EP0381050A1 - Gashebel mit zweifacher Sicherheitsstellung - Google Patents

Gashebel mit zweifacher Sicherheitsstellung Download PDF

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Publication number
EP0381050A1
EP0381050A1 EP90101476A EP90101476A EP0381050A1 EP 0381050 A1 EP0381050 A1 EP 0381050A1 EP 90101476 A EP90101476 A EP 90101476A EP 90101476 A EP90101476 A EP 90101476A EP 0381050 A1 EP0381050 A1 EP 0381050A1
Authority
EP
European Patent Office
Prior art keywords
throttle
lever
link
breakover
shaft
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
EP90101476A
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English (en)
French (fr)
Other versions
EP0381050B1 (de
Inventor
Tibor J Villanyi
Kevin W Westerson
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.)
Cummins Inc
Original Assignee
Cummins Engine Co Inc
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 Cummins Engine Co Inc filed Critical Cummins Engine Co Inc
Publication of EP0381050A1 publication Critical patent/EP0381050A1/de
Application granted granted Critical
Publication of EP0381050B1 publication Critical patent/EP0381050B1/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
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/04—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by mechanical control linkages

Definitions

  • the present invention relates generally to throttle levers and specifically to a heavy duty throttle lever having a dual acting - double breakover capability that enhances the reliability of the throttle lever.
  • Throttle operating devices have long been employed in automotive and other vehicular internal combustion engines. These operating devices typically include a throttle lever attached to a throttle shaft and operatively connected to an associated throttle control linkage.
  • the throttle control linkage is operatively connected to a foot-operated throttle pedal or "accelerator” or to another type of operator-actuated throttle control element within the vehicle's passenger compartment. This permits the operator to control the action of a fuel supply system, such as a fuel injection system or throttle valve through the throttle control linkage and associated throttle lever simply by pressing down or releasing the throttle pedal or by moving the throttle control element.
  • Throttle levers are normally arranged to move between two positions: an idle position wherein sufficient fuel is supplied to the engine so that it will run at a predetermined idling speed, and a full throttle position wherein a maximum amount of fuel is supplied to the engine.
  • the idle and full throttle positions are normally defined by adjustable stops.
  • a return spring is typically used to bias the throttle lever to the setting required to maintain a preset engine idle speed when pressure on the throttle pedal is released or when the throttle control is fully retracted.
  • Two part throttle levers one part of which is pivotally mounted with respect to the other to form a lever link, are normally used to provide the breakover function.
  • the lever link is able to move or "break over" independently of the throttle lever when conditions require breakover capability.
  • a torsion spring is typically provided on the throttle lever to urge the lever link toward its normal position and to return the lever link to its normal position upon release of the breakover causing force.
  • Some type of stop structure may also be provided to limit breakover travel.
  • a throttle return system including a two part lever and a coiled safety spring, which returns a throttle valve to the desired idle setting in the event of a failure of either the throttle return spring or the associated throttle control linkage.
  • a stop structure on one of the lever sections prevents travel of this lever section in the event of a failure of the safety spring.
  • this stop structure also holds one end of the coiled safety spring. Consequently, the stop is under constant pressure from the spring and is, therefore, susceptible to breakage. If the stop breaks, it can no longer hold the safety spring, which, in turn, can no longer provide the safety function it was intended to provide.
  • One known throttle lever design includes a one way breakover mechanism to permit over travel of the throttle linkage when the throttle shaft reaches its full throttle position.
  • This known design includes a torsion spring for biasing the link lever toward its normal operating position and for transmitting the spring biasing force to the link lever.
  • a stop pin, mounted on the link lever, is arranged to be engaged by one end of the torsion spring and to form a stop to define the normal operation position of the link lever relative to the throttle lever.
  • This throttle lever design has some limitations, however. It can be installed by the end user in a way that may overstress the throttle lever torsion spring and cause it to break.
  • the stop pin holds the spring and is subject to the same constant stresses which under certain conditions can lead to premature breakage of the stop pin. Breakage of the stop pin results not only in the loss of spring function but can also result in loss of control by a human operator over the position of the throttle shaft.
