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EP1001143B1 - 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
EP1001143B1
EP1001143B1 EP99121736A EP99121736A EP1001143B1 EP 1001143 B1 EP1001143 B1 EP 1001143B1 EP 99121736 A EP99121736 A EP 99121736A EP 99121736 A EP99121736 A EP 99121736A EP 1001143 B1 EP1001143 B1 EP 1001143B1
Authority
EP
European Patent Office
Prior art keywords
valve
control according
valve control
seat
intake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99121736A
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German (de)
English (en)
Other versions
EP1001143A2 (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
Application filed by Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
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.
  • valve controls have been developed in order to influence and be able to change control times, lift characteristics of the intake and exhaust valves as a function of the engine speed, the load and other influencing variables.
  • the course of the valve lift can thus be influenced or changed by variations in the phase position, the valve lift or the valve opening duration.
  • Such measures can be used individually or in combination, on the one hand to reduce fuel consumption and emissions on the gasoline engine and on the other hand to improve the torque curve and to increase the maximum power.
  • Another advantage arises from the ability to influence the intake air volume by changing the valve opening cross-section and thus to allow a throttle-free load control without throttle.
  • such a circuit can be made that the sucked charge flows only through an inlet valve and thus their amount is affected.
  • a cylinder deactivation by influencing the intake and exhaust valves can also be realized, wherein the fired cylinders can work in the best efficiency range by hiding injections and combustion air. With modern engine electronics, the cylinder deactivation can cyclically (selectively) change to avoid the cooling of the cylinder wall.
  • variable valve timing According to the type of valve actuation, a distinction is made between directly and indirectly actuated systems.
  • the energy is stored similar to the so-called common rail system and fed by fast solenoid or servo valves the control piston surfaces or discharged from them, with which in turn the intake and exhaust valves are actuated.
  • Such systems are known for use in slow-running diesel engines.
  • the invention has for its object to form a valve control of this kind so that while avoiding a complex servo valve a simple and reliable operation at high switching frequencies is possible, so that the valve control can also be used for high-speed internal combustion engines.
  • piezoelectric actuators are used as adjusting elements. With them, low-mass valve elements are actuated, which control the inflow and outflow of the pressure medium to and from the control piston, through the stroke of the inlet and outlet valves of the engine are opened and closed.
  • Piezoelectric actuators convert electrical voltages directly into paths and forces. The conversion of the electrical input into a mechanical output is extremely fast. Adjustment strokes of, for example, 40 ⁇ m (0.04 mm) can be carried out in a positioning time of 50 ⁇ s (0.000.05 sec). The resolution of the travel is possible with suitable electrical control in the nanometer range (0.0001 mm). Actuating forces are achieved in the kilonewton range, ie actuators with very high mechanical rigidity. Since the two piezo elements act as opener and closer, a variable stroke of the inlet / outlet valve can be easily achieved.
  • the availability of suitable power amplifiers is an essential prerequisite for synchronizing the control curve and the response of the intake and exhaust valves.
  • the opening and closing times for the intake / exhaust valves the duration of the opening times can be determined as needed in accordance with the engine management in an advantageous manner.
  • FIGS. 4 to 12 show concrete embodiments of such valve controls and associated characteristic curves.
  • valve controls described below allow high control frequencies, so that these valve controls can also be used in high-revving internal combustion engines.
  • Figs. 1 and 4 to 12 show an embodiment in which the stroke of an intake / exhaust valve 30 can be changed.
  • the valve control has two piezo elements 1, 1 a, with which two plungers 2, 2 a can be actuated in order to displace two valve elements 3, 3 a 2 of two seat valves 9, 9 a.
  • the two valve elements 3, 3a are each under the force of at least one compression spring 6, 6a.
  • a valve chamber 4a of the seat valve 9a opens a pressure line 7.
  • the pressure line 7 is separated via the closed valve element 3a from a supply line 10 for hydraulic medium, which opens into a pressure chamber 14 which is provided in a valve housing 5 and in the an adjusting piston 15 is located, whose one end face 16 can be acted upon by the hydraulic medium.
