EP0405187B1 - Dispositif électromagnétique de positionnement - Google Patents

Dispositif électromagnétique de positionnement Download PDF

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Publication number
EP0405187B1
EP0405187B1 EP90110559A EP90110559A EP0405187B1 EP 0405187 B1 EP0405187 B1 EP 0405187B1 EP 90110559 A EP90110559 A EP 90110559A EP 90110559 A EP90110559 A EP 90110559A EP 0405187 B1 EP0405187 B1 EP 0405187B1
Authority
EP
European Patent Office
Prior art keywords
positioning device
armature
transmission system
control element
spring
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
EP90110559A
Other languages
German (de)
English (en)
Other versions
EP0405187A1 (fr
Inventor
Peter Dr.-Ing. Kreuter
Armin Dipl.-Ing. Zoschke
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.)
FEV Europe GmbH
Original Assignee
FEV Motorentechnik GmbH and Co KG
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 FEV Motorentechnik GmbH and Co KG filed Critical FEV Motorentechnik GmbH and Co KG
Priority to AT90110559T priority Critical patent/ATE95277T1/de
Publication of EP0405187A1 publication Critical patent/EP0405187A1/fr
Application granted granted Critical
Publication of EP0405187B1 publication Critical patent/EP0405187B1/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
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • F01L1/182—Centre pivot rocking arms the rocking arm being pivoted about an individual fulcrum, i.e. not about a common shaft
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • 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
    • 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
    • F01L1/18—Rocking arms or levers
    • F01L2001/188—Fulcrums at upper surface
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/20—Control lever and linkage systems
    • Y10T74/20576—Elements
    • Y10T74/20882—Rocker arms