  • the prior art therefore, has failed to provide a reliable, heavy duty throttle lever assembly for an internal combusion engine including substantially failure-proof structure capable of performing a double breakover function to maintain throttle control in the event of a failure of the throttle lever torsion spring or any of the associated throttle lever linkage structures.
  • a primary object of the present invention to overcome the disadvantages of the prior art and to provide a substantially failure-proof dual action - double breakover throttle lever assembly capable of reliably controlling throttle function in heavy duty internal combusion engine applications.
  • Still another object of the present invention is to provide a throttle lever assembly for operating a rotatable throttle shaft between idle and full throttle positions including a link lever and means for affording a first breakover function beyond the full throttle position of the throttle shaft and a second breakover function in the return direction past the idle position of the throttle shaft wherein stop means are provided to limit the rotational displacement of the link lever relative to the throttle lever and further wherein spring biasing means are provided separate from the stop means to exert force on the lever link to return to its non-breakover position.
  • a throttle lever assembly for an internal combustion engine fuel system having a throttle shaft rotatable between an idle position and a full throttle position wherein the throttled lever assembly includes a throttle lever connected to the throttle shaft to move the shaft between the idle position and the full throttle position in response to movement of a throttle control.
  • a throttle link means operatively connects the throttle lever and the throttle control to limit the degree of force that may be applied to the throttle lever means when the throttle shaft reaches either the idle or full throttle positions.
  • the throttle link means includes a link lever pivotally connected to the throttle lever and a spring biasing means for urging the link lever toward a normal operating position relative to the throttle lever.
  • Throttle link stop means limit the rotational displacement of the link lever relative to the throttle lever independently of the spring biasing means. The limited displacement permits continued control over the throttle shaft by the throttle operator even when the spring biasing means ceases to function.
  • the throttle link stop means include a first stop surface formed on the link lever near the throttle shaft and is positioned to engage the throttle shaft to define a first breakover limit position when the link lever is rotated in a first direction.
  • the throttle link stop means further includes a second stop surface on the link lever positioned to engage the throttle shaft to define a second breakover limit position when the link lever is rotated in a second direction opposite to the first direction.
  • the spring biasing means is mounted on the throttle lever and engages tabs on the the link lever and throttle lever that are entirely separate from the throttle link stop means.
  • Figure 1 discloses a known type of internal combustion engine throttling system which includes a throttle shaft 20 rotatably mounted within a throttle sleeve (not illustrated) contained within the housing of the engine fuel pump 12.
  • a throttle shaft 20 rotates within the throttle sleeve, fuel ports (not illustrated) in both structures move from (1) an idle condition in which the ports are substantially misaligned to cause only minimal fuel flow into the engine into (2) a full throttle condition in which the ports are substantially aligned to cause maximum fuel flow into the engine.
  • the throttle shaft 20 includes a stop element 18 mounted thereon for rotation with the throttle shaft.
  • Stop element 18 is designed to limit the rotation of the throttle shaft between an adjustable full throttle position wherein the ports are substantially fully aligned and maximum fuel flow is possible and an adjustable idle position, wherein the ports are substantially misaligned and only a small quantity of fuel can flow through the ports.
  • the precise limits of rotation of the throttle shaft can be set by adjusting threaded stops 14 and 16, respectively, provided on the fuel pump housing 12.
  • a throttle lever 22 is mounted on the throttle shaft 20 to rotate the throttle shaft 20 in response to forces exerted on the throttle lever 22 by the engine throttle control (i.e., an accelerator pedal, not illustated) and throttle return spring 34.
  • the throttle lever 22 is attached to the throttle shaft 20 by a nut and bolt assembly 24 so that rotation of the throttle lever 22 rotates the throttle shaft 20 between the full throttle and idle positions.
  • a throttle linkage member 32 connected between the throttle control and the throttle lever 22, causes the throttle lever 22 to move the throttle shaft 20 to the full throttle position.
