WO1997037116A1 - Steuereinrichtung zum steuern einer leistung einer antriebsmaschine - Google Patents
Steuereinrichtung zum steuern einer leistung einer antriebsmaschine Download PDFInfo
- Publication number
- WO1997037116A1 WO1997037116A1 PCT/DE1996/002220 DE9602220W WO9737116A1 WO 1997037116 A1 WO1997037116 A1 WO 1997037116A1 DE 9602220 W DE9602220 W DE 9602220W WO 9737116 A1 WO9737116 A1 WO 9737116A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- spring
- intermediate member
- stop
- control device
- end position
- Prior art date
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
Definitions
- Control device for controlling a power of an engine
- the invention is based on a control device for controlling an output of a drive machine according to the preamble of claim 1.
- a known control device (international patent application WO 88/02064) there is an adjusting element for controlling the power of a drive machine.
- the actuator has the shape of a throttle valve.
- the actuator can be adjusted using an actuator. If the actuator fails or the actuator is switched off, the actuator is in a rest position. The rest position is dimensioned so that emergency operation of the drive machine is possible.
- there is a return spring which acts on the actuating element in the direction of closing the suction channel.
- a second spring acting as an emergency running spring acts on this Control element in the direction of opening until the control element reaches the rest position. By means of a stop against which the second spring can come to rest, it is achieved that the second spring can only act on the actuating element up to the rest position.
- the known control device has the disadvantage that an additional, powerful spring is required, which has a negative effect on the production outlay and the size of the known control device.
- the control device according to the invention for controlling an output of a drive machine with the characterizing features of claim 1 has the advantage that the spring device can adjust the actuating element from the direction of the first end position as well as from the direction of the second end position into the rest position lying between the two end positions. This reduces the number of springs required, which advantageously significantly reduces the manufacturing outlay and the installation space required.
- control element and the intermediate element are rotatably or pivotably mounted and the effects of the spring device occur as torques, then can advantageously, the effects of the spring device can be adjusted very simply by simply tuning the radii.
- this gear stage increases the speed from the actuator in the direction of the intermediate member or idler gear
- this gear stage can advantageously as part of the translation of the speed of the actuator to the angular speed of the control element can also be used.
- the second spring linkage or the correspondingly shaped spring end of the spring device forming the second spring linkage comes into contact with the rest stop in the rest position, the number of components required is further advantageously reduced.
- the idle stop is set so that when the idle stop determines the position of the actuating element, the actuating element is in a position in which the prime mover operates in emergency operation, then this has the advantage that emergency operation of the prime mover is possible even if the actuator fails .
- the throttle valve also cannot freeze to the gas duct if the engine is parked for a longer period.
- FIGS. 1, 2, 3 and 6 show different exemplary embodiments in symbolic form and FIGS. 4, 5, 7 and 8 show different details and views of different exemplary embodiments.
- the control device can be used in any drive machine in which the power of the drive machine is to be controlled.
- the prime mover can either be stationary, or it can e.g. B. a self-propelled machine, ie a vehicle.
- the prime mover is, for example, an Otto engine with a suction channel.
- the actuator has the shape of a throttle valve, for example.
- the prime mover can also be a diesel engine, in which case the adjusting element is an adjusting lever for adjusting the Injection quantity of the injection pump can act.
- the prime mover can also be an electric motor. Then the actuating element is, for example, a lever with which the energization of the electric motor can be changed.
- control device according to the invention is installed in a vehicle with an Otto engine.
- FIG. 1 shows a first particularly selected exemplary embodiment in symbolic form.
- FIG. 1 shows a gas channel 2, an actuating element 4, an actuating lever 4a, a transmission ratio 6 of a transmission, a spring device 8 with a spring 8a, an intermediate member 10, a stop piece 12, a transmission ratio 14, an actuator 16, an electrical line 18 , a rest stop 20, a first end position stop 21 and a second end division diagram 22.
- the gas duct 2 leads, for example, from an air filter, not shown, to combustion chambers of the drive machine, not shown. Air or a fuel-air mixture flows through the gas channel 2, for example.
- the actuator 4 has the shape of a slide 4b.
- the free cross section of the gas channel 2 can be opened more or less with the slide 4b.
- an arrow 24 and an arrow 26 pointing in the opposite direction are shown.