Definitions

  • the invention relates to an electromagnetically operating control device for at least one oscillatingly movable control element for displacement machines, in particular flat slide valves and globe valves, with two switching electromagnets, which correspond to the open and the closed switching position of at least one control element, with one arranged between the two switching electromagnets ,
  • the position of the control element determining armature, and with a spring system for oscillating force transmission to the armature between the switching positions, which is dimensioned such that the position of the equilibrium position of the armature lies between the two switching positions.
  • Such an actuator is known from DE-OS 30 24 109.
  • the control element of a displacement machine is held in the closed state by a compression spring in an actuating device of the type listed.
  • Another compression spring acts on a magnet armature interacting with the control element, so that the equilibrium position of the spring system lies in the middle or near the middle between the end positions of the movement of the magnet armature.
  • the end positions of the armature movement are each on an electrically operated switching magnet. To switch this device, one switching magnet is energized and the other switched off. Due to the force of the prestressed spring, the armature is accelerated to the equilibrium position and decelerated on its further path by the counteracting force of the other spring which then determines. Due to friction, the armature cannot reach the opposite end position. On the missing remaining path, the armature is attracted by the pulling force of the switching magnet.
  • This is also an oscillating spring mass system with an equilibrium position between two switching positions.
  • An essential feature of this system is the design of the spring system as a torsion bar spring with valve actuation via a rocker arm with a fixed transmission ratio that is connected to the torsion bar spring in a rotationally fixed manner.
  • the main goals are to minimize the moving masses of the spring-mass system and to increase the effective stroke of the poppet valve when the armature moves for standard electromagnets.
  • systems of this type achieve a reduction in size because the radial dimension of the winding window can be kept small due to the smaller air gap to be bridged. This is particularly important with regard to the use of the actuating device on displacement machines.
  • the working stroke of such an actuating device is to be dimensioned such that a sufficient opening cross-section is available for the largest mass flow occurring at the control element of a displacement machine and thus throttling is avoided.
  • operation of the actuating device at this maximum working stroke is uneconomical, since the electrical energy to be supplied for changing the position of the control element increases as a function of the stroke of the control element.
  • the reduction in the opening cross-section results in an increase in the flow speed at the control element, which contributes to the improvement of the preparation of multiphase mixtures, in particular an air-fuel mixture in internal combustion engines.
  • the executable maximum stroke of the control valve is, however, limited in the previously known types by the dimensions of the actuating device and by the predetermined positioning in the extension of the valve axis and cannot be changed.
  • US-A-1 395 851 describes a possibility of varying the rocker gear ratio by changing the position of the rocker arm axis, with the aim of achieving an improvement in efficiency by means of an opening cross section which is adapted to the respective engine power.
  • the opening and closing times of the valves can only be varied in direct dependence on one another.
  • the object of the present invention is to achieve a flexible adaptation of the actuating device to the respective operating conditions and at the same time an energy saving with the most compact possible dimensions of the actuating device and a freer arrangement of the actuating device in the receptacle, in particular in a cylinder head for an internal combustion engine.
  • an electromagnetically operating control device of the type described in the introduction by means of a variable power transmission system which interacts with the armature and at least one control element, by means of which the armature switches the at least one control element back and forth via means for changing the transmission ratio, the transmission system thus is connected to the oscillating system consisting of the spring system, the armature around the control element, that the equilibrium position of the armature is adjustable, by a common device for simultaneously changing the transmission ratio and the magnetic resistance in the magnetic circuit of one or both working magnets for setting the fall times of the armature , and to adapt the equilibrium position of the vibrating system to the new spring forces by changing the position of one or more spring base points.
  • the transmission system is designed as a hydraulic transmission which is variable in the transmission ratio.
