EP1001143A2 - Commande de soupape pour soupapes d'admission et d'échappement de moteur à combustion interne - Google Patents

Commande de soupape pour soupapes d'admission et d'échappement de moteur à combustion interne Download PDF

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Publication number
EP1001143A2
EP1001143A2 EP99121736A EP99121736A EP1001143A2 EP 1001143 A2 EP1001143 A2 EP 1001143A2 EP 99121736 A EP99121736 A EP 99121736A EP 99121736 A EP99121736 A EP 99121736A EP 1001143 A2 EP1001143 A2 EP 1001143A2
Authority
EP
European Patent Office
Prior art keywords
valve
control according
valve control
seat
actuating piston
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
EP99121736A
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German (de)
English (en)
Other versions
EP1001143B1 (fr
EP1001143A3 (fr
Inventor
Dieter Tischer
Alfred Trzmiel
Dieter Maisch
Herbert Panowitz
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of EP1001143A2 publication Critical patent/EP1001143A2/fr
Publication of EP1001143A3 publication Critical patent/EP1001143A3/fr
Application granted granted Critical
Publication of EP1001143B1 publication Critical patent/EP1001143B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets
    • F01L1/25—Hydraulic tappets between cam and valve stem
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means

Definitions

  • the invention relates to a valve control for intake and exhaust valves of internal combustion engines according to the preamble of claim 1.
  • the Stroke movements of the intake and exhaust valves by one of the Crankshaft in the speed ratio 2: 1 driven camshaft is for the entire area of the map proportional to the cam profile and therefore unchangeable.
  • the closing point of the inlet valve is due to different ones Flow velocity in the intake manifold, not optimally placed.
  • the The inlet or opening point can also not be optimally set.
  • the values for the best possible filling of the combustion chamber at high speeds and the cylinder exhaust gas content at low Speeds and idle are diametrically opposed to each other.
  • the opening point or start of the outlet is therefore usually chosen so that the expulsion losses are minimized and the gas in the Able to do maximum work.
  • valve controls have been developed to control timing, Stroke curves of the intake and exhaust valves depending on the Motor speed, the load and other influencing factors influence and to be able to change.
  • the course of the valve lift can be done by Variations in phase, valve lift or valve opening time be influenced or changed.
  • Such measures can individually or in combination to be used on gasoline engines on the one hand to reduce fuel consumption and emissions and on the other hand to improve the torque curve and increase the maximum performance.
  • Another advantage arises from the possibility of changing the amount of air sucked in to influence the valve opening cross-section and thus a throttle-free Allow load control without throttle.
  • variable valve timing The aforementioned options for influencing and changing of parameters are called “variable valve timing” summarized. Depending on the type of valve actuation, between distinguish directly and indirectly operated systems.
  • the invention has for its object the generic valve control to be designed so that instead of a complex servo valve simple and reliable operation at high switching frequencies is possible, so that the valve control for high-revving Internal combustion engines can be used.
  • a control element is used piezoelectric actuator used. With it becomes a low-mass Valve element actuates the inflow and outflow of the pressure medium controls to and from the actuating piston, the stroke of which and exhaust valves of the internal combustion engine opened and closed become.
  • Piezoelectric actuators set electrical voltages directly into paths and forces. Implementation of the electrical Input variable in a mechanical output variable takes place extremely fast. Adjustment stroke of for example 40 ⁇ m (0.04 mm) can be in a positioning time of 50 ⁇ s (0.000.05 sec). The dissolution of the Travel is in the nanometer range with suitable electrical control (0.0001 mm) possible. Actuating forces are in the kilonewton range reached, that is to say actuators with very high mechanical rigidity.
  • valve control according to the invention can be advantageous Way according to the engine management the opening and Closing times for the intake / exhaust valves the duration of the opening hours be determined as required.
  • valve controls in their mode of operation. 9 to 21 then show specific configurations of such valve controls and associated characteristics.