- an adjustment of the actuating element 4 in the direction of the arrow 24 means an enlargement of the free cross section through the gas channel 2 and thus an increase in the power required by the drive machine. Adjustment in the direction of arrow 26 means reduction in the power of the drive machine.
- the actuator 16 is, for example, an electric motor, preferably a tendon-running DC motor.
- the actuator 16 can the intermediate member 10, the
- the spring 8a of the spring device 8 is connected directly to the actuating lever 4a of the actuating element 4 via a first spring linkage 31, and via a second
- the translation 6 is composed of a first gear stage 6a and a second gear stage 6b.
- a stop 32b which is operatively assigned to the second spring linkage 32
- a stop 10b which is operatively assigned to the intermediate member 10.
- the movable parts can perform straight-line movements.
- the control element 4 with the control lever 4a, the intermediate member 10 and the stop piece 12 can also be rotatably or pivotably mounted.
- the parts mentioned are rotatably mounted.
- the first gear stage 6a translates the rotational speed of the actuating lever 4a, which is connected in a rotationally fixed manner to the actuating element 4, into a rotational speed of the intermediate member 10.
- the first gear stage 6a is designed, for example, such that the intermediate member 10 rotates by four angular units (for example 4 °) when the Control lever 4a rotates by an angle unit (for example 1 °). This means that the translation of the speed from the control element 4 to the intermediate member 10 is one to four (1: 4).
- the gear stage 6a designed in this way the torque is reshaped such that the torque acting on the intermediate member 10 exerts a quarter (1/4) of that exerted on the actuating element 4 by the spring device 8 Torque is.
- the translation of the torque from the actuating element 4 to the intermediate element 10 is four to one (4: 1).
- the spring device 8 acts on the intermediate member 10 in the direction of the arrow 26 via the first spring linkage 31, the torque of the spring device 8 on the intermediate member 10 being increased by seventy-five percent (75%) to twenty-five percent (25th) through the first gear stage 6a %) is reduced.
- the second gear stage 6b can, for example, be designed such that the second gear stage 6b converts a pivoting movement of the stop piece 12 by four angular units (e.g. 4 °) into a pivoting movement of the intermediate member 10 by seven
- Angular units e.g. 7 °.
- the spring device 8 can act on the intermediate member 10 with fifty-seven percent (57%) via the second spring linkage 32, as long as the stop piece 12 has lifted off the rest stop 20 with its stop 32a.
- the actuator 16 If the actuator 16 is not energized, so no torque is exerted by the actuator 16, then the stop 32a of the stop piece 12 is at the rest stop 20 and the stop 10b is against the stop 32b. Then there is the control element 4, as well the other moving parts, in a rest position.
- the rest position is in an intermediate position between the first end stop 21 and the second end stop 22.
- the drawing shows the actuating element 4, as well as the other movable parts, in the rest position. Starting from the rest position, the actuator 16 can move the actuating element 4 in the direction of the arrow 24 to the end position stop 22, ie until the actuating lever 4a comes into contact with the second end position stop 22, and in the direction of the arrow 26 to
- the stop piece 12 has lifted off the rest stop 20 and the spring device 8 can, via the second spring linkage 32, on the intermediate member 10 in the direction of arrow 24 with the fifty-seven calculated as an example above Percent (57%) of the original torque act.
- the spring device 8 also acts via the first spring linkage 31 in the direction of arrow 26 on the intermediate member 10 with twenty-five percent (25%) of the original torque, so that a torque acting in the direction of arrow 24 acts on the intermediate member 10 as excess.
- the electric actuator 16 can, via the gear ratio 14, via the intermediate member 10, via the gear stage 6a, via the actuating lever 4a, the actuating element 4 starting from the rest position shown in FIG Adjust the direction of arrow 26 (to the left) as well as in the direction of arrow 24 (to the right) until the actuating element 4 at the first end stop 21 or the second
- the actuator 16 has the actuating element 4, starting from the rest position shown in FIG adjusted to the right, and then the actuator 16 is switched off or becomes ineffective due to a defect, then the spring device 8 adjusts the adjusting element 4 in the direction of the arrow 26 (to the left) until the stop 10b comes to rest against the stop 32b and until that Control element 4 is again in the rest position shown in Figure 1.
- Movements of the intermediate member 10 lead to corresponding movements of the actuating element 4.