  • the vibratory spring-mass system with compression springs on both sides of the armature is designed according to a further embodiment of the invention so that the springs or spring assemblies are divided into springs arranged on the magnet side and springs arranged on the control element.
  • a plurality of control elements cooperate with one transmission system each, with valve displacement machines each having a transmission system per valve or a common transmission system for several valves.
  • a further embodiment of the invention provides for the non-moving base point of one or more springs of the vibratable system to be adjustable.
  • the aim here is that the adjustment in the receiving housing, in particular in the cylinder head of an internal combustion engine, is arranged so that it is easily accessible, since the correct setting of the equilibrium position takes place under operating conditions.
  • this adjustment takes place either directly by shifting wedge surfaces relative to one another or via a transmission member which is designed as a rocker arm or finger follower.
  • a hydraulic compensation element is provided for the play-free actuation of the oscillating components.
  • the compensating element can be arranged at different positions within the moving components, in particular in the transmission system or in the magnet armature.
  • the hydraulic compensating element is arranged between the receptacle housing and the switching magnet assigned to the closed valve position, the axial displacement of the switching magnet compensating for the changes in length that occur in the moving components.
  • a further advantageous embodiment of the invention consists in the arrangement of the hydraulic compensating element between the mounting of the transmission element and the receiving housing or the adjusting element.
  • Another advantageous embodiment of the invention consists in the use of permanent magnets in the switching magnets.
  • Another embodiment of the invention relates to damping the armature movement shortly before reaching the end positions.
  • the base point of one of the springs or spring assemblies assigned to the oscillatory system can be adjusted according to further developments of the invention.
  • the magnetic resistance of the magnetic circuit of one or both working magnets is changed when the ratio of the transmission system changes and thus when the effective spring forces change, with the aim of changing the time between the switching off of the current Keep working magnets and the beginning of the armature movement, hereinafter called fall time, constant.
  • both the change in the magnetic resistance and the adjustment of the translation of the transmission element and the equilibrium position of the vibrating system are carried out by a common device.
  • the invention advantageously changes the switching stroke of the adjusting device and thus the effective opening cross-section of the lifting valve or flat slide valve while largely maintaining the compact dimensions of the adjusting device. Furthermore, compared to the arrangement of an actuating device in a direct extension of the shaft of the control element, an increase in the maximum stroke of the control element is possible. A further advantage is that the actuating device can be arranged around the valve stem within a radius predetermined by the transmission system, and thus greater freedom of design for the receiving housing is achieved. The invention also enables an exact adjustment of the equilibrium position of the vibrating system in the installed state, and the tracking of the equilibrium position of the vibrating system when the transmission ratio of the transmission system changes.
  • FIG. 1 shows an example of an electromagnetically operating actuating device with electromagnets 1 and 2, windings 3 and 4 and armature 5.
  • the electromagnets 1 and 2 are fixed in by a cover 6 and with the interposition of a cam ring 7 Housing 8 clamped.
  • the armature 5 is guided in a sleeve 53 and actuates a valve 12 via a rocker arm 10.
  • Pressure springs 13, 14 and 50 form the oscillating system, taking into account the transmission ratio of the rocker arm 10 with the armature 5, the rocker arm 10 and the valve 12.
  • the spring 14 is supported on the stem of the valve 12 via a spring plate 17.
  • the movement of the armature 5 is delayed near the pole face of the magnet 2 by compressing air.
  • the cam ring 7 is provided with shoulders such that the outflow cross-section 58 between the armature 5 and the cam ring 7 is reduced before the armature 5 hits the pole face.
  • the rocker arm 10 is supported in the adjusting member 52 via a hydraulic length compensation element 51.
  • the acting force of the prestressed compression spring 14 is supported on the valve seat 16 via the spring plate 17, the stem of the valve 12 and the valve plate 15.
  • the armature 5 rests on the switching magnet 2, with a holding force that is greater than the force of the prestressed compression spring 13 minus the force of the spring 50.