  • valve controls described below enable high Control frequencies, so that these valve controls even at high revs Internal combustion engines can be used.
  • valve 1 has a piezo element as an actuator 1, whose plunger 2 acts on a valve element 3, which acts as a valve ball is trained.
  • the valve element 3 lies in a valve chamber 4 of a valve housing 5.
  • the valve element 3 is under the force a compression spring 6 with which the valve element 3 when the piezo element is de-energized 1 is held in a closed position.
  • the valve element 3 is by the compression spring 6, which is a conical helical compression spring is pressed up against the valve seat. In this In the closed position, the valve element 3 closes a pressure line 7, supplied via the hydraulic medium from a pressure source 8 becomes.
  • the valve element 3 and the valve chamber 4 are part of one Two-way seat valve 9, to which a supply line 10 for hydraulic medium connected. It has at least one restriction 11 provided.
  • a tank line 12 opens into the feed line 10 which is also a throttle point 13.
  • the feed line 10 connects the valve chamber 4 with a pressure chamber 14 in the valve housing 5 is provided and in which there is an actuating piston 15, the an end face 16 can be acted upon by hydraulic medium.
  • Cylinder chamber 17, which has at least one opening 18 with the atmosphere connected is located on the side opposite the pressure chamber 14 .
  • a plunger 19 projects into the cylinder space 17 cooperates with a tappet 20. He is under the force at least one compression spring 21 which via a valve stem 22 Cup tappet 20 and thus the bolt-shaped tappet 19 in the direction loaded on the actuating piston 15 (see also Fig. 9).
  • On the tappet 20 is applied to the valve stem 22, the one with a free end Valve plate 23 is provided. With it is an inlet or outlet opening 24 of a combustion chamber 25 of an internal combustion engine 26 of a motor vehicle opened and closed.
  • the piezo element 1 is controlled by a control (not shown) energized by its plunger 2, the valve element 3 against Force of the compression spring 6 is lifted off the valve seat.
  • the hydraulic medium can then via the pressure line 7, the valve chamber 4 and the Flow supply line 10 into the pressure chamber 14. Part of this hydraulic medium flows over the tank line 12, which is in the range between the valve chamber 4 and the pressure chamber 14 to the supply line 10 connects to the tank.
  • the two throttle points 11, 13 in the feed line 10 and in the tank line 12 are thus one on the other matched that in the pressure chamber 14 by the hydraulic medium pressure required to move the actuating piston 15 is applied can be.
  • the piezo element 1 can be operated at a very high frequency, so that the opening and closing process described Intake / Auslassventils 30 take place in the required high control frequency can.
  • the valve control is therefore for internal combustion engines suitable that work at high speeds. On the described All of the valves 30 of the internal combustion engine 26 are actuated in this manner.
  • the inlet / outlet valve 30 is in the open position and in the closed position each over a period of time specified by the engine management held. This results in the inlet / outlet valve 30 four cyclically repeating operating states, namely opening, keep open, close and keep closed.
  • Fig. 9 shows a concrete embodiment of the embodiment 1.
  • the piezo element 1 is located in the valve housing 5 next to the Adjusting piston 15 and the valve element 3.
  • the piezo element 1 is in a receiving space 31 of the valve housing 5 and is by springs 32, preferably biased by disc springs, in the receiving space 31.
  • the piezo element 1 acts with a two-armed lever 33 together, which is pivotally mounted in a housing space 34.
  • One lever arm interacts with the piezo element while on the other lever arm, the tappet 2 actuating the valve element 3 engages an adjusting screw 82.
  • the stroke positions can be done with it of the piezo element 1 and the plunger 2 match each other.
  • the plunger 2 is guided by a bearing 35 so that it is reliable can be moved.
  • the actuating piston 15 is located in the area between the two-way seat valve 9 and the piezo element 1.
