EP0441909B1 - Valve control device with magnetic valve for internal combustion engines - Google Patents
Valve control device with magnetic valve for internal combustion engines Download PDFInfo
- Publication number
- EP0441909B1 EP0441909B1 EP90910571A EP90910571A EP0441909B1 EP 0441909 B1 EP0441909 B1 EP 0441909B1 EP 90910571 A EP90910571 A EP 90910571A EP 90910571 A EP90910571 A EP 90910571A EP 0441909 B1 EP0441909 B1 EP 0441909B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- reservoir
- space
- piston
- valve control
- 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
Links
Images
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
- 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
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
- F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
- F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
-
- 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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34446—Fluid accumulators for the feeding circuit
Definitions
- the invention relates to a valve control device with a solenoid valve for internal combustion engines according to the preamble of the main claim.
- the liquid reservoir is integrated into the solenoid valve , wherein the valve member serves as a storage piston, which has a storage space separates from a magnetic space, the connection between the valve inlet and the storage space being controlled via the one end edge of the storage piston in cooperation with the valve seat.
- the magnet counteracts the memory escape direction, since in the special exemplary embodiment the solenoid valve is to be de-energized, ie it is only to be blocked under voltage.
- valve control device according to the preamble of claim 1 is also previously known.
- the liquid store is provided as a separate store, which is arranged downstream of the solenoid valve.
- the memory serves to receive quantities of pressure medium drawn from the stroke transmission chamber via the solenoid valve and, at the same time, also serves to supply lifting medium to the transmission chamber when the solenoid valve and the relieved stroke transmission chamber are closed, for which purpose a bypass line containing a check valve is provided in parallel with the solenoid valve.
- the solenoid valve and the separate memory which are each assigned to a single engine valve, take up a relatively large amount of space.
- the valve control device with the characterizing features of claim 1 has the Advantage that the combined storage valve unit is constructed much simpler, for example as a spring only has the storage spring.
- the permissible tolerance range with regard to the forces and pressures is also expanded in that the storage piston no longer has to assume an intermediate position when the magnet is not excited, but is held in its end position by the storage spring.
- the static pressure that can be generated by the accumulator piston due to the accumulator spring must be greater than the leakage-compensating supply pressure, but in any case must be less than the hydraulic pressure from the stroke transmission chamber of the engine inlet valve.
- the magnet itself can advantageously be designed in a wide variety of ways - the only important thing is that when the solenoid coil is excited, the storage piston as a movable valve member is briefly lifted off its seat in order to then be moved further by the fluid pressure from the engine valve as a storage device. A trigger pulse is sufficient to effect this lifting.
- Another advantage is that the control of the valve is not dependent on a mechanical spring, the force of which must be limited to a relatively low value due to the force ratio described above, so that a certain inertia of this control is the result, but that Driven by the electromagnet, with the resulting high response speed.
- the storage piston is pot-shaped and has a pot bottom facing the storage space, the edge of which cooperates with a valve seat between the valve inlet and the storage space and which is guided radially on an inner wall of the control valve housing and with a central housing-fixed pin as a magnetic yoke dives into the pot opening.
- the magnet coil is arranged in the magnet space formed between the peg and the inner wall, as a result of which the assembly of the storage magnet valve unit can be simplified, but the construction volume can also be minimized.
- a central bore for relieving the magnetic space is present in the journal, which brings considerable connection advantages.
- a throttle opening is present in the pot base separating the magnet space and the storage space. to ensure that the accumulator piston comes back to the valve seat after sealing the engine valve pressure.
- the storage space is connected to the crankcase via a throttle bore and a check valve opening towards the storage space.
- the pin can serve as a stroke stop of the storage piston and also have a blind bore into which the storage spring partially dips.
- This blind bore can be at least so deep that it fully absorbs the spring when it is compressed into a block. This also saves additional space that benefits the volume of the storage space.
- the magnetic coil is electrically switched off after the storage piston has been lifted off the valve seat. This saves considerable electrical energy, since only one pulse is sufficient for the actual actuation of the solenoid valve, because the further opening, if there is any possibility of control, is effected by the engine valve pressure.
- the most Control variables attacking the storage piston in the form of the engine valve pressure and the storage spring force are not additionally superimposed by magnetic forces.
- FIG. 1 shows a longitudinal section through a valve control device with an uncut storage-solenoid valve unit
- FIG. 2 shows a longitudinal section through the storage-solenoid valve unit on an enlarged scale.
- valve control device shown in FIG. 1 for an intake or exhaust valve 10 of an internal combustion engine is arranged between a valve stem 12 carrying a valve member 11 and a valve control cam 14 rotating with a camshaft 13.
- the valve stem 12 is axially displaceably guided in a valve housing 15 and lies with the valve member 11 under the action of two valve closing springs 16, 17 on a valve seat 18 in the valve housing 15, which surrounds a valve inlet or valve outlet opening 19.
- the valve control device has a control housing 20 placed on the valve housing 15, in which a housing chamber 21 is arranged coaxially with a spring chamber 22 in the valve housing 15, in which the valve closing springs 16, 17 are accommodated coaxially to one another.
- a housing block 23 having a central axially continuous housing bore 24 is inserted from below into the housing chamber 21.
- a valve piston 25 connected to the valve stem 12 and a piston part 26 of a cam piston 27 arranged above it are axially displaceable.
- the cam piston 27 is pressed against the valve control cam 14 by a return spring 28 which is supported in the housing block 23.
- the piston part 26 is pressed positively against the cam piston 27 via the return spring 28.
- the valve piston 25 and the piston part 26 delimit an oil-filled stroke transmission chamber 29, the axial length effective between the cam piston 27 and the valve piston 25 can be changed by relative movement of the pistons.
- the stroke transfer chamber 29 is connected via a line 30 to a cylindrical magnetic control valve 31, which is shown in an uncut form in FIG.