  • a cylinder chamber 17 On the opposite side of the pressure chamber 14 is a cylinder chamber 17 which is connected via at least one opening 18 to the atmosphere.
  • a plunger 19 which cooperates with a tappet 20. He is under the force of at least one compression spring 21, which loads the bucket tappet 20 and thus the bolt-shaped plunger 19 in the direction of the actuating piston 15 via a valve stem 22.
  • the tappet 20 is located on the valve stem 22, which is provided at the free end with a valve plate 23. With him an inlet or outlet opening 24 of a combustion chamber 25 of an internal combustion engine 26 of a motor vehicle is opened and closed.
  • the valve stem 22 is moved against the force of the compression spring 21 and opened in this way the inlet / outlet valve 30.
  • the actuating piston 15 is displaced until it comes to rest on the bottom 29 of the cylinder chamber 17.
  • the stroke of the actuating piston 15 and thus of the valve 30 corresponds to the normal stroke plus an overstroke.
  • both piezo elements 1, 1a are energized and the piezoelectric element 1 a made de-energized after a stroke-determining time, so that the valve element 3 a is moved by the force of the compression spring 6 a in its closed position.
  • the pressure line 7 of the Feed line 10 separated.
  • the piezoelectric element 1 remains energized, thereby closing the valve 3 and the chamber chambered in the pressure chamber 14.
  • the piezoelectric element 1 is de-energized.
  • the compression spring 6 lifts the valve element 3 from its valve seat 66, whereby the hydraulic medium in the pressure chamber 14 can be displaced via the supply line 10 and the open valve chamber 4 into the tank line 12.
  • valve element 3 and the compression spring 6 are in a bushing 64, which is pressed into an installation space 65 of the valve housing 5.
  • the provided for the valve element 3 valve seat 66 is provided on an insert 43.
  • the compression spring 6 holds the valve element 3 at pronouncevorromtem piezoelectric element 1 in the open position, which is shown in Fig. 8, the insert 43 is axially secured by the flanged end 67 of the sleeve 64.
  • a central axial bore 68 of the stükkes 43 is closed by a closure element 69, preferably a ball.
  • valve element 3a is also received in a bushing 70 (FIG. 7) whose lower end 71 is flanged.
  • the valve element 3a is pressed by the compression spring 6a up against a valve seat 72, which the plunger 2a penetrates axially and thus generates an annular surface 81 required for the flow.
  • the two seat valves 9, 9a are on both sides of the actuating piston 15 and axially parallel to him. As a result, the valve housing 5 has only a small axial height.
  • the cylinder chamber 17 is, as shown in FIG. 5, connected via the vent line 18 to the atmosphere, so that the actuating piston 15 can be moved to open the on / off valve 30 reliably.
  • both piezo elements 1, 1a are energized.
  • the size of the stroke of the actuating piston 15 and thus of the inlet / outlet valve 30 depends on the time from the beginning of the opening, the piezoelectric element 1a is no longer energized and thus no hydraulic medium can flow into the pressure chamber 14.
  • the stroke of the inlet / outlet valve 30 can thus be steplessly controlled.
  • both end faces 16, 28 of the actuating piston 15 are provided with a throttle cross-section, which is an example diametrically extending, in cross-section triangular depression.
  • the throttle cross-sections cooperate with control edges when the actuator piston 15 is moved. When driving over the respective control edge, a pressure builds up in the medium due to the constantly decreasing flow area for the hydraulic medium, which counteracts the movement of the actuating piston 15 and thus causes the damping by reducing speed.
  • the phase position with respect to the opening and closing of the intake / exhaust valves 30 can be changed. This is possible by virtue of the fact that the piezoelements assigned to the intake / exhaust valves 30 are energized or out-flowed at the desired time.
  • the size of the opening stroke of the inlet / outlet valve 30 can additionally be varied in the described manner.