- the movements of the actuating element 4 are directly coupled to the movements of the intermediate member 10 via the gear stage 6a.
- the gear stage 6a provides a translation between the movements of the adjusting element 4 and the movements of the intermediate member 10.
- FIG. 2 shows, in symbolic form, a further possibility, selected by way of example, for implementing the control device according to the invention.
- a pivoting movement of the stop piece 12 is transmitted one to one into a pivoting movement of the intermediate member 10 at the second gear stage 6b, which is why, in the case of the symbolic representation of FIG. 2, in the gear stage 6b that in the figure 1 box shown is not shown.
- the first gear stage 6a of the transmission ratio 6 is designed, for example, such that a pivoting movement of the actuating lever 4a by two angular units (e.g. 2 °) is converted into a rotary movement of the intermediate member 10 by five angular units (e.g. 5 °).
- FIG. 3 symbolically shows a further preferred embodiment of the control device according to the invention.
- the speed is not converted between the actuating lever 4a and the intermediate member 10.
- the first gear stage 6a is designed in such a way that a pivoting movement or a rotary movement of the actuating element 4 results in a pivoting movement or rotary movement of equal magnitude, i. H. one to one, is transferred to the intermediate member 10.
- the rectangular box symbolizing the first gear stage 6a in FIG. 1 is symbolically replaced by rectangular teeth, which is intended to symbolize that the control element 4 and the
- Intermediate member 10 are coupled to each other in terms of movement and the ratio is one to one.
- the gear stage 6b of the transmission 6 is designed, for example, such that a rotational movement of the stop piece 12 by two angular degrees (eg 2 °) results in a rotational movement of the intermediate member 10 by an angular unit (1 °).
- the spring device 8 acts on the intermediate member 10 via the second spring link 32 with two hundred percent (200%) of the torque generated by the spring device 8 (to the right). It looks to the left Spring device 8 via the first spring linkage 31 to the intermediate member 10 with one hundred percent (100%) torque. This has the effect, when the actuating element 4 is to the left of the rest position shown in FIG. 3, that the intermediate member 10 is from the
- FIGS. 4 and 5 show examples of details of how the exemplary embodiment shown in FIG. 1 in a more symbolic form can be implemented in practice.
- the actuator 4 comprises a throttle valve 4d and a throttle valve shaft 4w.
- the throttle valve 4d is firmly connected to the throttle valve shaft 4w via a fastening screw 4s.
- a toothed segment 4z is firmly connected to the throttle valve shaft 4w.
- Tooth segment 4z have the same function as the control lever 4a shown in FIG. 1 and the slide 4b attached to the control lever 4a.
- FIG. 4 shows a housing 36.
- the housing 36 preferably has the shape of a throttle valve connector and serves as a throttle valve connector.
- On the housing 36 is a Gear box 36r formed.
- the gear chamber 36r is covered by a cover 36d.
- the cover 36d belongs to the housing 36.
- the throttle valve shaft 4w is rotatably or pivotably mounted in the housing 36 via a bearing 34.
- the throttle valve shaft 4w has an axis of rotation 4x.
- In the housing 36 there is a recess 36a for receiving the bearing 34.
- the bearing 34 has an outer diameter which is matched to the recess 36a in such a way that the bearing 34 is rigidly connected to the housing 36 after it has been pressed into the recess 36a. As a result, the bearing 34 can hold the throttle valve shaft 4w both in the radial and in the axial direction.
- the bearing 34 is, for example, a plain bearing.
- the intermediate member 10 has the shape of a gearwheel with a first toothing 10g with a large radius and a second toothing 10k with a small radius.
- the intermediate member 10 is rotatably mounted on an axle 38 which is fixedly connected to the housing 36.
- the toothed segment 4z firmly connected to the throttle valve shaft 4w has an external toothing 4k.
- Adjusting the throttle valve 4d is usually 90 °, so that an angular arc of approximately 110 ° is usually sufficient for the external toothing 4k.
- the stop piece 12 has a through hole 12d.
- the stop piece 12 is by means of the through hole 12d on the throttle valve shaft 4w freely rotatable.
- the spring device 8 comprises a helically wound torsion spring 8d.
- the torsion spring 8d of the spring device 8 has a first spring end 8e acting on the toothed segment 4z and a second spring end 8f acting on the stop piece 12.