- any leakage quantities of oil flowing out of the valve control device are discharged from a reservoir 32 via a delivery line 33 compensated by means of a feed pump 34, the line 33 being branched into a line 35 which opens into the line 30 connecting the stroke transmission chamber 29 and the solenoid control valve 31 and into a line 36 which leads to the solenoid control valve 31, to the lower end thereof.
- a check valve 37 and 38 opening in the direction of the solenoid control valve 31 is arranged.
- the maximum delivery pressure of the delivery pump 34 is limited by a pressure relief valve 39, so that a certain supply pressure of the oil is not exceeded.
- the amount of oil present in the stroke transmission chamber 29 can be controlled by the solenoid control valve 31, which is shown in section in FIG. 2.
- a pot-shaped storage piston 41 is arranged axially displaceably and radially sealing in the solenoid valve housing 40.
- This storage piston 41 separates an inlet space 42 from a storage space 43 and a magnet space 44 in the illustrated closed position of the solenoid valve.
- the storage piston 41 is loaded by a storage spring 45 which also acts as a closing spring and has a throttle bore 46 on the piston head through which the storage space 43 and the magnet space 44 are connected to one another.
- a throttle bore 56 is provided between the storage space 43 and the check valve 38.
- the storage spring 45 is supported on the side facing away from the storage piston 41 from a pin 47 of a housing cover 48 arranged axially with the storage piston 41, a blind bore 49 being provided for receiving a section of the storage spring 45 at the free end of the pin 47.
- a leak channel 50 is present in the pin 47, which leads to the oil container 32 via a leak line 51.
- a magnetic coil 52 is arranged in the annular space of the magnetic space 44 formed by the magnetic valve housing 40 and the pin 47.
- this annular space into which the storage piston 41 dips with its annular walls when displaced against the storage spring 45, is connected to the leakage channel 50 via a leak hole 53 in order to avoid, when immersed, that a liquid jam occurs between the magnet coil 52 and the storage piston 41 within the magnet space 44 .
- valve control device works as follows: for the operation of the internal combustion engine, the valve control cam 14 lifts the valve plate 11 down from the valve seat at the given time and the inlet channel to the combustion chamber is opened.
- the piston part 26, which is filled with oil is displaced into the housing bore 24 via the cam piston 27 and counter to the force of the return spring 28.
- the valve piston 25 is displaced downward by the oil as an almost inelastic force transmitter and thereby displaces the valve stem 12 including the valve plate 11 against the force of the valve closing springs 16 and 17.
- the opening stroke of the engine valve 10 corresponds to the height of the valve control cam 14, since the piston part 26 and the valve piston 25 have the same working diameter.
- This working stroke of the valve stem 12 is changed by the solenoid control valve 31 when the time cross section between the valve plate 11 and the valve seat 18 is sufficiently large, for example if the engine speed is to be reduced by reducing this time cross section. In this case, the amount of fuel / air mixture drawn into the combustion chamber is reduced in accordance with the time cross section.
- the solenoid valve 31 is selectively opened from a certain working stroke, in that the coil 52 is excited and at least the valve edge 54 of the accumulator piston 41 lifts off the valve seat 55 by the first current pulse, so that the pressure prevailing in the stroke transmission chamber 29 overcomes the line 30 transmits into the storage space 43 in order to push it upward against the force of the storage spring 45 by acting on the lower face of the storage piston 41.
- the volume in the stroke transmission chamber 29 is reduced by this volume swallowed by the memory. Due to the action of the springs 16 and 17, the valve plate 11 closes prematurely.
- valve control cam 14 As valve control cam 14 continues to rotate, it reaches the basic circle position shown, in which piston part 26 is pushed all the way up again by return spring 28. During this movement, the accumulator piston 41 of the solenoid control valve 31, driven by the accumulator spring 45, displaces the oil in front of it via the line 30 back into the stroke transmission chamber 29 until the accumulator piston 41 rests with its valve edge 54 on the valve seat 55.
- any cavities in the valve inlet space 42 of the line 30 or the stroke transmission chamber 29 are filled with oil via the feed pump 34 and the feed line 33, with backflow through the check valve 37 being prevented, so that when the valve control cams 14 drive again, the initial situation is reached again.
- the throttle bore 46 in the bottom of the accumulator piston 41 ensures that there is no back pressure in the accumulator space 43, ie it is achieved that the accumulator piston 41 lies snugly on the valve seat 55.
- oil flows continuously from the feed pump 34 into the storage space 43 and from there via the throttle bore 46 into the magnet space 44 and back into the oil container 32, so that here a constant filling of the storage space 43 under constant low pressure is guaranteed.
- the preferably provided throttle 56 between the check valve 38 and the storage space 43 is smaller in diameter than the throttle 46 and causes Changes in the engine oil pressure serving as system pressure only have an attenuated effect on the pressure in the storage space.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Die Erfindung geht aus von einer Ventilsteuervorrichtung mit Magnetventil für Brennkraftmaschinen nach der Gattung des Hauptanspruchs.The invention relates to a valve control device with a solenoid valve for internal combustion engines according to the preamble of the main claim.