  • the piezo element 1 is energized and thus elongated, the lever 33 is perpendicular to its Axis of the piezo element 1 lying axis 36 counterclockwise pivoted. This pushes the plunger 2 downwards whereby the valve element 3 against the force of the compression spring 6 is moved to the open position.
  • the pressure line 7 will opened so that the pressurized hydraulic medium over the Throttle point 11 can flow into the pressure chamber 14.
  • the actuating piston 15 is thereby moved down.
  • the swivel movement ends with the Closing the valve element 3.
  • the valve stem 22 is through the Compression spring 21 moved upwards, causing the tappet 20 and the plunger 19 of the piston 15 is moved upwards.
  • the hydraulic medium located in the pressure chamber 14 is via the Throttle point 13 and the tank line 12 in the manner described displaced to the tank.
  • the piezo element remains in this closed position de-energized according to engine management.
  • the tappet 20 is located in a receiving space 37 of the Internal combustion engine 26.
  • the valve housing 5 is on the internal combustion engine 26 attached.
  • the receiving space 37 is through the valve housing 5 closed.
  • the valve housing 5 Since the piezo element 1 in the area next to the two-way seat valve 9 and the control piston 15 is arranged, the valve housing 5 only a low overall height. This is helped by the fact that the adjusting piston 15 is arranged in the area next to the two-way seat valve 9.
  • the lever 33 serves as a translation lever, which the very small ways of Piezo element 1 over the longer lever arm in sufficiently large Ram 2 displacement paths translated.
  • FIG. 9a shows a conventional valve control by means of a camshaft 39. For the sake of clarity, it is between the camshaft 39 and tappet 20 lying rocker arm not shown.
  • the cams 40 of the camshaft 39 act with the tappets 20 the inlet / outlet valves together in a known manner.
  • the one through the Cam 40 achieved stroke of the valve stem 22 has the same size as in the described valve control according to FIGS. 1 and 9.
  • Fig. 9b shows with solid lines that with the camshaft Valve control opens the inlet / outlet valve 30 faster and can be closed than with the conventional camshaft control (dashed line in Fig. 9b). With the dotted line the possibility is shown with the camshaft-less valve control to vary the opening duration of the intake / exhaust valve 30.
  • Fig. 9c shows the possibility in the camshaft-less valve control also the phase position (solid and dotted line) and also vary the opening time (dotted line).
  • FIGS. 1 and 9 show a valve control, which compared to Embodiment according to FIGS. 1 and 9 higher control frequencies allows.
  • the valve 9 ' is different from the previous embodiment a three-way valve with two seats.
  • Fig. 2 again shows the State with de-energized piezo element 1.
  • the valve element 3 lies under the force of the compression spring 6 on an upper valve seat 41 (Fig. 11).
  • the tank line 12 opens out Embodiment in a lower valve seat 42 of the three-way valve 9 '.
  • Fig. 11 shows the three-way valve of Fig. 10 in an enlarged view Presentation.
  • the piezo element 1 is energized and thereby expands.
  • the two-armed lever 33 will thereby pivoted counterclockwise about axis 36, whereby the plunger 2 downwards against the force of the compression spring 6 is moved until it rests on the lower valve seat 42.
  • the tank line 12 is closed, so that the pressure line 7 flowing medium exclusively via the feed line 10 in reaches the pressure chamber 14.
  • the end face 16 of the actuating piston 15 pressurized with pressure medium so that it is described in the Way is moved down and over the plunger 19 and the tappet 20 moves the valve stem 22.
  • the inlet / outlet valve 30 is opened in the manner described and kept in the open position if necessary.
  • the piezo element 1 de-energized and shortened to its original length.
  • the valve element 3 becomes the upper valve seat by the compression spring 6 41 moved, which closed the pressure line 7 and the Tank line 12 is opened. This can cause the hydraulic medium from the pressure chamber 14 via the feed line 10 into the tank line 12 stream.
  • the pressure relief of the pressure chamber 14 will Inlet / outlet valve 30 closed in the manner already described and kept in the closed position if necessary.