- the first spring linkage 31 is formed at the point where the spring end 8e engages the toothed segment 4z, and the second spring linkage 32 is located where the second spring end 8f engages the stop piece 12.
- the spring device 8 can be via the spring ends 8e and 8f exert a torque on the toothed segment 4z of the actuating element 4 and on the stop piece 12.
- the spring device 8 can also comprise two or three or more individual springs instead of just one torsion spring 8d. These several springs can be dimensioned such that if one of the springs fails, the rest of the springs are strong enough to return the actuating element 4 to the rest position.
- Spring device 8 the tooth segment 4z and an angle sensor 40.
- a part of the angle sensor 40 is firmly connected to the cover 36 and a part of the angle sensor 40 is located on the tooth segment 4z.
- the angle sensor 40 can sense the respective rotational position of the throttle valve 4d.
- the spring device 8 generates a torque about the axis of rotation 4x via the spring linkage 31 and via the toothed segment 4z on the actuating element 4 and an opposing torque via the second spring linkage 32 on the stop piece 12.
- the length of the torsion spring 8d is dimensioned such that the spring device 8 In addition to this torque, a force is generated 4x to the axis of rotation. This force tends to axially push the tooth segment 4z and the stop piece 12 apart. This will make it
- Stop piece 12 axially pressed against the bearing 34 firmly pressed into the housing 36 (to the left in FIG. 4).
- the spring device 8 presses the throttle valve shaft 4w to the right via the toothed segment 4z. To absorb this axial force
- Spring device 8 on the throttle valve shaft 4w is provided in the throttle valve shaft 4w with a recess 4e with an inserted locking washer 34a.
- the locking washer 34a is supported on the one hand on the edge of the recess 4e and on the other hand by the
- Spring device 8 axially pressed against the bearing 34 (to the right in FIG. 4). As already mentioned, the bearing 34 is firmly connected to the housing 36 by pressing. Due to the axial preload caused by the spring device 8 on the
- Throttle valve shaft 4w the throttle valve 4d is positioned exactly in the axial direction.
- the spring device 8 can serve both to generate a torque and to axially fix the throttle valve 4d with respect to the gas channel 2.
- FIG. 5 shows a view in the direction of an arrow shown in FIG. 4 and labeled V.
- the cover 36d and the housing 36 are not shown in FIG. 5.
- the housing 36 only the rest stop 20 molded onto the housing 36 and the end position stops 21 and 22 also molded onto the housing 36 are shown in FIG.
- the actuating movement of the actuating element 4 is limited in the direction of the arrow 24 when a stop provided on the toothed segment 4z comes to rest on the second end position stop 22 fixed to the housing.
- the rotational movement of the actuating element 4 in the direction of the arrow 26 is limited by a stop provided on the toothed segment 4z, which can come to rest on the first end position stop 21 fixed to the housing.
- the pivoting movement of the adjusting element 4 in the direction of the arrow 26 in that the throttle valve 4d (FIG. 4) starts on the gas channel 2. It is correspondingly the case in the exemplary embodiment shown in FIG. 1, in which the slide 4b corresponding to the throttle valve 4d strikes the gas channel 2 on movement in the direction of the arrow 26, at which the first end position stop 21 is located.
- the electric actuator 16 can adjust the toothed segment 4z of the adjusting element 4 in the direction of arrow 26 via the intermediate member 10 until the toothed segment 4z (FIG. 5) or the slide 4b (FIG. 1) or the throttle valve 4d at the first end position stop 21 Facility is coming. In the opposite direction (in the direction of arrow 24), the actuator 16 can rotate the actuating element 4 until the toothed segment 4z on the second
- the control device is preferably designed so that the prime mover operates with minimal power when the actuator 4 is at the first end stop 21 and when the actuator 4 is at the second end stop 22, then the prime mover operates at maximum power.
- the spring device 8 acts on the intermediate member 10 via the first spring linkage 31 via the external toothing 4k, and in addition the spring device 8 acts on the intermediate link 10 via the stop piece 12 via the stopper 32b
- Control element 4 in the direction of arrow 26 when the control element 4 is between the rest position shown and the second end position stop 22.