Bei einer bereits vorgeschlagenen Ventilsteuervorrichtung zum Steuern der Schließ- und Öffnungszeit eines von einem Ventilsteuernocken einer Nockenwelle über einen axial verschiebbaren Ventilschaft betätigen Motorventils (EP-A 0 341 440) (Stand der Technik gemäß Art. 54.3 EPÜ) ist der Flüssigkeitsspeicher in das Magnetventil integriert, wobei das Ventilglied als Speicherkolben dient, der einen Speicherraum von einem Magnetraum trennt, wobei die Verbindung zwischen Ventileinlaß und Speicherraum über die eine Stirnkante des Speicherkolbens in Zusammenwirkung mit dem Ventilsitz gesteuert wird. Der Magnet wirkt der Speicherausweichrichtung entgegen, da bei dem speziellen Ausführungsbeispiel das Magnetventil stromlos, offen d. h. nur unter Spannung gesperrt sein soll. Hierdurch soll sichergestellt werden, daß bei Steckerabfall am Magnetventil der Motor nicht durchgehen kann. Die Folge ist jedoch, daß der Motor bei einem solchen Steckerabfall stehen bleibt. Um obere vorgeschlagene Ausgestaltung der Erfindung zu erhalten, bei der einerseits der Flüssigkeitsspeicher im Magnetventil integriert ist und bei dem andererseits das Magnetventil stromlos geöffnet sein soll, ist ein nicht unerheblicher, insbesondere konstruktiver Aufwand erforderlich, vor allem deshalb, weil die mechanischen Verstellkräfte - einerseits die Speicherkraft und andererseits die Öffnungskraft - des Magnetventils einander entgegenwirken, so daß mindestens zwei Federn am als Ventilglied dienenden Speicherkolben angreifen müssen. Es muß nicht nur der dafür erforderliche Raum vorhanden sein, sondern es müssen auch diese beiden Federn sehr genau aufeinander abgestimmt sein, was vor allem deshalb aufwendig ist, weil bei dieser Abstimmung auch die durch die hydraulischen Drücke bewirkten Kräfte berücksichtigt werden müssen. So ist es erforderlich, daß der statische Druck, der durch die Speicherfeder am Speicherkolben angreift kleiner sein muß als der Hydraulikdruck, der durch das Motorventil bewirkt wird und am Speicherkolben angreift. Nur so ist die gewünschte Speicherwirkung möglich. Andererseits muß dieser statische Druck aber größer sein als der Ölversorgungsdruck mit dem Leck- und Abschlußverluste des Hydrauliköls aus der Ventilsteuervorrichtung ausgeglichen werden. Nur so ist gewährleistet, daß der Speicherkolben bei Abbau des Motorventildruckes wieder in die Ausgangsstellung gelangt, aus der er bei Erregung des Magnets in die Ventilschließstellung gefahren werden kann oder umgekehrt, bei Abbau der Erregung und Aufbau des Stößeldruckes ausweichen kann.In a previously proposed valve control device for controlling the closing and opening times of an engine valve actuated by a valve control cam of a camshaft via an axially displaceable valve stem (EP-A 0 341 440) (prior art according to Art. 54.3 EPC), the liquid reservoir is integrated into the solenoid valve , wherein the valve member serves as a storage piston, which has a storage space separates from a magnetic space, the connection between the valve inlet and the storage space being controlled via the one end edge of the storage piston in cooperation with the valve seat. The magnet counteracts the memory escape direction, since in the special exemplary embodiment the solenoid valve is to be de-energized, ie it is only to be blocked under voltage. This is to ensure that the motor cannot run through if the plug on the solenoid valve falls off. The consequence, however, is that the motor stops in the event of such a plug drop. In order to obtain the above proposed embodiment of the invention, in which on the one hand the liquid reservoir is integrated in the solenoid valve and on the other hand in which the solenoid valve is to be opened when deenergized, a not inconsiderable, in particular constructional effort is required, above all because the mechanical adjusting forces - on the one hand the Storage force and on the other hand, the opening force - of the solenoid valve counteract each other, so that at least two springs must act on the storage piston serving as a valve member. Not only must the space required for this be available, but these two springs must also be coordinated very precisely with one another, which is particularly complex because the forces caused by the hydraulic pressures must also be taken into account in this coordination. So it is necessary that the static pressure that acts on the storage piston by the storage spring must be less than that Hydraulic pressure, which is caused by the engine valve and acts on the accumulator piston. This is the only way to achieve the desired storage effect. On the other hand, this static pressure must be greater than the oil supply pressure with the leakage and termination losses of the hydraulic oil from the valve control device. This is the only way to ensure that the accumulator piston returns to the starting position when the engine valve pressure is reduced, from which it can be moved to the valve closing position when the magnet is excited or vice versa, when the excitation is reduced and the tappet pressure builds up.
Um den Sicherheits- und Komfortanforderungen bei einem Kraftfahrzeug zu genügen, reicht obengenannte Abstellsicherung bei Steckerabfall am Magnetventil nicht aus. Ein solcher Steckerabfall kann nämlich den Fall nicht vermeiden, bei dem das Magnetventil im erregten Zustand festklemmt und der Motor dann möglicherweise durchgehen könnte. Es sind also zusätzliche die Kraftstoffzufuhr oder -zündung abschaltende Einrichtungen unabdingbar.In order to meet the safety and comfort requirements in a motor vehicle, the above-mentioned parking lock in the case of a plug drop on the solenoid valve is not sufficient. Such a plug drop cannot avoid the case in which the solenoid valve is stuck in the excited state and the motor could then possibly run through. Additional devices that switch off the fuel supply or ignition are therefore essential.
Durch die US-A-4 765 288 ist ferner eine Ventilsteuervorrichtung gemäß der Gattung des Patentanspruchs 1 vorbekannt. Bei dieser Ventilsteuereinrichtung ist der Flüssigkeitsspeicher als separater Speicher vorgesehen, der stromabwärts des Magnetventils angeordnet ist. Der Speicher dient der Aufnahme von der Hubübertragungskammer über das Magnetventil entnommenen Druckmittelmengen und dient zugleich auch bei geschlossenem Magnetventil und entlasteter Hubübertragungskammer der Zuführung von Hubmittel zur Übertragungskammer, wozu parallel zum Magnetventil eine ein Rückschlagventil enthaltende Bypassleitung vorgesehen ist. Das Magnetventil und der separate Speicher, die jeweils einem einzelnen Motorventil zugeordnet sind, nehmen einen verhältnismäßig großen Bauraum ein.From US-A-4 765 288 a valve control device according to the preamble of claim 1 is also previously known. In this valve control device, the liquid store is provided as a separate store, which is arranged downstream of the solenoid valve. The memory serves to receive quantities of pressure medium drawn from the stroke transmission chamber via the solenoid valve and, at the same time, also serves to supply lifting medium to the transmission chamber when the solenoid valve and the relieved stroke transmission chamber are closed, for which purpose a bypass line containing a check valve is provided in parallel with the solenoid valve. The solenoid valve and the separate memory, which are each assigned to a single engine valve, take up a relatively large amount of space.
