring and the emergency running spring on the adjusting shaft.
  • the control lever can be positively connected to the actuating shaft, so that it at assembly can simply be plugged onto it.
  • a second control element part as in the known load adjustment device can be according to another advantageous development of the invention Simply avoid it if the emergency running spring is in the emergency running position on a house-fixed Stop and is at an angle of the control lever
  • a release of the return spring from the steep lever can be according to another simply avoid advantageous development of the invention if a Leg of the return spring is positively connected to the actuating lever. This reliably prevents the drive from failing of the actuating gear, the actuating shaft remains in the full load position.
  • the load adjustment device requires particularly little Actuating forces when the actuating lever is in an emergency position from the return spring has a bend biased against one leg of the emergency running spring. Because the return spring and the emergency spring for counter-tensioning the control shaft are arranged, is thereby between the emergency running position and the full load only the return spring in engagement with the Lever. Act between the emergency running position and the minimum load position the two springs opposed, so that here, too, particularly small Actuating forces for pivoting the actuating shaft are required.
  • Load adjustment device in the radial direction of the control shaft contributes when the emergency running spring and the return spring concentrically around a storage of the Control shaft are arranged.
  • Contamination of the end of the actuating shaft facing the springs can easy according to another advantageous development of the invention avoid if the emergency running spring and the return spring are in one of one Lid lockable shaft-like housing are arranged.
  • the emergency running spring could be arranged on the actuating lever in such a way that it when the control shaft is pivoted from the emergency running position in the direction the minimum load position is tensioned more than the return spring.
  • FIG. 1 shows a throttle valve connector 1 with an inventive one Load adjustment device 2 in longitudinal section.
  • a control shaft 4 penetrating a channel 3 is pivotably mounted.
  • On the control shaft 4 is a for controlling a free cross-sectional area of the Channel serving throttle valve 5 attached.
  • the control shaft 4 is one arranged in a pot-shaped housing 6 of the throttle valve connector 1 Actuator 7 pivoted.
  • Control electronics 8 for controlling an electric motor shown in Figure 2 9 arranged. With the electric motor 9, the actuating gear 7 can be drive and thus pivot the control shaft 4. Alternatively, it can Actuator 7 of course also in addition to the electric motor 9 or instead of being adjusted by a throttle cable, not shown.
  • the throttle valve connector 1 has two bearings 10 for the actuating shaft 4, 11 on. At the opposite end of the actuating gear 7 of the actuating shaft 4, an adjusting lever 12 is attached. To the storage 11 of this end of the Actuating shaft 4, an emergency running spring 13 and a return spring 14 are concentric arranged. The return spring 14 and the emergency running spring 13 are each designed as leg springs and arranged in a shaft-like housing 15. The housing 15 is closed by a cover 16.
  • FIG. 2 shows the throttle valve connector 1 from FIG. 1 in a sectional illustration along the line II - II.
  • the adjusting lever 12 is made as a sheet metal part and has bends 17, 18.
  • Each a leg 19, 20 of the emergency spring 13 and the return spring 14 are in the throttle body 1 attached.
  • One of the bends 18 is from behind a leg 21 of the return spring 14.
  • the other angle 17 bears against a second leg 22 of the emergency running spring 13.
  • the return spring 14 counteracts the actuating shaft 4 pivoted clockwise, while the emergency running spring 13 only in Clockwise acting forces can exert on the control shaft 4.
  • the Emergency running spring 13 Since the Emergency running spring 13 has a larger spring constant than the return spring 14, can the control shaft 4 of the return spring 14 only up to the drawn Be pivoted position in which one of the bends 17 of the control lever 12 rests on the emergency running spring 13. In this position the control shaft 4 the second leg 22 of the emergency running spring 13 is also at a stop 23 of the throttle valve connector 1, so that the actuating shaft 4 by the emergency running spring 13 cannot be adjusted further clockwise.
  • This position indicates the emergency running position of the load adjustment device 2, the is inevitably achieved when no actuating forces above that shown in Figure 1 Actuate actuator 7 on the actuating shaft 4. A deflection of the Actuator shaft 4 from the drawn emergency position is therefore only about Actuator 7 shown in Figure 1 possible.