  • the throttle return spring 34 then causes the throttle lever 22 to move the throttle shaft 20 to the preset idle position.
  • the breakover mechanism includes a link lever 26 pivotally connected at one end to the throttle lever 22 by pivot pin 28.
  • the other end of the throttle link lever 26 is attached a connector 30 which is, in turn, connected to a linkage member 32.
  • the linkage member 32 provides the operative connection between the throttle link lever 26 and the throttle control (now shown).
  • this end of the throttle link lever 26 is also connected to the vehicle throttle return spring 34.
  • the throttle return spring 34 returns the throttle shaft 20 from the full throttle position shown in Figure 1 to the idle position (not shown), wherein side 21 of the stop element 18 contacts the idle adjustment screw 14.
  • a torsion spring 36 is coiled around the pivot pin 28.
  • One end 38 of the spring 36 engages a stop pin 40, which is attached to the throttle link lever 26.
  • the stop pin 40 also functions to define the normal operating relationship of the throttle and link levers and to transmit force from the return spring to the throttle shaft 20 through the link lever 26 and throttle lever 27.
  • the breakover mechanism allows adjustment in the full throttle position without creating the possibility that excessive force will be applied to the throttle lever.
  • the throttle link lever 26 can assume is shown in dashed lines in Figure 1.
  • the throttle shaft 20 is in the full throttle position; however, the link lever 26 has rotated out of alignment with the throttle lever 22.
  • the breakover mechanism allows the throttle shaft stop element 18 to move until it contacts the full throttle fuel adjusting screw 16.
  • the throttle link lever 26 is capable of continued pivotal movement independent of the movement of the throttle shaft 20. This movement will not affect the fueling, and the throttle shaft 20 will remain in the position shown in Figure 1 without any increase in fueling.
  • the torsion spring 36 is coiled and positioned on the throttle lever assembly to urge the link lever 26 back into the normal position whenever the human operator causes the throttle control to return toward the idle position. The breakover mechanism, thus, allows adjustment in the full throttle position without creating the possibility that excessive force can eb applied to the throttle lever.
  • the throttle lever assembly of the present invention overcomes these problems.
  • the present throttle lever assembly provides dual acting, double breakover elements that are formed integrally with the components of the throttle lever assembly.
  • all of the components of the assembly are preferably made of stainless steel so that corrosion, which is a common cause of the failure of currently available throttle lever assemblies, is not a problem.
  • the assembly of the present invention 50 is mounted on a throttle shaft 52 of the type described above and includes a U-shaped throttle lever 54 mounted on the throttle shaft by a nut and bolt assembly 53.
  • One leg of the throttle lever 54 terminates in an integrally formed projection or tab 55 which extends substantially prependicularly to one surface of the throttle lever 54.
  • a throttle link lever 56 and a link spacer 58 are pivotally secured together between the legs of the throttled lever by means of a rivet 60.
  • the link lever 56 is flat and significantly longer than link spacer 58.
  • the link spacer 58 terminates in a projection or tab 57 that extends outwardly of the surface of the link spacer 58 and through an opening 62 in the link lever 56 so that it is substantially parallel to tab 55.
  • the link spacer 58 is used to move the link lever 56 relative to the throttle lever 54, as will be described hereinbelow.
  • Rivet 60 is formed as a projection from a pivot pin 63 having a larger diameter outer section 64 and an end cap 66.
  • Pivot pin 63 mounts the link lever 56 and the link spacer 58 for pivotal movement relative to the throttle lever 54.
  • the "sandwiching" of the link lever and link spacer within the legs of the throttle lever 54 and the securing of the link lever 56 and link spacer 58 permanently with rivet 60 has been found to provide maximum support to the moving link against side loading forces. This also causes the link lever 56 and link spacer 58 to pivot in unity about the throttle lever pivot pin 63 relative to the throttle lever 54 in a manner which will be described in detail hereinbelow.
  • the terminus 68 of the throttle link lever 58 is connected through a suitable connector linkage (not shown) to the vehicle throttle control (not shown) and to the throttle return spring (not shown).
  • a torsion spring 70 is coiled about the throttle lever pivot pin outer section 64 between the end cap 66 and one leg of throttle lever 54 to bias the throttle lever 54, link lever 56 and link spacer 58 so that they are axially aligned in a breakover resist or normal operating position.
  • the ends 71 and 72 of the spring 70 engage stop tabs 55 and 57, thereby tending to urge the throttle lever 54, the link lever 56 and the link spacer 58 toward a normal operating position wherein these structures are substantially aligned, as shown in Figures 3, 4 and 6.