Die erfindungsgemäße Ventilsteuervorrichtung, mit den kennzeichnenden Merkmalen des Patentanspruches 1 hat den Vorteil, daß die kombinierte Speicherventileinheit wesentlich einfacher aufgebaut ist, beispielsweise als Feder nur noch die Speicherfeder aufweist. Der zulässige Toleranzbereich bezüglich der Kräfte und Drücke ist auch dadurch erweitert, daß der Speicherkolben bei nicht erregtem Magnet nicht mehr eine Zwischenstellung einnehmen muß, sondern in seiner Endstellung durch die Speicherfeder gehalten wird. Natürlich gilt auch hier, daß der vom Speicherkolben aufgrund der Speicherfeder erzeugbare statische Druck größer sein muß als der leckagenausgleichende Versorgungsdruck, in jedem Fall aber kleiner sein muß als der Hydraulikdruck von der Hubübertragungskammer des Motoreinlaßventils her. Der Magnet selbst kann vorteilhafterweise in der unterschiedlichsten Art gestaltet sein - maßgebend ist nur, daß bei Erregung der Magnetspule der Speicherkolben als bewegliches Ventilglied kurz von seinem Sitz abgehoben wird um dann durch den Flüssigkeitsdruck vom Motorventil als Speicher weiterverschoben zu werden. Hierzu genügt bereits ein Ansteuerimpuls, um dieses Abheben zu bewirken. Ein weiterer Vorteil besteht darin, daß die Aufsteuerung des Ventils nicht in Abhängigkeit von einer mechanischen Feder erfolgt, deren Kraft aufgrund des oben beschriebenen Kräfteverhältnisses auf einen verhältnismäßig niederen Wert begrenzt sein muß, so daß eine gewisse Trägheit dieser Aufsteuerung die Folge ist, sondern daß der Antrieb durch den Elektromagneten erfolgt, mit der dadurch möglichen hohen Ansprechschnelligkeit.The valve control device according to the invention with the characterizing features of claim 1 has the Advantage that the combined storage valve unit is constructed much simpler, for example as a spring only has the storage spring. The permissible tolerance range with regard to the forces and pressures is also expanded in that the storage piston no longer has to assume an intermediate position when the magnet is not excited, but is held in its end position by the storage spring. Of course, it also applies here that the static pressure that can be generated by the accumulator piston due to the accumulator spring must be greater than the leakage-compensating supply pressure, but in any case must be less than the hydraulic pressure from the stroke transmission chamber of the engine inlet valve. The magnet itself can advantageously be designed in a wide variety of ways - the only important thing is that when the solenoid coil is excited, the storage piston as a movable valve member is briefly lifted off its seat in order to then be moved further by the fluid pressure from the engine valve as a storage device. A trigger pulse is sufficient to effect this lifting. Another advantage is that the control of the valve is not dependent on a mechanical spring, the force of which must be limited to a relatively low value due to the force ratio described above, so that a certain inertia of this control is the result, but that Driven by the electromagnet, with the resulting high response speed.
Nach einer vorteilhaften Ausgestaltung der Erfindung ist der Speicherkolben topfförmig ausgebildet und weist einen, dem Speicherraum zugewandten Topfboden auf, dessen Kante mit einem zwischen Ventileinlaß und Speicherraum vorhandenen Ventilsitz zusammenwirkt und der radial an einer Innenwand des Steuerventilgehäuses geführt ist und wobei ein zentraler gehäusefester Zapfen als Magnetjoch in die Topföffnung taucht. Durch die entsprechende Gestaltung der Zapfenaußenfläche und der Topfinnenfläche ist eine Optimierung des Magnetflusses und damit der Magnetkräfte erzielbar. Außerdem wird eine günstige Raumaufteilung erreicht, was einer Verkleinerung der Speicher-Magnetventileinheit entgegenkommt.According to an advantageous embodiment of the invention, the storage piston is pot-shaped and has a pot bottom facing the storage space, the edge of which cooperates with a valve seat between the valve inlet and the storage space and which is guided radially on an inner wall of the control valve housing and with a central housing-fixed pin as a magnetic yoke dives into the pot opening. An appropriate design of the outer surface of the spigot and the inner surface of the pot enables the magnetic flux and thus the magnetic forces to be optimized. In addition, a favorable division of space is achieved, which accommodates a downsizing of the storage solenoid valve unit.
Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist in dem zwischen Zapfen und Innenwand gebildeten Magnetraum die Magnetspule angeordnet, wodurch die Montage der Speicher-Magnetventileinheit vereinfachbar ist, aber auch das Bauvolumen minimierbar ist.According to a further advantageous embodiment of the invention, the magnet coil is arranged in the magnet space formed between the peg and the inner wall, as a result of which the assembly of the storage magnet valve unit can be simplified, but the construction volume can also be minimized.
Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist im Zapfen eine zentrale Bohrung zur Entlastung des Magnetraums vorhanden, was erhebliche Anschlußvorteile mit sich bringt.According to a further advantageous embodiment of the invention, a central bore for relieving the magnetic space is present in the journal, which brings considerable connection advantages.
Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist in dem Magnetraum und Speicherraum trennenden Topfboden eine Drosselöffnung vorhanden, um sicherzustellen, daß der Speicherkolben nach Abbau des Motorventildruckes wieder dichtend auf den Ventilsitz gelangt.According to a further advantageous embodiment of the invention, a throttle opening is present in the pot base separating the magnet space and the storage space. to ensure that the accumulator piston comes back to the valve seat after sealing the engine valve pressure.
Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist der Speicherraum über eine Drosselbohrung und ein zum Speicherraum hin öffnendes Rückschlagventil mit dem Kurbelgehäuse verbunden. Durch die Drossel wirken sich Änderungen bei dem als Systemdruck verwendeten Motoröldruck nur noch in abgeschwächter Form auf den Druck im Speicherraum aus.According to a further advantageous embodiment of the invention, the storage space is connected to the crankcase via a throttle bore and a check valve opening towards the storage space. As a result of the throttle, changes in the engine oil pressure used as the system pressure only have a reduced effect on the pressure in the storage space.
Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung kann der Zapfen als Hubanschlag des Speicherkolbens dienen und außerdem eine Sackbohrung aufweisen, in die die Speicherfeder teilweise taucht. Diese Sackbohrung kann mindestens so tief sein, daß sie die Speicherfeder voll aufnimmt, wenn diese zu einem Block zusammengedrückt ist. Außerdem wird dadurch weiterer Raum gespart, der dem Volumen des Speicherraums zugutekommt.According to a further advantageous embodiment of the invention, the pin can serve as a stroke stop of the storage piston and also have a blind bore into which the storage spring partially dips. This blind bore can be at least so deep that it fully absorbs the spring when it is compressed into a block. This also saves additional space that benefits the volume of the storage space.
Nach einer weiteren Ausgestaltung der Erfindung wird die Magnetspule nach Abheben des Speicherkolbens vom Ventilsitz elektrisch abgestellt. Hierdurch wird erhebliche elektrische Energie eingespart, da zur tatsächlichen Betätigung des Magnetventils nur ein Impuls genügt, weil das weitere Öffnen sofern überhaupt eine Steuermöglichkeit besteht, durch den Motorventildruck erfolgt. Hinzu kommt der Vorteil, daß die am Speicherkolben angreifenden Steuergrößen in Form des Motorventildrucks und der Speicherfederkraft nicht zusätzlich von Magnetkräften überlagert werden.According to a further embodiment of the invention, the magnetic coil is electrically switched off after the storage piston has been lifted off the valve seat. This saves considerable electrical energy, since only one pulse is sufficient for the actual actuation of the solenoid valve, because the further opening, if there is any possibility of control, is effected by the engine valve pressure. In addition, there is the advantage that the most Control variables attacking the storage piston in the form of the engine valve pressure and the storage spring force are not additionally superimposed by magnetic forces.
Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention can be found in the following description, the drawing and the claims.
Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und im folgenden näher beschrieben. Es zeigen Fig. 1 einen Längsschnitt durch eine Ventilsteuervorrichtung mit ungeschnittener Speicher-Magentventileinheit und Fig. 2 einen Längsschnitt durch die Speicher-Magnetventileinheit in vergrößertem Maßstab.An embodiment of the object of the invention is shown in the drawing and described in more detail below. 1 shows a longitudinal section through a valve control device with an uncut storage-solenoid valve unit, and FIG. 2 shows a longitudinal section through the storage-solenoid valve unit on an enlarged scale.
Die in Fig. 1 dargestellte Ventilsteuervorrichtung für ein Ein- oder Auslaßventil 10 einer Brennkraftmaschine ist zwischen einem ein Ventilglied 11 tragenden Ventilschaft 12 und einem mit einer Nockenwelle 13 umlaufenden Ventilsteuernocken 14 angeordnet. Der Ventilschaft 12 ist in einem Ventilgehäuse 15 axial verschiebbar geführt und liegt mit dem Ventilglied 11 unter der Wirkung zweier Ventilschließfedern 16, 17 auf einem Ventilsitz 18 im Ventilgehäuse 15 auf, der eine Ventilein- bzw. Ventilauslaßöffnung 19 umgibt. Die Ventilsteuervorrichtung weist ein auf das Ventilgehäuse 15 aufgesetztes Steuergehäuse 20 auf, in welchem eine Gehäusekammer 21 achsgleich zu einer Federkammer 22 im Ventilgehäuse 15 angeordnet ist, in der die Ventilschließfedern 16, 17 koaxial zueinander untergebracht sind. In die Gehäusekammer 21 ist von unten her ein Gehäuseblock 23 eingeschoben, der eine zentrale axial durchgehende Gehäusebohrung 24 aufweist. In der Gehäusebohrung 24 ist ein, mit dem Ventilschaft 12 verbundener Ventilkolben 25 und ein darüber angeordneter Kolbenteil 26 eines