  • the lower valve seat 42 of the three-way valve 9 ' is on one Insert 43 provided (Fig. 11), which in turn in another Insert 44 is held. It is in an installation space 45 of the Valve housing 5 pressed. The free end of the insert 44 is flanged inwards, whereby the insert located in it 43 is held.
  • the three-way valve 9 forms a shuttle valve.
  • the valve element 3 has accordingly two seat parts 83 and 85, with which it alternates abuts the upper valve seat 41 and the lower valve seat 42.
  • the upper seat part 83 is in the illustrated embodiment partially spherical, but can also have a conical shape.
  • the seat part 83 is approximately hemispherical.
  • An approach 84 connects to it to which the compression spring 6 is pushed with its upper end is.
  • the approach 84 widens conically from the upper seat part 83.
  • At the transition from the neck 84 in the upper seat part 83 is a Stage formed.
  • the diameter difference between the approach 84 and the seat part 83 corresponds to twice the wire thickness of Compression spring 6.
  • the upper end of the compression spring 6 does not stand radially over the seat part 83.
  • the compression spring 6 has a conical shape.
  • the compression spring 6 is with its upper end region on the jacket of the neck 84. Since the Approach 84 and the compression spring 6 are conical and expand from the seat part 83 is an axial lock for the compression spring 6 given on the approach 84. This will assemble this Valves 9 'relieved.
  • the lower seat part 85 is again part-spherical trained and has a maximum diameter that the corresponds to the maximum diameter of the extension 84.
  • the seat part 85 can also be conical.
  • the largest diameter of the Approach 84 or the lower seat part 85 is smaller than the largest Diameter of the upper seat part 83.
  • the lower one Seat part 85 has a smaller seat diameter than the upper seat part 83, so that the upper valve seat 41 has a larger diameter than that lower valve seat 42.
  • the upper valve seat 41 is axial from the tappet 2 permeated.
  • the resulting ring surface 81 (Fig. 11) of the Upper valve seat 41 is approximately the same area as the circular area 88 (Fig. 11) of the lower valve seat 42.
  • the valve element 3 can manufacture themselves inexpensively from a sphere. In this case the upper and lower seat portions 83, 85 share a common curvature.
  • FIGS. 2, 10 and 11 The valve control according to FIGS. 2, 10 and 11 is otherwise the same formed like the previous embodiment (Fig. 1 and 9). However can with this valve control the intake / exhaust valves even faster can be opened and closed like the corresponding diagrams show below Fig. 11 (solid and dotted lines). In comparison, the closing and Opening times of conventional camshaft valve controls are shown. As already explained with reference to FIGS. 9b and 9c, the Phase position and the opening time can be changed in the same way.
  • valve control with end position damping of the control piston 15.
  • the valve control has the piezo element 1, with which the plunger 2 for actuating the valve element 3 in the described Way is moved.
  • the connection between the Piezo element 1 and the plunger 2 takes place in a specific embodiment (Fig. 12) again via the two-armed lever 33, with which the plunger 2 is displaced when the piezo element 1 is energized is and the valve element 3 moves accordingly.
  • the Valve 9 "is in accordance with the previous embodiment (Fig. 11) designed as a three-way valve with two valve seats. Is the piezo element 1 is not energized, the valve element 3 is under the force the compression spring 6 on the upper valve seat 41. The pressure line 7 is thereby separated from the feed line 10.
  • the end face 16 of the actuating piston 15 has a throttle cross section 48 provided that in the exemplary embodiment as a diametrically extending is formed triangular recess in cross section. Also the opposite end face 28 of the actuating piston 15 is with a Throttle cross section 49 provided, which is also advantageous as in Cross-section of triangular, diametrically extending recess is.
  • the actuating piston 15 lies with its end face 28 as in the previous embodiments on the plunger 19, the corresponding the previous embodiments a smaller cross section has as the end face 28 of the actuating piston 15. About the Tappet 19, the tappet 20 and the valve stem 22 in the described way postponed.