  • one leg of the throttle lever 54 terminates in an integrally formed projection or stop tab 55.
  • This tab is stationary and does not move relative to pivot pin 63, whereas tab 57 on the link spacer 58 is movable with link lever 56 relative to stop tab 55.
  • Figures 4 and 5 illustrate in more detail the additional features of the throttle lever assembly 50 and, in particular, of link lever 56 that provide the unique dual action-double breakover function of the present invention.
  • the end 74 of link lever 56 opposite the terminus 68 has a configuration specifically designed to limit the extent of the movement of the link lever relative to the throttle shaft 52 in a manner to be explained in detail in connection with Figures 5a-c.
  • the end 74 of the link lever 56 includes a central notch 76 which functions as a breakover limit mark.
  • curved surface 78 and 80 On each side of the central notch are curved surface 78 and 80, each of which forms an integral breakover stop 82 and 84. Because breakover stops 82 and 84 are formed integrally with the link lever 56, they are not subject to malfunctions should any part of spring 70 or tabs 55 or 57 become inoperable.
  • FIGS 5a, 5b and 5c illustrate the manner in which the stops 82 and 84 limit the breakover travel of throttle link lever 56 (illustrated in dashed lines).
  • the notch 76 facilitates the proper setting of the breakover travel limit. This is done by moving the link lever 56 longitudinally along its axis either toward or away from the throttle shaft 52.
  • the link spacer 58 can be employed to move the link lever 56 as required for the proper setting. Since the link lever 56 and spacer 58 are secured together, movement of the stop tab 57 in the opening 62 will also move the link lever 56.
  • the correct breakover setting is generally reached when the notch 76 can no longer be seen behind the throttle lever 54.
  • the breakover zone may be set to limit the link lever lateral travel anywhere from 0 degrees to about 22 degrees from the longitudinal axis of the link lever 56. In most circumstances, it will be desirable to set the limit of breakover travel such that the breakover limit is typically not reached even when the throttle lever is in its idle or full throttle position so long as the spring biasing mechanism is functioning properly.
  • Figures 5a, 5b and 5c show the maximum breakover travel zone of about 22 degrees relative to the throttle shaft 52 in either direction from notch 76.
  • the link lever 56 is shown in Figure 5a aligned in the normal operating position. In this orientation of link lever 56, breakover stops 82 and 84 do not contact the throttle shaft 52. However, should spring 70 fail for any reason the link lever 56 is limited in the rotational distance it can travel in either direction. The double curved configuration of the end 74 of the link lever 56 will stop the travel of the link lever. In particular, as illustrated in Figure 5b, rotation of link lever 26 in the counterclockwise direction will cause stop 84 to contact throttle shaft 52 and prevent the link lever 56 from traveling further. If the link lever travels in the opposite direction, as illustrated in Figure 5c, the opposite stop 82 will contact the throttle shaft, thereby limiting travel in this direction as well.
  • stops 82 and 84 Forming the surfaces of stops 82 and 84 with a radius of curvature that approximates that of the throttle shaft insures that a substantial portion of each surface and not just a contact line will contact with the throttle shaft, thereby providing a stronger, more positive contact and further reducing the likelihood of breakage. Moreover, since the stops 82 and 84 can contasct the throttle shaft during engine operation even when the spring 70 is fully operative, they prevent the spring from being overstressed during normal operation of the throttle assembly.
  • the throttle lever assembly 50 of the present invention functions to rotate the throttle shaft 52 between full throttle and idle positions in response to movement of the engine throttle control as described above in connection with Figure 1.
  • the present throttle lever provides a greatly improved, substantially failure-proof breakover mechanism that effectively prevents the occurrence of a "uncontrolled" throttle.
  • the link lever 56 includes integrally formed breakover stop tabs 82 and 84 which curve outwardly from a central notch 76. The breakover stops 82 and 84 will make contact with the throttle shaft only upon reaching the limit of travel in either breakover direction. Thus, excessive rotational displacement in the breakover mode is avoided.
  • the breakover function will continue even if the torsion spring breaks or tabs 55 and 57 become inoperative for any reason.
  • FIGS. 6, 7 and 8 illustrate, respectively, the normal operating, idle breakover, and full throttle breakover positions of the present throttle lever assembly.
  • Figure 6 shows the throttle layer 54 and the link lever 56 axially aligned in a normal operating idle position as the assembly is mounted on a fuel pump 86.