Nockenkolbens 27 axial verschiebbar. Der Nockenkolben 27 wird von einer im Gehäuseblock 23 sich abstützenden Rückstellfeder 28 an den Ventilsteuernocken 14 angepreßt. Der Kolbenteil 26 wird über die Rückstellfeder 28 formschlüssig an den Nockenkolben 27 gepreßt. Der Ventilkolben 25 und der Kolbenteil 26 begrenzen eine mit Öl gefüllte Hubübertragungskammer 29, deren zwischen Nockenkolben 27 und Ventilkolben 25 wirksame axiale Länge durch Relativbewegung der Kolben zueinander verändert werden kann. Die Hubübertragskammer 29 steht über eine Leitung 30 mit einem zylindrisch ausgebildeten Magnetsteuerventil 31 in Verbindung, welches in Fig. 1 ungeschnitten dargestellt ist und wobei die Leitung 30 radial auf das Magnetsteuerventil 31 stößt. Irgendwelche, aus der Ventilsteuereinrichtung abströmenden Leckmengen des Öls werden von einem Vorratsbehälter 32 aus über eine Förderleitung 33 mittels einer Förderpumpe 34 ausgeglichen, wobei die Leitung 33 aufgezweigt wird in eine Leitung 35, welche in die die Hubübertragungskammer 29 und das Magnetsteuerventil 31 verbindende Leitung 30 mündet und in eine Leitung 36, die zum Magnetsteuerventil 31 führt und zwar zu dessen unterer Stirnseite. In den Leitungen 35 und 36 ist jeweils ein, in Richtung zum Magnetsteuerventil 31 hin, öffnendes Rückschlagventil 37 und 38 angeordnet. Der maximale Förderdruck der Förderpumpe 34 wird durch ein Druckbegrenzungsventil 39 nach oben begrenzt, so daß ein bestimmter Versorgungsdruck des Öles nicht überschritten wird.The valve control device shown in FIG. 1 for an intake or
Durch das Magnetsteuerventil 31, das in Fig. 2 im Schnitt dargestellt ist, kann die, in der Hubübertragungskammer 29 vorhandene Ölmenge gesteuert werden. Hierfür ist im Magnetventilgehäuse 40 ein topfförmig ausgebildeter Speicherkolben 41 axial verschiebbar und radial dichtend angeordnet. Dieser Speicherkolben 41 trennt in der dargestellten Schließstellung des Magnetventils einen Einlaßraum 42 von einem Speicherraum 43 und einem Magnetraum 44. Der Speicherkolben 41 ist durch eine auch als Schließfeder wirkende Speicherfeder 45 belastet und weist am Kolbenboden eine Drosselbohrung 46 auf, durch die der Speicherraum 43 und der Magnetraum 44 miteinander verbunden sind. Nach einer bevorzugten Ausgestaltung ist zwischen Speicherraum 43 und Rückschlagventil 38 eine Drosselbohrung 56 vorgesehen. Die Speicherfeder 45 stützt sich auf der dem Speicherkolben 41 abgewandten Seite an einem achsgleich zum Speicherkolben 41 angeordneten Zapfen 47 eines Gehäusedeckels 48 ab, wobei zur Aufnahme eines Abschnitts der Speicherfeder 45 am freien Ende des Zapfens 47 eine Sackbohrung 49 vorgesehen ist. Außerdem ist im Zapfen 47 ein Leckkanal 50 vorhanden, der über eine Leckleitung 51 zum Ölbehälter 32 führt. In dem durch das Magnetventilgehäuse 40 und den Zapfen 47 gebildeten Ringraum des Magnetraums 44 ist eine Magnetspule 52 angeordnet. Außerdem ist dieser Ringraum, in den der Speicherkolben 41 bei Verschieben gegen die Speicherfeder 45 mit seinen Ringwänden taucht über eine Leckbohrung 53 mit dem Leckkanal 50 verbunden um bei dem Eintauchen zu vermeiden, daß zwischen Magnetspule 52 und Speicherkolben 41 innerhalb des Magnetraums 44 ein Flüssigkeitsstau entsteht.The amount of oil present in the
Die beschriebene Ventilsteuervorrichtung arbeitet wie folgt:
für den Betrieb der Brennkraftmaschine wird durch den Ventilsteuernocken 14 zu dem gegebenen Zeitpunkt der Ventilteller 11 vom Ventilsitz nach unten abgehoben und der Einlaßkanal zum Brennraum geöffnet. Hierfür wird über den Nockenkolben 27 und entgegen der Kraft der Rückstellfeder 28 der Kolbenteil 26 in die Gehäusebohrung 24 verschoben, welcher mit Öl gefüllt ist. Durch das Öl als nahezu unelastischer Kraftüberträger wird der Ventilkolben 25 nach unten verdrängt und verschiebt dabei den Ventilschaft 12 einschließlich Ventilteller 11 und zwar entgegen der Kraft der Ventilschließfedern 16 und 17. Bei unverändertem Flüssigkeitsvolumen in der Hubübertragungskammer 29 entspricht der Öffnungshub des Motorenventils 10 der Höhe des Ventilsteuernockens 14, da der Kolbenteil 26 und der Ventilkolben 25 den gleichen Arbeitsdurchmesser aufweisen. Dieser Arbeitshub des Ventilschafts 12 wird durch das Magnetsteuerventil 31 dann geändert, wenn der Zeitquerschnitt zwischen Ventilteller 11 und Ventilsitz 18 ausreichend groß ist, beispielsweise wenn durch Verkleinern dieses Zeitquerschnitts die Motordrehzahl verringert werden soll. Hierbei wird entsprechend dem Zeitquerschnitt die in den Brennraum gesaugte Kraftstoffluftgemischmenge verringert. Um diesen Zeitquerschnitt zu verringern wird gezielt ab einem bestimmten Arbeitshub das Magnetventil 31 geöffnet, indem die Spule 52 erregt wird und mindestens durch den ersten Stromimpuls die Ventilkante 54 des Speicherkolbens 41 vom Ventilsitz 55 abhebt, so daß sich der in der Hubübertragungskammer 29 herrschende Druck über die Leitung 30 in den Speicherraum 43 überträgt, um dort durch Beaufschlagung der unteren Stinseite des Speicherkolbens 41 diesen entgegen der Kraft