- the radius of the external toothing 4k (FIG. 5) is made four times as large as the radius of the toothing 10k, which is caused by the spring linkage 31 on the Intermediate member 10 gives a speed ratio of one to four (1: 4) or a torque ratio of four to one (4: 1). And one makes the radius of the stop 32b in relation to the radius of the stop 10b in a ratio of seven to four (7: 4), which is one of the second spring linkage 32 on the intermediate member 10
- the radius of the stop 10b is selected to be as large as the radius of the stop 32b, and the wheel s of the external toothing 4k is made two and a half (2.5) 3.1 as large like the radius of the toothing 10k.
- Actuator 16 via a toothed wheel 16a via the toothing 10g in active engagement with the intermediate member 10 and via the toothing 10k and the external toothing 4k in active engagement with the actuating element 4.
- an electric motor in particular a, is used for the actuator 16 DC motor, used at high speed.
- the speed of the actuator 16 is transmitted to the throttle valve shaft 4w over two stages.
- Gear ratio 14 is the first stage and gear stage 6a of gear ratio 6 is the second stage. Since the various gear stages of the control device embodied according to the invention can essentially also be used to reduce the high speed of the actuator 16 to a low speed of the throttle valve shaft 4w, the Control device overall requires few parts. There is the great advantage that the spring device 8, which can preferably consist of a single spring, the actuating element 4 in both directions of rotation, ie in the direction of the two arrows 24 and 26, in the
- FIGS. 6, 7 and 8 show examples of ways in which the stop piece 12 shown in FIGS. 1 to 5 can be dispensed with.
- FIG. 6 shows, in symbolic form, a further example of a particularly advantageous possibility for executing the control device according to the invention.
- the spring end 8f of the spring device 8 is formed in the region of the second spring link 32 so that the
- Spring end 8f when the actuating element 4 is in the rest position shown in the drawing, can rest against both the rest stop 20 and the stop 10b assigned to the intermediate member 10.
- the stop 10b lifts off the stop 32b provided at the spring end 8f, and the spring device 8 acts on the actuating element 4 in the direction of the first end position stop 21 (arrow 26 ).
- the spring link 32 is carried by the intermediate member 10 via the stops 10b, 32b in the direction of arrow 26, and the stop 32a at the spring end 8f of the spring device 8 lifts off the rest stop 20.
- the spring device 8 results in a resultant force or a resultant torque on the intermediate member 10 in the direction of the arrow 24. This resultant force or this resultant torque is transmitted from the intermediate member 10 to the actuating element 4.
- the spring device 8 thus acts in the direction of arrow 24 on the actuating element 4 until the actuating element 4 reaches the rest position shown in the drawing.
- FIG. 6 shows the further exemplary embodiment for the purpose of better understanding and larger
- FIG. 7 shows a cross section through another selected, particularly advantageous
- a shoulder 36e and a spring guide 36f are provided on the cover 36d.
- the spring device 8 can be supported on the shoulder 36e in the axial direction, so that the spring device 8 can exert a force on the throttle valve shaft 4w in the longitudinal direction to the axis of rotation 4x via the toothed segment 4z.
- the spring device 8 spans the
- Throttle valve shaft 4w firmly connected to the throttle valve 4d toothed segment 4z on the end against the bearing 34.
- the bearing 34 is a roller bearing which can transmit forces both in the radial direction and in the axial direction.
- the bearing 34 has an outer ring which is fixedly fixed relative to the housing 36.
- An inner ring of the bearing 34 guides the throttle valve shaft 4w in the radial direction.
- the outer ring can be fixed relative to the housing 36 by means of an appropriate press fit.
- the bent spring end 8e of the spring device 8 is suspended in a bore provided in the tooth segment 4z.
- the first spring linkage 31 is formed at this suspension point.
- FIG. 8 shows an end view of the control device.
- the direction of view assumed for FIG. 8 is indicated in FIG. 7 with an arrow marked VIII.
- FIG. 8 essentially shows that
- Housing 36 and cover 36d omitted. Of the housing 36 are only a section through the spring guide 36f and a section through the rest stop 20, which is located on the housing 36 or on the cover 36d, and the end stops 21 and 22 fixed to the housing.
- the end position stop 21 can be formed in that the toothed segment 4z can come into contact with the housing 36 or in that the throttle valve 4d of the actuating element 4 strikes the wall of the gas channel 2.