  • the feed line 10 opens into an annular channel 50 which is in the wall of the piston chamber 51 is provided.
  • Another ring channel 52 in the wall of the piston chamber 51 is provided in the cylinder chamber 17.
  • This ring channel 52 is connected via a return line 53 the tank line 12 connected.
  • the cylinder space 17 is over a Cross line 54 connected to a check valve 55, which the Cross line 54 separates from the return line 53 and that in the direction opens on the cross line 54.
  • the piezo element 1 is energized.
  • the plunger 2 is moved via the lever 33, whereby the valve element 3 is lifted from the seat 41 and on the opposite Valve seat 42 is brought into contact.
  • This will make the Pressure line 7 opened so that the hydraulic medium via the valve chamber 4, the feed line 10, the transverse bore 46 and the check valve 47 can flow into the pressure chamber 14.
  • the valve element 3 rests on the valve seat 42, the connection to the tank line 12 closed.
  • the hydraulic medium passes through the supply line 10 also in the annular channel 50, which is initially through the actuating piston 15 is closed.
  • the adjusting piston 15 is in the Pressure chamber 14 flowing hydraulic medium shifted downwards.
  • the piezo element 1 switched off again and thus shortened.
  • the valve element 3 is by the compression spring 6 in the manner described from the valve seat 42 lifted off and pressed against the valve seat 41. Thereby the pressure line 7 is closed against the supply line 10.
  • the tank line 12 is thus opened.
  • the actuating piston 15 is carried along via the tappet 19. It displaces the hydraulic medium from the pressure chamber 14 in the ring channel 50, through which the hydraulic medium via the valve chamber 4 reaches the tank line 12. Once the piston face 16 passes over the control edge 57 (FIG.
  • the described embodiment is advantageous in this that the actuating piston 15 is damped in both end positions. Thereby this valve control works very quietly.
  • the three-way valve 9 " is otherwise the same as in the previous Embodiment.
  • the three-way valve is also in this valve control 9 ", the actuating piston 15 and the piezo element 1 at a distance next to each other in the valve housing 5. This only has one low height.
  • valve controls 1 to 3 or 9 to 12 the same stroke 80 is reached as when using a conventional camshaft control (Fig. 5).
  • a conventional camshaft control Fig. 5
  • the camshaft-less valve control can be used instead the camshaft valve control.
  • FIG. 4 schematically shows the possibility of using the piezo element 1 via a plunger 58 to a one-armed transmission lever 59 Act.
  • the plunger 58 engages at a distance 60 from a pivot axis 61 on lever 59.
  • the free end of the lever 59 acts the plunger 2 with which the valve element 3 in the described Way is moved.
  • the free end of the lever has a distance of 62 from the pivot axis 61.
  • the two distances 60, 62 desired gear ratio determined.
  • the actuating piston stroke is and thus the stroke of the intake / exhaust valve 30 cannot be changed.
  • the valve control has two piezo elements 1, 1a, with which two plungers 2, 2a are operated in order to move two valve elements 3, 3a of two seat valves 9, 9a.
  • the two valve elements 3, 3a are each at least under the force a compression spring 6, 6a.
  • In the valve chamber 4a of the seat valve 9a opens the pressure line 7.
  • the piezo element 1a is de-energized the pressure line 7 via the closed valve element 3a from the Supply line 10 separated, which opens into the pressure chamber 14.
  • Of the Feed line 10 branches off a connecting line 63, which in the Valve chamber 4 of the seat valve 9 opens.
  • the piezo element is not energized 1, the valve chamber 4 is connected to the tank line 12.
  • Fig. 6 shows the situation when the two piezo elements 1, 1a de-energized and thus the inlet / outlet valves 30 are closed.
  • both piezo elements 1, 1a are energized.
  • the two plungers 2, 2a are displaced.