der Speicherfeder 45 nach oben zu schieben. Um dieses vom Speicher geschluckte Volumen wird jenes in der Hubübertragungskammer 29 reduziert. Durch die Wirkung der Federn 16 und 17 schließt der Ventilteller 11 dadurch vorzeitig. Außerdem wird bei diesem Speichervorgang im kombinierten Speicher-Magnetventil 31 im Magnetraum 44 vorhandene Flüssigkeit über die Leckbohrung 53 bzw. den Leckkanal 50 und die Leckleitung 51 zum Ölbehälter 32 geleitet. Beim Weiterdrehen des Ventilsteuernockens 14 gelangt er in die gezeigte Grundkreisstellung, in der der Kolbenteil 26 durch die Rückstellfeder 28 wieder ganz nach oben geschoben wird. Bei dieser Bewegung verdrängt der Speicherkolben 41 des Magnetsteuerventils 31, durch die Speicherfeder 45 angetrieben, das ihm vorgelagerte Öl über die Leitung 30 zurück in die Hubübertragungskammer 29 bis der Speicherkolben 41 mit seiner Ventilkante 54 auf dem Ventilsitz 55 aufliegt. Irgendwelche sich in Ventileinlaßraum 42 der Leitung 30 oder der Hubübertragungskammer 29 einstellende Hohlräume, werden über die Förderpumpe 34 und die Förderleitung 33 mit Öl aufgefüllt, wobei ein Zurückfliessen durch das Rückschlagventil 37 verhindert wird, so daß bei einem neuerlichen Antrieb durch den Ventilsteuernocken 14 die Ausgangssituation wieder erreicht ist. Über die Drosselbohrung 46 im Boden des Speicherkolbens 41 wird erreicht, daß im Speicherraum 43 kein Staudruck entsteht d. h. es wird erreicht, daß der Speicherkolben 41 satt auf dem Ventilsitz 55 aufliegt. Über die Leitung 36 und das Rückschlagventil 38 strömt von der Förderpumpe 34 kontinuierlich Öl in den Speicherraum 43 und von dort über die Drosselbohrung 46 in den Magnetraum 44 und zurück in den Ölbehälter 32, so daß hier eine stetige Füllung des Speicherraums 43 unter konstantem niederen Druck gewährleistet ist. Die bevorzugt vorgesehene Drossel 56 zwischen Rückschlagventil 38 und Speicherraum 43 ist im Durchmesser kleiner als die Drossel 46 und bewirkt, daß sich Änderungen des als Systemdruck dienenden Motoröldrucks nur in abgeschwächter Form auf den Druck im Speicherraum auswirken.The described valve control device works as follows:
for the operation of the internal combustion engine, the
Claims (8)
- Valve control appliance for controlling the closing time and opening time of an engine valve (10), of an internal combustion engine, actuated by a valve control cam (14) of a camshaft (13) via an axially displaceable valve stem (12), having a fluid-filled lift transmission chamber (29) arranged between the valve control cam (14) and the valve stem (12), which lift transmission chamber (29) has a passage (30), controllable by a magnetic valve (31), for draining and supplying the fluid in order to change the effective axial extent of the lift transmission chamber (29) between the valve control cam (14) and the valve stem (12), which passage (30) opens into a fluid reservoir (43, 41) at the other end, characterised in that the fluid reservoir (43, 41) is integrated into the magnetic valve (31) and, by the withdrawal of the valve element, becomes configured as the reservoir piston (41) in the opening direction beyond a position freeing a through-flow opening, the magnetic control valve (31) is closed when no electricity is supplied and in that the valve element configured as the reservoir piston (41) is loaded by a reservoir spring (45) acting as closing spring.
- Valve control appliance according to Claim 1, characterised in that the reservoir piston (41) has a cup-shaped configuration and has a cup bottom facing towards the reservoir space (43), the edge (54) of which cup bottom interacts with a valve seat (55) present between valve inlet space (42) and reservoir space (43) and which reservoir piston (41) is radially guided on an inner wall of the control valve housing (40) and in that a central shank (47) connected to the housing is immersed as the magnet yoke into the cup opening of the reservoir piston (41).
- Valve control appliance according to Claim 2, characterised in that the magnet coil (52) is arranged in the annular space of the magnet space (44) formed between the shank (47) and the inner wall of the housing (40).
- Valve control appliance according to Claim 2, or 3, characterised in that a central hole (50) for relieving the magnet space (44) is present in the shank (47).
- Valve control appliance according to one of Claims 1 to 4, characterised in that a throttle opening (46) is present in the means (bottom of the reservoir piston 41) separating the magnet space (44) from the reservoir space (43).
- Valve control appliance according to one of Claims 2-5, characterised in that the reservoir space (43) is connected to the crankcase via a throttle hole (56) and a non-return valve (38) opening towards the reservoir space (43).
- Valve control appliance according to one of Claims 2 to 6, characterised in that the shank (47) acts as a lift stop for the reservoir piston (41) and in that the reservoir spring (45) is partially immersed in a pocket hole (49) of the shank (47).