- the torsion spring 8d of the spring device 8 is wound helically.
- the torsion spring 8d can exert a torque on the actuating element 4 via the spring linkage 31 and a torque on the intermediate member 10 via the spring linkage 32.
- the spring linkage 32 In the area of the spring linkage 32
- the control device serves to control the power of a drive machine, in particular a drive machine of a vehicle.
- the position of the actuator 4 determines the performance of the prime mover.
- the control device is provided in particular for Otto engines, and the control device is particularly expedient when the control element 4 is a throttle valve rotatably mounted on a throttle valve shaft.
- the actuator 16 serves to adjust the throttle valve 4d of the actuating element 4 between the first end position determined by the first end position stop 21 and the second end position determined by the second end position stop 22. If the actuator 16 fails, the spring device 8 places the throttle valve 4d in the rest position, which is determined by the rest stop 20.
- the rest stop 20 lies between the first end position and the second end position.
- the spring device 8 acts on the actuating element 4 via the first spring linkage 31 and on the intermediate element 10 in the direction of the first end position, which is determined by the first end position stop 21, and via the second spring linkage 32 on the intermediate member 10 in the direction of the second End position, which is determined by the second end stop 22, until the rest position determined by the rest stop 20 is reached. Because the actuating element 4 is operatively connected to the intermediate element 10, or in other words, because the actuating element 4 is coupled to the intermediate element 10 in terms of movement, if the actuator 16 fails, the actuating element 4 together with the intermediate element 10 reaches the intended rest position.
- At least one transmission 6 is provided between the spring device 8 and the intermediate member 10. With the translation 6 it is achieved that between the first end position (first end position stop 21) and the rest position (rest stop 20) the effect (force or
- Torque of the spring device 8 on the intermediate member 10 in the direction of the second end position (second End position stop 22) is greater than the effect of the spring device 8 in the direction of the first end position (first end position stop 21).
- the effect of the spring device 8 are forces which, because the corresponding parts, as shown in FIGS. 4, 5, 7 and 8, are rotatably mounted, result in corresponding torques.
- the gear ratio 6 can have different gear stages, as is explained in detail in particular with reference to FIGS. 1 to 3 with the gear stages 6a and 6b.
- the control device is preferably designed so that when the actuating element 4 is in the first end position determined by the first end position stop 21, the drive machine operates with minimal power or is completely switched off or does not deliver any power. If the actuating element 4 is in the second end position determined by the second end position stop 22, the drive machine preferably works with maximum power.
- the rest position determined by the rest stop 20 is preferably set so that in the rest position the engine delivers so much power that emergency operation of the motor vehicle is possible.
- gear stages 6a and 6b of the transmission ratio 6 in such a way that the first gear stage 6a increases the speed from the first spring linkage 31 to the intermediate member 10 by a first transmission ratio and the second gear stage 6b increases the speed from the second Spring linkage 32 on the intermediate member 10 increased by a second translation amount, the first translation amount being greater than the second translation amount.
- the gear stages 6a and 6b of the transmission ratio 6 such that the first transmission stage 6a transfers the force or the torque from the first spring linkage 31 to the intermediate member 10 by a first transmission amount is reduced and the second gear stage 6b reduces the force or the torque from the second spring linkage 32 to the intermediate member 10 by a second gear ratio, the first gear ratio being greater than the second gear ratio.
- the first transmission stage 6a transfers the force or the torque from the first spring linkage 31 to the intermediate member 10 by a first transmission amount is reduced and the second gear stage 6b reduces the force or the torque from the second spring linkage 32 to the intermediate member 10 by a second gear ratio, the first gear ratio being greater than the second gear ratio.
- a gear ratio is particularly useful for the first gear stage 6a. Since the second gear stage 6b is also used in particular for the exact determination of the rest position, in the area of the second gear stage 6b no complex gearwheel translation is required, but rather how 4, 5, 7 and 8, the stops 32b and 10b, which can be brought into mutual engagement and serve as lever transmission. Between the first end position determined by the first end position stop 21 and the rest position, only a relatively small angle, for example 15 °, is covered, which likewise enables the lever transmission with the two stops 10b, 32b, which is easy to produce.
- the rest stop 20 can be designed to be adjustable, for example by using a screw on the rest stop 20.
- the screw can be used to set the rest position of the throttle valve 4d belonging to the actuating element 4.