  • a stop element 88 mounted on the throttle shaft 52 contacts the fuel pump idle adjustment screw 90.
  • a connector 92 is secured to link lever 56 and to a linkage element 94, which is operatively connected to a throttle control (not shown).
  • Throttle return springs 96 provide return force tending to move the throttle shaft to its idle position.
  • the ends 71,72 of torsion spring 70 engage stop tabs 55,57, which are substantially parallel to each other.
  • Figure 6 illustrates the relative positions occupied by all of the components in the present throttle lever assembly when the throttle shaft is in the preset idle position and a predetermined minimum amount of fuel flow is allowed.
  • FIG. 7 illustrates the present throttle lever assembly in a idle breakover position.
  • the throttle stop element 88 contacts the idle adjustment screw 90, thereby holding the throttle shaft 52 in the preset idle position.
  • sufficient force has been exerted on the lever link 56 to cause the lever assembly to "break over" and move out of axial alignment with the throttle lever 54.
  • the stationary stop tab 55 on the throttle lever 54 continues to engage end 71 of spring 70.
  • stop tab 57 on the link spacer moves with the link lever, thereby moving spring end 72 and tensioning the spring 70.
  • link lever 56 Because the maximum breakover movement of link lever 56 is limited by the link breakover stop 82, the link lever 56 and, therefore, the stop tab 55 can move only that distance allowed by the travel of the breakover stop 82 until it contacts the throttle shaft 52. Consequently, the maximum possible tension on spring 70 caused by the idle breakover is limited.
  • FIG 8 illustrates the present throttle lever assembly in a full throttle breakover position.
  • the throttle stop 88 contacts the full throttle adjustment screw 98 to allow maximum fuel flow through the throttle shaft and fuel pump.
  • the throttle lever maintains the throttle shaft in this position while the link lever is able to "break over" limited only by the breakover stop 84 which contacts the throttle shaft.
  • Stop tab 55 is moved out of alignment with stationary stop tab 57 to tension end 72 of spring 70. Spring end 71 contacts stop tab 57.
  • tension on the spring 70 is limited since the extent of the movement of the movable stop tab 55 is substantially the same as that of the link lever 56. If the breakover stop did not limit this movement, the tab 55 might move the spring ends 71 and 72 far enough to place the spring 70 under undesirably high stress.
  • the breakover stop 84 on the link lever 56 will still cause the throttle shaft 52 to respond to movement of the throttle control.
  • the vehicle return springs 96 ( Figure 8) are also able to return the throttle lever 56 to the idle position because the breakover stop 82 on the link lever 56 will contact the throttle shaft 52, thereby limiting the rotational movement of the lever link 56 relative to the throttle lever 54 and causing the throttle lever 54 to rotate the throttle shaft to its idle position.
  • the integrally formed stop tabs or projections 55 and 57 of the present invention are more like to remain in place and will not fall out of the throttle lever link. Additionally, these stop tabs 55 and 57 are not as susceptible to breakage from the tension placed on them by spring 70.
  • the spring 70 can be coiled to a desired torsion strength before installation on the pivot pin section 64. Because the relative movement of the stop tabs 55 and 57 holding the ends of the springs is limited by the breakover travel of the throttle lever link as discussed above, the additional stress placed on the spring by this movement is held within predetermined maximum limits. Consequently, overstressing of the torsion spring 70 should not occur with the present invention, which further enhances the reliability of this throttle lever assembly.
  • the present throttle lever assembly moreover, requires only five separate components to achieve its virtually failure-proof control of engine throttling.
  • the currently available throttle levers include many more components and, as discussed above, do not provide the virtually failure proof measure of control over engine throttling achieved by the present design.
  • throttle lever assembly 50 Because, as stated above, all of the individual components of throttle lever assembly 50 are fabricated from stainless steel, corrosion of these components in the hostile environment encountered in an internal combustion engine will not occur. Consequently, their useful life is long, which further increases the reliability of the dual acting - double breakover throttle lever of the present invention. Bench tests have demonstrated, moreover, that the throttle lever assembly of the present invention has a life cycle in excess of one million miles.
  • the dual acting - double breakover throttle lever assembly of the present invention will find its primary application as a component of an internal combustion engine in which reliable maximum control over throttling function is desired.