  • Fig. 9 shows stroke characteristics of the manner described with reference to the embodiment of FIGS. 1 and 5 to 8, the opening stroke of the inlet / outlet valve 30 to vary.
  • FIG. 10 shows by means of characteristics that the opening duration of the inlet / outlet valve 30 can be changed in the manner described. From the characteristics in Fig. 11 shows that in addition, the phase angle can be adjusted in the manner described. Finally, FIG. 12 shows characteristic curves for the exemplary embodiment according to FIGS. 1 and 4 to 8, in which the three adjustment possibilities according to FIGS. 9 to 11 can be used in combination. The valve lift, the opening duration and the phase position can be changed. This embodiment represents a fully variable control of the intake / exhaust valves 30.
  • the plungers 2, 2a can be actuated directly by the piezo elements 1, 1a, as shown schematically in FIG. But it is also possible between the plunger 2, 2a and the piezoelectric element 1, 1a each have a transmission lever 59, 59a provided to increase the opening and closing of the valve element 3, 3a at a given piezohub.
  • the transmission lever 59, 59a one-armed lever. At a distance 60 from the pivot axis 61, 61a of the lever 59, 59a attacks on them the plunger 58, 58a.
  • the levers 33, 33a are two-armed levers which have differently long lever arms 86, 87. At the shorter lever arm 87, the plunger 58, 58a of the piezo elements 1, 1 a engage. On the same side of the levers 33, 33a engage at the free ends of the longer lever arms 86, the plunger 2, 2a. About the ratio of the length of the lever arms to each other can also set the gear ratio.
  • the two plunger 2, 58; 2a, 58a are on the same side of the levers 33, 33a, results in a low overall height 73.
  • the two-armed levers 33, 33a are, as explained with reference to the embodiment of FIGS. 4 to 8 in detail, spatially offset from each other, so that the valve housing 5 has only correspondingly small dimensions.
  • the overall height is greater than in the embodiment of FIG. 3, because the piezo elements 1, 1a with their plungers 58, 58a on one side and the plunger 2, 2a with the valves 9, 9a on the other side the lever 59, 59a sit.
  • the 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 plungers 2, 2a and the pivot levers 59, 59a denoted by 75. It can be seen that the overall height 74, 75 is about twice as large as the overall height 73 in the embodiment of FIG. 3rd
  • the two two-armed levers 33, 33a in the housing space 34, which is closed by a housing cover 76.
  • the two levers 33, 33a are arranged offset to one another and are each at an acute angle to a longitudinal center plane 77 of the valve housing 5. Seen in side view, the two levers 33, 33a overlap one another at a small distance one behind the other.
  • the pivot axes 36, 36a are parallel to each other.
  • the plunger 58, 58 a of the two piezo elements 1, 1 a engage.
  • the plunger 2, 2 a At the free ends of the longer lever arms are the plunger 2, 2 a, with which the valve elements 3, 3 a are actuated in the manner described.