- the rest position of the throttle valve 4d can also be adjusted by turning the toothed segment 4z correspondingly with respect to the throttle valve shaft 4w until the throttle valve 4d reaches the desired position when the stop 32a is in contact with the rest stop 20. Only then is the toothed segment 4z fixed on the throttle valve shaft 4w.
- the spring 8a of the spring device 8 (FIGS. 1, 2, 3, 6) or the torsion spring 8d of the spring device 8 (FIGS. 4, 5, 7, 8) is articulated directly on the actuating element 4.
- the spring device 8 acts directly and continuously on the actuating element 4 via the first spring linkage 31.
- nothing is required which the spring device 8 should alternately couple and uncouple with the actuating element 4.
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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)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP96945744A EP0828932B1 (de) | 1996-03-30 | 1996-11-21 | Steuereinrichtung zum steuern einer leistung einer antriebsmaschine |
JP53478197A JP3957757B2 (ja) | 1996-03-30 | 1996-11-21 | 駆動機械の出力を制御するための制御装置 |
US08/973,947 US6050241A (en) | 1996-03-30 | 1996-11-21 | Control device for controlling an output of a driving machine |
DE59608764T DE59608764D1 (de) | 1996-03-30 | 1996-11-21 | Steuereinrichtung zum steuern einer leistung einer antriebsmaschine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE19612869.2 | 1996-03-30 | ||
DE19612869A DE19612869A1 (de) | 1996-03-30 | 1996-03-30 | Steuereinrichtung zum Steuern einer Leistung einer Antriebsmaschine |
Publications (1)
Publication Number | Publication Date |
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WO1997037116A1 true WO1997037116A1 (de) | 1997-10-09 |
Family
ID=7790062
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1996/002220 WO1997037116A1 (de) | 1996-03-30 | 1996-11-21 | Steuereinrichtung zum steuern einer leistung einer antriebsmaschine |
Country Status (8)
Country | Link |
---|---|
US (1) | US6050241A (de) |
EP (1) | EP0828932B1 (de) |
JP (1) | JP3957757B2 (de) |
KR (1) | KR100426887B1 (de) |
CZ (1) | CZ292796B6 (de) |
DE (2) | DE19612869A1 (de) |
ES (1) | ES2173342T3 (de) |
WO (1) | WO1997037116A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999010642A1 (de) * | 1997-08-22 | 1999-03-04 | Mannesmann Vdo Ag | Lastverstellvorrichtung |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6155533C1 (en) * | 1999-01-29 | 2002-07-30 | Visteon Global Tech Inc | Default mechanism for electronic throttle control system |
US6070852A (en) * | 1999-01-29 | 2000-06-06 | Ford Motor Company | Electronic throttle control system |
US6095488A (en) * | 1999-01-29 | 2000-08-01 | Ford Global Technologies, Inc. | Electronic throttle control with adjustable default mechanism |
US6513491B1 (en) * | 1999-10-15 | 2003-02-04 | Siemens Vdo Automotive Inc. | Electronic throttle control linkage with limp home mechanism |
US6575427B1 (en) * | 1999-11-10 | 2003-06-10 | Visteon Global Technologies, Inc. | Electronic throttle control mechanism with reduced friction and wear |
US6253732B1 (en) * | 1999-11-11 | 2001-07-03 | Ford Global Technologies, Inc. | Electronic throttle return mechanism with a two-spring and two-lever default mechanism |
US6286481B1 (en) * | 1999-11-11 | 2001-09-11 | Ford Global Technologies, Inc. | Electronic throttle return mechanism with a two-spring and one lever default mechanism |
US6267352B1 (en) * | 1999-11-11 | 2001-07-31 | Ford Global Technologies, Inc. | Electronic throttle return mechanism with default and gear backlash control |