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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)
EP19900101476 1989-01-25 1990-01-25 Gashebel mit zweifacher Sicherheitsstellung Expired - Lifetime EP0381050B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US30105789A 1989-01-25 1989-01-25
US301057 1999-04-28

Publications (2)

Publication Number Publication Date
EP0381050A1 true EP0381050A1 (de) 1990-08-08
EP0381050B1 EP0381050B1 (de) 1994-06-08

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19900101476 Expired - Lifetime EP0381050B1 (de) 1989-01-25 1990-01-25 Gashebel mit zweifacher Sicherheitsstellung

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EP (1) EP0381050B1 (de)
JP (1) JP2593947B2 (de)
DE (1) DE69009508T2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0718141A1 (de) * 1994-12-23 1996-06-26 FIAT AUTO S.p.A. Pedalbetätigungsvorrichtung zur Steuerung des Bowdenzugs der Drosselklappe einer Brennstoffzufuhrvorrichtung für Brennkraftmaschine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0447147U (de) * 1990-08-23 1992-04-22

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3698372A (en) * 1971-06-08 1972-10-17 Holley Carburetor Co Throttle return spring redundancy system
US3699943A (en) * 1971-06-07 1972-10-24 Philip V Eshelman Throttle return spring redundancy system
US3760786A (en) * 1972-12-01 1973-09-25 Colt Ind Operating Corp Redundant throttle return system
FR2211978A6 (de) * 1972-12-27 1974-07-19 Peugeot & Renault
US3943907A (en) * 1973-10-19 1976-03-16 Societe Industrielle De Brevets Et D'etudes S.I.B.E. Throttle return systems for carburettors
DE3620738A1 (de) * 1986-06-20 1987-12-23 Opel Adam Ag Vorrichtung zur betaetigung des getriebezuges eines automatischen getriebes

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5127454Y2 (de) * 1971-05-13 1976-07-12
JPS5230688Y2 (de) * 1971-07-12 1977-07-13

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3699943A (en) * 1971-06-07 1972-10-24 Philip V Eshelman Throttle return spring redundancy system
US3698372A (en) * 1971-06-08 1972-10-17 Holley Carburetor Co Throttle return spring redundancy system
US3760786A (en) * 1972-12-01 1973-09-25 Colt Ind Operating Corp Redundant throttle return system
FR2211978A6 (de) * 1972-12-27 1974-07-19 Peugeot & Renault
US3943907A (en) * 1973-10-19 1976-03-16 Societe Industrielle De Brevets Et D'etudes S.I.B.E. Throttle return systems for carburettors
DE3620738A1 (de) * 1986-06-20 1987-12-23 Opel Adam Ag Vorrichtung zur betaetigung des getriebezuges eines automatischen getriebes

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0718141A1 (de) * 1994-12-23 1996-06-26 FIAT AUTO S.p.A. Pedalbetätigungsvorrichtung zur Steuerung des Bowdenzugs der Drosselklappe einer Brennstoffzufuhrvorrichtung für Brennkraftmaschine

Also Published As

Publication number Publication date
JPH02245432A (ja) 1990-10-01
EP0381050B1 (de) 1994-06-08
DE69009508T2 (de) 1994-09-22
DE69009508D1 (de) 1994-07-14
JP2593947B2 (ja) 1997-03-26

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