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  • 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)

Claims (8)

  1. Dispositif de commande de charge permettant de contrôler un élément de réglage, qui contrôle la puissance d'un moteur à combustion, qui est notamment c onçu comme c lapet d'étranglement (5) et qui est monté sur un arbre de réglage (4), l'arbre de réglage (4) pouvant être entraíné et pivoté, sous l'action d'une pièce de réglage qui lui est fixée de telle sorte qu'elle ne peut pas riper en tournant, et au moyen d'un mécanisme de réglage (7) inversible, e ntre u ne p osition de charge minimum et u ne p osition de p leine charge, le dispositif de commande de charge ayant un ressort de rappel (14), soumis à une prétension qui tend à ramener l'arbre de réglage (4) dans le sens de la charge minimum, et un ressort de marche de secours (13), grâce auquel l'arbre de réglage (4) peut être déplacé dans le sens de la pleine charge jusqu'à une position de marche de secours, le ressort de marche de secours (13) et le ressort de rappel ( 14) étant c hacun c onçus comme ressorts de torsion et étant montés sur le côté de l'arbre de réglage opposé au mécanisme de réglage (7), caractérisé par le fait que le ressort de marche de secours (13) et le ressort de rappel (14) sont maintenus fixes par une extrémité et, par l'autre extrémité, sont articulés, entre la position de charge minimum et la position de marche de secours, sur un levier de commande (12) commun fixé à l'arbre de réglage (4) et que, entre la position de charge minimum et la position de pleine charge, seul le ressort de rappel (14) est articulé sur le levier de commande (12).
  2. Dispositif de commande de charge selon la revendication 1 caractérisé par le fait que le ressort de marche de secours (13) et le ressort de rappel (14) sont conçus comme deux ressorts à branches qui s'engagent l'un dans l'autre et qui soumettent chacun l'arbre de réglage (4) à une précontrainte inverse l'une par rapport à l'autre.
  3. Dispositif de commande de charge selon au moins l'une des revendications précédentes caractérisé par le fait que, dans la position de marche de secours, le ressort de marche de secours (13) est appliqué sur une butée (23) fixée au carter et sur un crochet (17) du levier de commande (12).
  4. Dispositif de commande de charge selon au moins l'une des revendications précédentes caractérisé par le fait qu'une branche (21) du ressort de rappel (14) est liée par engagement positif au levier de commande (12).
  5. Dispositif de commande de charge selon au moins l'une des revendications précédentes caractérisé par le fait que le levier de commande a un crochet qui est soumis par le ressort de rappel, dans la position de marche de secours, à une prétension contre une branche du ressort de marche de secours.
  6. Dispositif de commande de charge selon au moins l'une des revendications précédentes caractérisé par le fait que le ressort de marche de secours (13) et le ressort de rappel (14) sont montés d'une façon concentrique autour d'un palier (11) de l'arbre de réglage (4).
  7. Dispositif de commande de charge selon au moins l'une des revendications précédentes caractérisé par le fait que le ressort de marche de secours (13) et le ressort de rappel (14) sont montés dans un carter (15) en forme de puits pouvant être fermé par un couvercle (16).
  8. Dispositif de commande de charge selon au moins l'une des revendications précédentes caractérisé par le fait que le ressort de marche de secours (13) a une constante de rappel supérieure à celle du ressort de rappel (14).
EP99118628A 1998-09-24 1999-09-21 Dispositif de commande de charge Expired - Lifetime EP0989293B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843769 1998-09-24
DE19843769A DE19843769A1 (de) 1998-09-24 1998-09-24 Lastverstellvorrichtung

Publications (3)

Publication Number Publication Date
EP0989293A2 EP0989293A2 (fr) 2000-03-29
EP0989293A3 EP0989293A3 (fr) 2000-11-08
EP0989293B1 true EP0989293B1 (fr) 2004-07-21

Family

ID=7882062

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99118628A Expired - Lifetime EP0989293B1 (fr) 1998-09-24 1999-09-21 Dispositif de commande de charge

Country Status (4)

Country Link
EP (1) EP0989293B1 (fr)
KR (1) KR20000023458A (fr)
BR (1) BR9904314A (fr)
DE (2) DE19843769A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE60011065T2 (de) 1999-03-29 2005-01-27 Hitachi, Ltd. Elektronisch geregelte drosselklappe
DE10042577A1 (de) * 2000-08-30 2002-03-14 Siemens Ag Drosseleinrichtung mit Notlufteinrichtung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4207096A1 (de) * 1992-03-06 1993-09-09 Pierburg Gmbh Stellvorrichtung fuer eine drosselklappe einer brennkraftmaschine
DE4330198A1 (de) * 1993-09-07 1995-03-09 Pierburg Gmbh Drosselklappeneinrichtung für Brennkraftmaschinen
DE4337184A1 (de) * 1993-10-30 1995-05-04 Pierburg Gmbh Drosselklappenstutzen
JP3785209B2 (ja) * 1995-12-28 2006-06-14 株式会社ケーヒン 絞り弁制御装置
JPH102236A (ja) * 1996-06-17 1998-01-06 Aisan Ind Co Ltd スロットル弁制御装置

Also Published As

Publication number Publication date
KR20000023458A (ko) 2000-04-25
DE19843769A1 (de) 2000-03-30
EP0989293A2 (fr) 2000-03-29
EP0989293A3 (fr) 2000-11-08
DE59909996D1 (de) 2004-08-26
BR9904314A (pt) 2000-09-26

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