  • the valve element 3 against the force of the spring 6 in its Moves the closed position in which it closes the tank line 12.
  • the valve element 3a With the plunger 2a, the valve element 3a is in an open position moves so that the hydraulic medium via the pressure line 7 and Valve chamber 4a can flow into the feed line 10. The hydraulic medium thereby enters the pressure chamber 14 and shifts the Set piston 15 down.
  • both piezo elements 1, 1a energized and the piezo element 1a after a stroke-determining Time de-energized so that the valve element 3a moved into its closed position by the force of the compression spring 6a becomes.
  • the pressure line 7 is separated from the supply line 10.
  • the piezo element 1 remains energized and thereby the valve 3 closed and the volume in the pressure chamber 14 chambered.
  • Liquid volume of the hydraulic medium flowing into the pressure chamber thus determines the stroke of the actuating piston 15 and thus also the stroke of the inlet / outlet valve 30, since the piezo element 1 continues to be energized, thereby closing line 63 to tank 12 remains.
  • the volume of liquid in the pressure chamber 14 thereby remains enclosed (chambered), the valve 30 less wide open, so that a correspondingly smaller amount of Air-fuel mixture in the combustion chamber of the internal combustion engine reached.
  • the piezo element 1 switched off.
  • the compression spring 6 lifts the valve element 3 from its valve seat 66, whereby the pressure chamber 14 located hydraulic medium via the feed line 10 and the open Valve chamber 4 can be displaced into the tank line 12.
  • valve element 3 and the Compression spring 6 in a socket 64, which is in an installation space 65 of the Valve housing 5 is pressed.
  • the one provided for the valve element 3 Valve seat 66 is provided on insert 43, which is essentially is of the same design as in the embodiment according to 10 and 11.
  • the compression spring 6 maintains the valve element 3 non-energized piezo element 1 in the open position, which is shown in FIG is shown.
  • the insert 43 is through the flanged end 67 of the sleeve 64 axially secured.
  • a central axial bore 68 of the insert 43 is preferably by a closure element 69 a ball, closed.
  • valve element 3a is also received in a bushing 70 (Fig. 16), the lower end 71 is crimped.
  • the valve element 3a is pushed up against a valve seat 72 by the compression spring 6a pressed, the plunger 2a penetrates axially and thus one for the Flow required ring area 81 generated.
  • the two seat valves 9, 9a are located on both sides of the actuating piston 15 and axially parallel to it. As a result, the valve housing 5 has only one low axial height.
  • the cylinder chamber 17 is, as shown in FIG. 14, via the ventilation line 18 connected to the atmosphere, so that the actuating piston 15 to Opening the intake / exhaust valve 30 can be reliably moved can.
  • both piezo elements 1, 1a energized.
  • the size of the stroke of the actuating piston 15 and thus of the intake / exhaust valve 30 depends on the time after the start of opening the piezo element 1a is no longer energized and thus no more hydraulic medium can flow into the pressure chamber 14.
  • the piezo element 1 a leaves thus control the stroke of the intake / exhaust valve 30 continuously.
  • Fig. 19 shows on the basis of characteristic curves that the opening duration of the Inlet / outlet valves 30 can be changed in the manner described can. From the characteristics in Fig. 20 it follows that additionally the phase position can be set in the manner described. 21 shows characteristic curves for the exemplary embodiment 6 and 13 to 17, in which the three setting options 18 to 20 can be used in combination. The valve lift, the duration of the opening and the phase position to be changed. This embodiment represents one fully variable control of the inlet / outlet valves 30.
  • the plungers 2, 2a can be actuated directly by the piezo elements 1, 1a as shown schematically in Fig. 6. But it is also possible between the plunger 2, 2a and the piezo element 1, 1a each provide a transmission lever 59, 59a to the Opening and closing stroke of the valve element 3, 3a at a predetermined Magnify Piezohub.