  • the rocker arm 10 is force-free, so that the hydraulic compensating element 51 used compensate for the lengthening that occurs can and thus ensures that when the armature 5 rests on the pole face of the electromagnet 2, the valve plate 15 rests in the valve seat 16.
  • a soft magnetic bushing 55 supported in the adjusting member 52 on an inclined plane 54 changes the prestressing of the spring 50 when the adjusting member 52 is actuated and thus corrects the equilibrium position of the oscillating system. Furthermore, the soft magnetic sleeve 55 contains an annular recess 56 which, when the sleeve 55 moves, is displaced relative to a magnetically non-permeable ring 57 arranged in the magnet 1. Depending on the position of the soft magnetic sleeve 55, this results in a different magnetic resistance in the magnetic circuit of the magnet 1.
  • the adjusting member 52 is moved to the left. This shortens the lever arm l 1 and the lever arm l 2 is extended. This increases both the biasing force of the spring 14 acting on the armature 5 and the spring stiffness which is reduced on the armature side.
  • the biasing force of the spring 50 is reduced by the movement of the sleeve 55.
  • the increasing with increasing stroke holding forces on the opening magnet 1 are compensated for by reducing the magnetic resistance in the magnet 1, so that the required holding current and the fall time of the armature remain constant. This change is also caused by the movement of the sleeve 55.
  • the process is analogous when the stroke is reduced.
  • Figure 2 shows an electromagnetic actuator with a hydraulic transmission system consisting of the electromagnets 1 and 2, the armature 5, the valve 12 and the springs 13, 14 and 50.
  • the armature 5 displaces oil from a space 60 during its movement is located in cover 63 of the actuating device, through line 61 in cylinder 62.
  • cylinder 62 there is a three-part piston consisting of mushroom 64 and bushes 65 and 66. These have a bore 67 and 68 on the circumference, as well as cylinder 62 The bores of all three components are aligned when the valve 12 is in the closed position.
  • the adjusting member 69 has at its end a pin-shaped projection 70 which is guided in a bore 71 of the cylinder 62 and can engage in the bores 67 and 68 when the adjusting member 69 is displaced . This allows the sockets 65 and 66 to be locked.
  • the transmission ratio results from the ratio of the diameters of the acting cylinders d1 to d2, d3 and d4.
  • the adjusting member 69 has an inclined plane 73 which adjusts the prestress of the spring 50 via a bush 74 and a spring plate 75 and thus the equilibrium position of the oscillating one Systems tracks.
  • FIGS. 3 and 4 show an arrangement of 2 rocker arms 20 and 21 for actuating two valves or slides 22 and 23, respectively.
  • FIG. 5 shows an arrangement for actuating two valves or slides by means of a common rocker arm 26. This enables two or more valves or slides to be actuated with a small valve spacing.
  • Figure 6 shows a device for adjusting the equilibrium position of the vibrating system.
  • the position of the base point of the spring 13 is adjusted via two components 27 and 28 with wedge surfaces.
  • the component 27 is guided in a bore 29 of the housing 8.
  • Component 28 lies on the flat bottom 30 of the bore 29 and contains a radial threaded bore 31.
  • a bolt 32 is locked in the housing 8 by a stop 33 in its axial displacement and moves the component 28 in the direction of the longitudinal axis of the bolt when it rotates.
  • the device is self-locking.
  • FIG. 7 shows a device for adjusting the equilibrium position in accordance with the previously described type, but here a screw 34 with a wedge-shaped beveled surface 35 forms the counterpart to component 27.
  • the wedge surfaces lie only at a precisely defined position per revolution of the screw 34, so that the equilibrium position is set in discrete steps.
  • the device described is self-locking.
  • FIG. 8 shows a device for adjusting the equilibrium position, which is accessible in an axis parallel to the longitudinal axis 85 of the adjusting device.
  • a lever 36 rests on an abutment 37 and is positioned by an adjusting screw 38, which is supported in the housing 8.
  • the other end of the adjusting lever 36 acts on a spring support via a guided pin 39 40.
  • the device described is self-locking if the thread pitch of the screw 38 is chosen accordingly.
  • FIG. 9 shows a further possible arrangement of a hydraulic compensating element 76 between the housing 8 and the magnet 2 of an electromagnetic actuating device assigned to the closed position.
  • the axially displaceable assembly consisting of the magnets 1 and 2 and the lifting ring 7, can establish the frictional connection between the armature 5, rocker arm 10 and valve by the force of a compression spring acting in the compensating element 76.
  • FIGS. 10 and 11 show further possible arrangements of the compensating element on the rocker arm 10.
  • FIG. 12 shows a possible arrangement of the actuating unit 43, transmission element 10 and control element 12, the force being transmitted via a push rod 44.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Servomotors (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)
  • Switches With Compound Operations (AREA)
  • Massaging Devices (AREA)