EP1369564A1 (de) * | 2002-06-07 | 2003-12-10 | Siemens Aktiengesellschaft | Winkelbewegungsaktuator und Zahnrad mit Anschlag dafür |
DE102004043125B4 (de) * | 2004-09-07 | 2017-10-05 | Robert Bosch Gmbh | Drosselvorrichtung |
JP4366324B2 (ja) * | 2005-03-17 | 2009-11-18 | 三菱電機株式会社 | 内燃機関用吸気量制御装置 |
DE102005062467B4 (de) * | 2005-12-27 | 2017-02-09 | Robert Bosch Gmbh | Stellantrieb für ein Stellorgan |
DE102005063021B4 (de) | 2005-12-30 | 2017-03-30 | Robert Bosch Gmbh | Stellantrieb für ein Stellorgan |
DE102008014609A1 (de) * | 2008-03-17 | 2009-09-24 | Continental Automotive Gmbh | Aktuator für Schaltelement einer Verbrennungskraftmaschine |
JP6675959B2 (ja) * | 2016-09-07 | 2020-04-08 | 愛三工業株式会社 | スロットル装置及びその製造方法 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1988002064A1 (en) * | 1986-09-13 | 1988-03-24 | Robert Bosch Gmbh | System for regulated dosing of combustion air into an internal combustion engine |
EP0413082A1 (de) * | 1989-08-16 | 1991-02-20 | VDO Adolf Schindling AG | Lastverstelleinrichtung |
US5492097A (en) * | 1994-09-30 | 1996-02-20 | General Motors Corporation | Throttle body default actuation |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3815735A1 (de) * | 1988-05-07 | 1989-11-16 | Vdo Schindling | Lastverstelleinrichtung |
DE4030901A1 (de) * | 1990-09-29 | 1992-04-02 | Bosch Gmbh Robert | Vorrichtung zum steuern der antriebsleistung eines fahrzeug-antriebsmotors |
DE4243893C2 (de) * | 1991-12-26 | 1996-03-28 | Hitachi Ltd | Vorrichtung zum Steuern einer Drosselklappe einer Brennkraftmaschine |
DE19524941B4 (de) * | 1995-07-08 | 2006-05-18 | Siemens Ag | Lastverstellvorrichtung |
US5812050A (en) * | 1996-12-18 | 1998-09-22 | Figgins; Daniel S. | Electrical control apparatus with unidirectional tactile indicator |
-
1996
- 1996-03-30 DE DE19612869A patent/DE19612869A1/de not_active Ceased
- 1996-11-21 US US08/973,947 patent/US6050241A/en not_active Expired - Lifetime
- 1996-11-21 EP EP96945744A patent/EP0828932B1/de not_active Expired - Lifetime
- 1996-11-21 CZ CZ19973696A patent/CZ292796B6/cs not_active IP Right Cessation
- 1996-11-21 JP JP53478197A patent/JP3957757B2/ja not_active Expired - Lifetime
- 1996-11-21 DE DE59608764T patent/DE59608764D1/de not_active Expired - Lifetime
- 1996-11-21 WO PCT/DE1996/002220 patent/WO1997037116A1/de active IP Right Grant
- 1996-11-21 KR KR1019970708553A patent/KR100426887B1/ko not_active IP Right Cessation
- 1996-11-21 ES ES96945744T patent/ES2173342T3/es not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1988002064A1 (en) * | 1986-09-13 | 1988-03-24 | Robert Bosch Gmbh | System for regulated dosing of combustion air into an internal combustion engine |
EP0413082A1 (de) * | 1989-08-16 | 1991-02-20 | VDO Adolf Schindling AG | Lastverstelleinrichtung |
US5492097A (en) * | 1994-09-30 | 1996-02-20 | General Motors Corporation | Throttle body default actuation |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999010642A1 (de) * | 1997-08-22 | 1999-03-04 | Mannesmann Vdo Ag | Lastverstellvorrichtung |
US6360718B1 (en) | 1997-08-22 | 2002-03-26 | Mannesmann Vdo Ag | Load setting device |
Also Published As
Publication number | Publication date |
---|---|
KR19990022074A (ko) | 1999-03-25 |
EP0828932A1 (de) | 1998-03-18 |
JPH11507118A (ja) | 1999-06-22 |
ES2173342T3 (es) | 2002-10-16 |
DE19612869A1 (de) | 1997-10-02 |
EP0828932B1 (de) | 2002-02-20 |
CZ292796B6 (cs) | 2003-12-17 |
JP3957757B2 (ja) | 2007-08-15 |
US6050241A (en) | 2000-04-18 |
DE59608764D1 (de) | 2002-03-28 |
CZ369697A3 (cs) | 1998-03-18 |
KR100426887B1 (ko) | 2004-07-30 |
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