  • the two piezoelectric elements 1, 1a lie in separate housing spaces 78, 79 (FIG. 6). In the area between the two housing chambers 78, 79 is the cylinder chamber 17 with the piston 15. By the ratio of the length the lever arms of the respective lever 33, 33 a, the gear ratio is determined. In this way, the small path of movement of the piezo counselen plunger 58, 58a can be translated into the required adjustment of the plunger 2, 2a very simply to move the respective valve element 3, 3a reliably with the required stroke in the corresponding open or 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)

Claims (24)

  1. Commande de soupape pour des soupapes d'admission et d'échappement (30) de moteurs à combustion interne, comportant des éléments de réglage (1, 1a) par lesquels la soupape d'admission/échappement (30) est ouverte et fermée et par lesquels un élément de soupape respectif (3, 3a) est actionné, qui commandent l'afflux et l'évacuation d'un fluide sous pression vers et depuis au moins un piston de réglage (15) mobile au moyen du fluide sous pression pour ouvrir et fermer la soupape d'admission/échappement (30), dans laquelle l'un des éléments de soupape (3a) relie dans une position une conduite sous pression (7) à un compartiment sous pression (14) devant le piston de réglage (15), et l'autre élément de soupape (3) referme dans une position une conduite de réservoir (12), la soupape d'admission/échappement (30) peut être déplacée dans sa position de fermeture par une force indépendante de la sollicitation en pression du piston de réglage (15), l'un des éléments de soupape (3a) est déplacé dans sa position refermant la conduite sous pression (7), et le fluide sous pression situé dans le compartiment de pression (14) devant le piston de réglage (15) est refoulé dans une conduite de réservoir (12), caractérisée en ce que les éléments de réglage (1, 1a) sont des éléments piézoélectriques, en ce que les deux éléments de soupape (3, 3a) opèrent en sens opposés et commandent l'afflux vers une conduite d'alimentation commune (10) pour le fluide sous pression, conduite qui débouche dans le compartiment de pression (14), en ce que les deux éléments piézoélectriques (1, 1a) pour régler la course de la soupape d'admission/échappement (30) sont actionnables indépendamment l'un de l'autre, et en ce que l'un des éléments piézoélectriques (1) fait office de dispositif de fermeture pour la conduite de réservoir et l'autre élément piézoélectrique (1a) fait office de dispositif d'ouverture pour la conduite sous pression.
  2. Commande de soupape selon la revendication 1, caractérisée en ce que les deux éléments de soupape (3, 3a) font partie de soupapes à siège (9, 9a) qui commandent l'afflux du fluide sous pression depuis la conduite sous pression (7) vers le piston de réglage (15).
  3. Commande de soupape selon la revendication 2, caractérisée en ce que les deux soupapes à siège (9, 9a) sont branchées à la conduite d'alimentation commune (10).
  4. Commande de soupape selon l'une ou l'autre des revendications 2 et 3, caractérisée en ce que dans l'état sans courant des éléments piézoélectriques (1, 1a), l'une des soupapes à siège (9) est ouverte et l'autre soupape à siège (9a) est fermée.
  5. Commande de soupape selon l'une des revendications 1 à 4, caractérisée en ce que le piston de réglage (15) coopère par un poussoir (19) avec une tige de soupape (22) de la soupape d'admission/échappement (30), tige qui coopère avec le poussoir (19) avantageusement par un poussoir à cloche (20).
  6. Commande de soupape selon l'une des revendications 1 à 5, caractérisée en ce que les deux éléments piézoélectriques (1, 1a) coopèrent avec l'élément de soupape (3, 3a) par un poussoir respectif (2, 2a).
  7. Commande de soupape selon l'une des revendications 4 à 6, caractérisée en ce que l'élément de soupape (3) de la soupape à siège ouverte (9) est susceptible d'être déplacé dans sa position de fermeture par le poussoir (2) de l'un des éléments piézoélectriques (1) lors de son alimentation en courant, position dans laquelle la conduite d'alimentation (10) est séparée de la conduite de réservoir (12).
  8. Commande de soupape selon l'une des revendications 4 à 7, caractérisée en ce que l'élément de soupape (3a) de la soupape à siège fermée (9a) est susceptible d'être déplacé dans sa position d'ouverture par le poussoir (2a) de l'autre élément piézoélectrique (1a) lors de son alimentation en courant, position dans laquelle la conduite sous pression (7) est reliée à la conduite d'alimentation (10) débouchant dans le compartiment de pression (14).
  9. Commande de soupape selon l'une des revendications 1 à 8, caractérisée en ce que lors d'une alimentation en courant de durée suffisante des deux éléments piézoélectriques (1, 1a), le piston de régalage (15) et ainsi la soupape d'admission/échappement entraînée (30) décrivent leur course maximale et peuvent y être maintenus.
  10. Commande de soupape selon l'une des revendications 2 à 9, caractérisée en ce que pour maintenir le piston de réglage (15) dans la position d'ouverture maximale, les deux soupapes à siège (9, 9a) sont fermées.