  • the transmission levers 59, 59a one-armed lever. At a distance 60 from the pivot axis 61, 61a Lever 59, 59a engages the plunger 58, 58a in accordance with the Embodiment according to FIG. 4.
  • the plunger 2, 2a attacks.
  • the plungers 2, 58 and 2a, 58a lie on each other opposite sides of the lever 59, 59a.
  • about the relationship of the distances 60 and 62 to each other can be the gear ratio be determined.
  • the levers 33, 33a have two arms Levers that have lever arms 86, 87 of different lengths.
  • the plungers 58, 58a of the piezo elements engage on the shorter lever arm 87 1, 1a.
  • the levers 33, 33a engage on the same side the plungers 2, 2a to the free ends of the longer lever arms 86.
  • About the ratio of the length of the lever arms to each other also determine the gear ratio.
  • the overall height is greater than that of Embodiment according to Fig. 8, because the piezo elements 1, 1a with their plungers 58, 58a on one and the plungers 2, 2a with the Valves 9, 9a sit on the other side of the levers 59, 59a.
  • Fig. 7 is the overall height of the piezo elements 1, 1a with the plungers 58, 58a with 74 and the height of the seat valves 9, 9a with the tappets 2, 2a and the pivot levers 59, 59a at 75. It is recognizable that the overall height 74, 75 is about twice as large as the total height 73 in the exemplary embodiment according to FIG. 8.
  • the two two-armed levers 33, 33a in the housing space 34 which by a housing cover 76 is closed.
  • the two levers 33, 33a are staggered and are each under one acute angle to a longitudinal center plane 77 of the valve housing 5. Seen in side view, the two levers 33, 33a lie one against the other overlapping with a short distance behind each other.
  • the swivel axes 36, 36a are parallel to each other.
  • At the free end of the shorter one Lever arms engage the plungers 58, 58a of the two piezo elements 1, 1a.
  • the tappets are located on the free ends of the longer lever arms 2, 2a with which the valve elements 3, 3a in the described Way to be operated.
  • the two piezo elements 1, 1a are located in separate housing spaces 78, 79 (Fig. 15). In the area between the two housing rooms 78, 79 is the cylinder space 17 with the piston 15 the ratio of the length of the lever arms of the respective lever 33, 33a, the gear ratio is determined. In this way can easily the small movement path of the piezo-side Tappet 58, 58a in the required adjustment path of the tappet 2, 2a be translated reliably to the respective valve element 3, 3a with the required stroke in the corresponding open or To move the closed position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP99121736A 1998-11-12 1999-11-03 Commande de soupape pour soupapes d'admission et d'échappement de moteur à combustion interne Expired - Lifetime EP1001143B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19852209 1998-11-12
DE19852209A DE19852209A1 (de) 1998-11-12 1998-11-12 Ventilsteuerung für Ein- und Auslaßventile von Verbrennungsmotoren

Publications (3)

Publication Number Publication Date
EP1001143A2 true EP1001143A2 (fr) 2000-05-17
EP1001143A3 EP1001143A3 (fr) 2000-12-06
EP1001143B1 EP1001143B1 (fr) 2005-09-21

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ID=7887573

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EP99121736A Expired - Lifetime EP1001143B1 (fr) 1998-11-12 1999-11-03 Commande de soupape pour soupapes d'admission et d'échappement de moteur à combustion interne

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US (1) US6374784B1 (fr)
EP (1) EP1001143B1 (fr)
JP (1) JP2000161031A (fr)
DE (2) DE19852209A1 (fr)
ES (1) ES2245495T3 (fr)

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US6374784B1 (en) 2002-04-23
ES2245495T3 (es) 2006-01-01
DE59912577D1 (de) 2006-02-02
EP1001143B1 (fr) 2005-09-21
EP1001143A3 (fr) 2000-12-06
JP2000161031A (ja) 2000-06-13
DE19852209A1 (de) 2000-05-18

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