Claims (17)

  1. Dispositif de positionnement fonctionnant par voie électromagnétique pour au moins un élément de distribution (12) susceptible d'être animé d'un mouvement oscillant et destiné à des machines à déplacement ou volumétriques, en particulier pour tiroirs plans et soupapes à mouvements alternatifs, dispositif qui comprend deux électroaimants de commutation ou de changement de position (1, 2) correspondant à la position ouverte et à la position fermée de l'élément de distribution (12) ou des éléments de distribution, au nombre d'un au moins, qui comprend une armature (5) disposée entre les deux électroaimants de commutation (1, 2) et déterminant la position de l'élément de distribution (12), et qui comprend un système à ressort (13, 14, 50) pour la transmission oscillante de forces à l'armature (5) entre les positions de commutation, système qui est dimensionné de manière que le lieu de la position d'équilibre de l'armature (5) se trouve entre les deux positions de commutation, caractérisé par un système de transmission de forces (10, 52) variable, coopérant avec l'armature (5) et ledit élément de distribution (12), système par lequel l'armature (5) commute ledit élément de distribution (12) par l'intermédiaire de moyens (52, 54, 69, 73) pour changer le rapport de transmission, le système de transmission étant relié au système capable d'osciller constitué du système à ressort (13, 14, 50), de l'armature (5) et de l'élément de distribution (12), de manière que la position d'équilibre de l'armature (5) soit ajustable, ainsi que par un dispositif commun (52) pour la variation simultanée du rapport de transmission et de la réluctance (55, 56, 57) dans le circuit magnétique d'un ou des deux électroaimants (1, 2), en vue du réglage des temps de décollage de l'armature (5), de même que pour l'adaptation de la position d'équilibre du système oscillant aux nouvelles forces de ressort, par le changement de l'emplacement d'un ou plusieurs points d'appui de ressort.
  2. Dispositif de positionnement selon la revendication 1, caractérisé en ce que le système de transmission est un mécanisme (10, 51, 52) à transmission mécanique.
  3. Disposition de positionnement selon la revendication 1 ou 2, caractérisé en ce que le système de transmission comporte une pièce mécanique transmettant des efforts de pression, en particulier une tige-poussoir (44).
  4. Dispositif de positionnement selon la revendication 1, caractérisé en ce que le système de transmission est un mécanisme (60-71) à transmission hydraulique.
  5. Dispositif de positionnement selon une des revendications 1-4, caractérisé en ce que le système à ressort est réparti sur plusieurs ressorts (13, 50 et 14) placés des deux côtés du système de transmission.
  6. Dispositif de positionnement selon la revendication 5, caractérisé en ce que les ressorts (13, 50 et 14), placés des deux côtés du système de transmission sont formés de plusieurs ressorts séparés ayant des raideurs différentes.
  7. Dispositif de positionnement selon une des revendications 1 à 6, caractérisé en ce qu'un système de transmission (26) coopère chaque fois avec plusieurs éléments de distribution.
  8. Dispositif de positionnement selon la revendication 1, caractérisé en ce que la position d'équilibre est ajustable au moyen de deux faces de coin (27, 28) mobiles en translation l'une par rapport à l'autre.
  9. Dispositif de positionnement selon la revendication 8, caractérisé en ce que les faces de coin (27, 28) sont mutuellement déplaçables en translation à l'aide d'une liaison filetée (32).
  10. Dispositif de positionnement selon la revendication 8 ou 9, caractérisé en ce que l'une des faces de coin (35) est reliée fixe à la partie mobile de la liaison filetée (34).
  11. Dispositif de positionnement selon la revendication 1, caractérisé en ce que la position d'équilibre est ajustable par un organe de transmission sous la forme d'un culbuteur ou d'un levier d'entraînement (36).
  12. Dispositif de positionnement selon une des revendications 1 à 7, caractérise par au moins un élément (51) de compensation de jeu de soupape pour compenser le jeu provoqué par le système de transmission ou se produisant sur ce système.
  13. Dispositif de positionnement selon la revendication 12, caractérisé en ce que l'élément (51, 76) de compensation de jeu de soupape est disposé soit du côté de l'élément de distribution soit du côté de l'électroaimant dans le système de transmission.
  14. Dispositif de positionnement selon la revendication 12, caractérisé en ce que l'élément (76) de compensation de jeu est placé entre le montage du système de transmission et le carter (8) fixe.
  15. Dispositif de positionnement selon la revendication 12, caractérisé en ce que l'élément (76) de compensation de jeu est placé entre l'électroaimant de fermeture (2) et le carter (8).
  16. Dispositif de positionnement selon une des revendications 1 à 15, caractérisé en ce que des aimants permanents sont disposés dans l'un ou dans les deux électroaimants (1, 2).
  17. Dispositif de positionnement selon une des revendications 1 à 16, caractérisé en ce que le mouvement du système de communication est amorti près des positions extrêmes, dans l'une ou dans les deux directions de mouvement (58).
EP90110559A 1989-06-27 1990-06-05 Dispositif électromagnétique de positionnement Expired - Lifetime EP0405187B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90110559T ATE95277T1 (de) 1989-06-27 1990-06-05 Elektromagnetisch arbeitende stelleinrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3920931 1989-06-27
DE3920931A DE3920931A1 (de) 1989-06-27 1989-06-27 Elektromagnetisch arbeitende stelleinrichtung

Publications (2)

Publication Number Publication Date
EP0405187A1 EP0405187A1 (fr) 1991-01-02
EP0405187B1 true EP0405187B1 (fr) 1993-09-29

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Application Number Title Priority Date Filing Date
EP90110559A Expired - Lifetime EP0405187B1 (fr) 1989-06-27 1990-06-05 Dispositif électromagnétique de positionnement

Country Status (4)

Country Link
US (1) US5117213A (fr)
EP (1) EP0405187B1 (fr)
AT (1) ATE95277T1 (fr)
DE (2) DE3920931A1 (fr)

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Also Published As

Publication number Publication date
US5117213A (en) 1992-05-26
EP0405187A1 (fr) 1991-01-02
ATE95277T1 (de) 1993-10-15
DE59002881D1 (de) 1993-11-04
DE3920931A1 (de) 1991-01-03

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