  11. Commande de soupape selon l'une des revendications 2 à 10, caractérisée en ce que pour maintenir le piston de réglage (15) dans la position d'ouverture maximale, l'une des soupapes à siège (9) est fermée et l'autre soupape à siège (9a) est ouverte.
  12. Commande de soupape selon l'une des revendications 2 à 11, caractérisée en ce que lors d'une alimentation en courant d'une durée plus courte des deux éléments piézoélectriques (1, 1a), le piston de réglage (15) décrit une course plus petite par comparaison avec la course maximale.
  13. Commande de soupape selon la revendication 12, caractérisée en ce que pour maintenir le piston de réglage (15), la course d'ouverture étant réduite, les deux soupapes à siège (9, 9a) sont fermées.
  14. Commande de soupape selon l'une des revendications 1 à 13, caractérisée en ce que les deux éléments piézoélectriques (1, 1a) coopèrent avec le poussoir (2, 2a) par un transmetteur (33, 33a), de préférence par un levier à deux bras.
  15. Commande de soupape selon la revendication 14, caractérisée en ce que les deux transmetteurs (33, 33a) sont agencés, vus en direction de leur axe de pivotement (36, 36a), de manière à se chevaucher.
  16. Commande de soupape selon l'une ou l'autre des revendications 14 et 15, caractérisée en ce que les deux transmetteurs (33, 33a) sont disposés en rangée.
  17. Commande de soupape selon l'une des revendications 14 à 16, caractérisée en ce que les deux transmetteurs (33, 33a) se trouvent parallèlement l'un à l'autre et de préférence sous un angle aigu par rapport à un plan longitudinal médian (77) d'un boîtier de soupape (5).
  18. Commande de soupape selon l'une des revendications 1 à 17, caractérisée en ce que l'élément de soupape (3, 3a) fabriqué avantageusement à partir d'une bille comprend une partie formant siège (83) depuis laquelle fait saillie un talon (84) de plus petite section transversale.
  19. Commande de soupape selon la revendication 18, caractérisée en ce que le ressort de compression (6, 6a) est enfilé sur le talon (84) de l'élément de soupape (3, 3a), talon qui va en s'élargissant coniquement avantageusement à partir de la partie formant siège (83).
  20. Commande de soupape selon l'une ou l'autre des revendications 18 et 19, caractérisée en ce qu'à la transition du talon (84) vers la partie formant siège (83), la différence de diamètre correspond au double de l'épaisseur de fil du ressort de compression (6, 6a).
  21. Commande de soupape selon l'une des revendications 18 à 20, caractérisée en ce qu'à l'extrémité libre du talon (84) est prévue une autre partie formant siège (85) réalisée de préférence sous forme partiellement sphérique ou conique.
  22. Commande de soupape selon la revendication 21, caractérisée en ce que l'autre partie formant siège (85) présente un diamètre de siège plus petit que l'autre partie formant siège (83).
  23. Commande de soupape selon l'une des revendications 14 à 22, caractérisée en ce que les deux poussoirs (2, 2a) se trouvent sur le même côté des deux transmetteurs (33, 33a).
  24. Commande de soupape selon l'une des revendications 14 à 23, caractérisée en ce que les deux transmetteurs (33, 33a) sont agencés en décalage dans l'espace l'un par rapport à l'autre.
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 EP1001143A2 (fr) 2000-05-17
EP1001143A3 EP1001143A3 (fr) 2000-12-06
EP1001143B1 true EP1001143B1 (fr) 2005-09-21

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

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EP1001143A2 (fr) 2000-05-17
US6374784B1 (en) 2002-04-23
DE59912577D1 (de) 2006-02-02
ES2245495T3 (es) 2006-01-01
EP1001143A3 (fr) 2000-12-06
JP2000161031A (ja) 2000-06-13
DE19852209A1 (de) 2000-05-18

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