- Valve control appliance according to one of the preceding claims, characterised in that the supply of electricity to the magnet coil (52) can be interrupted after the reservoir piston (41) lifts from the seat (54).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3929072A DE3929072A1 (en) | 1989-09-01 | 1989-09-01 | VALVE CONTROL DEVICE WITH SOLENOID VALVE FOR INTERNAL COMBUSTION ENGINES |
| DE3929072 | 1989-09-01 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0441909A1 EP0441909A1 (en) | 1991-08-21 |
| EP0441909B1 true EP0441909B1 (en) | 1993-09-29 |
Family
ID=6388437
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP90910571A Expired - Lifetime EP0441909B1 (en) | 1989-09-01 | 1990-07-28 | Valve control device with magnetic valve for internal combustion engines |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US5113812A (en) |
| EP (1) | EP0441909B1 (en) |
| JP (1) | JP3142555B2 (en) |
| DE (2) | DE3929072A1 (en) |
| WO (1) | WO1991003627A1 (en) |
Families Citing this family (24)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5275136A (en) * | 1991-06-24 | 1994-01-04 | Ford Motor Company | Variable engine valve control system with hydraulic damper |
| EP0614507B1 (en) * | 1991-11-29 | 1996-09-25 | Caterpillar Inc. | Engine valve seating velocity hydraulic snubber |
| AU1338892A (en) * | 1992-01-13 | 1993-08-03 | Caterpillar Inc. | Engine valve seating velocity hydraulic snubber |
| US5451029A (en) * | 1992-06-05 | 1995-09-19 | Volkswagen Ag | Variable valve control arrangement |
| US5540201A (en) | 1994-07-29 | 1996-07-30 | Caterpillar Inc. | Engine compression braking apparatus and method |
| US5647318A (en) | 1994-07-29 | 1997-07-15 | Caterpillar Inc. | Engine compression braking apparatus and method |
| US5526784A (en) | 1994-08-04 | 1996-06-18 | Caterpillar Inc. | Simultaneous exhaust valve opening braking system |
| US5619965A (en) * | 1995-03-24 | 1997-04-15 | Diesel Engine Retarders, Inc. | Camless engines with compression release braking |
| US5829397A (en) * | 1995-08-08 | 1998-11-03 | Diesel Engine Retarders, Inc. | System and method for controlling the amount of lost motion between an engine valve and a valve actuation means |
| US5746175A (en) * | 1995-08-08 | 1998-05-05 | Diesel Engine Retarders, Inc. | Four-cycle internal combustion engines with two-cycle compression release braking |
| WO1997006355A1 (en) * | 1995-08-08 | 1997-02-20 | Diesel Engine Retarders, Inc. | Internal combustion engines with combined cam and electro-hydraulic engine valve control |
| US5537976A (en) * | 1995-08-08 | 1996-07-23 | Diesel Engine Retarders, Inc. | Four-cycle internal combustion engines with two-cycle compression release braking |
| US6474277B1 (en) | 1999-09-16 | 2002-11-05 | Diesel Engine Retarders, Inc. | Method and apparatus for valve seating velocity control |
| ITTO20010660A1 (en) * | 2001-07-06 | 2003-01-06 | Fiat Ricerche | MULTI-CYLINDER DIESEL ENGINE WITH VARIABLE VALVE OPERATION. |
| US6694933B1 (en) * | 2002-09-19 | 2004-02-24 | Diesel Engine Retarders, Inc. | Lost motion system and method for fixed-time valve actuation |
| JP2007500314A (en) * | 2003-05-06 | 2007-01-11 | ジェイコブス ビークル システムズ、インコーポレイテッド | System and method for improving the performance of hydraulic actuation systems |
| DE102008049181A1 (en) * | 2008-09-26 | 2010-04-01 | Schaeffler Kg | Electrohydraulic valve control |
| EP2204566B1 (en) * | 2008-12-29 | 2011-06-29 | Fiat Group Automobiles S.p.A. | Adaptive control system of the air-fuel ratio of an internal combustione engine with a variable valve timing system |
| DE102009042544A1 (en) | 2009-09-22 | 2011-03-31 | Schaeffler Technologies Gmbh & Co. Kg | Electro-hydraulic valve drive for stroke-variable actuation of gas exchange valve of internal combustion engine, has supply channel positioned such that channel opening is opened in extended position of actuator piston |
| KR20120017982A (en) * | 2010-08-20 | 2012-02-29 | 현대자동차주식회사 | Electro-Hydraulic Variable Valve Lift Device |
| CN103061845B (en) * | 2013-01-18 | 2017-04-12 | 浙江吉利汽车研究院有限公司杭州分公司 | Valve mechanism |
| DE102013220555B4 (en) * | 2013-10-11 | 2015-05-13 | Schaeffler Technologies AG & Co. KG | Hydraulic valve control of an internal combustion engine |
| JP6254245B2 (en) * | 2016-12-05 | 2017-12-27 | 三菱重工業株式会社 | Exhaust valve driving device and internal combustion engine provided with the same |
| DE102017005069A1 (en) * | 2017-05-22 | 2018-11-22 | Bernd Niethammer | Device for adjusting the stroke of a valve of internal combustion engines |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0341440A1 (en) * | 1988-05-07 | 1989-11-15 | Robert Bosch Gmbh | Valve operating device with a magnetic valve for an internal-combustion engine |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4203397A (en) * | 1978-06-14 | 1980-05-20 | Eaton Corporation | Engine valve control mechanism |
| DE3135650A1 (en) * | 1981-09-09 | 1983-03-17 | Robert Bosch Gmbh, 7000 Stuttgart | "VALVE CONTROL FOR PISTON PISTON INTERNAL COMBUSTION ENGINES WITH MECHANICAL-HYDRAULIC MOTION TRANSMITTERS" |
| JPH0612058B2 (en) * | 1984-12-27 | 1994-02-16 | トヨタ自動車株式会社 | Variable valve timing lift device |
| DE3511819A1 (en) * | 1985-03-30 | 1986-10-09 | Robert Bosch Gmbh, 7000 Stuttgart | VALVE CONTROL DEVICE |
| DE3511820A1 (en) * | 1985-03-30 | 1986-10-02 | Robert Bosch Gmbh, 7000 Stuttgart | VALVE CONTROL DEVICE FOR A PISTON PISTON INTERNAL COMBUSTION ENGINE |
| DE3532549A1 (en) * | 1985-09-12 | 1987-03-19 | Bosch Gmbh Robert | VALVE CONTROL DEVICE |
| US4982706A (en) * | 1989-09-01 | 1991-01-08 | Robert Bosch Gmbh | Valve control apparatus having a magnet valve for internal combustion engines |
-
1989
- 1989-09-01 DE DE3929072A patent/DE3929072A1/en not_active Ceased
-
1990
- 1990-07-28 JP JP02510652A patent/JP3142555B2/en not_active Expired - Lifetime
- 1990-07-28 DE DE90910571T patent/DE59002946D1/en not_active Expired - Fee Related
- 1990-07-28 WO PCT/DE1990/000585 patent/WO1991003627A1/en active IP Right Grant
- 1990-07-28 EP EP90910571A patent/EP0441909B1/en not_active Expired - Lifetime
- 1990-07-28 US US07/663,928 patent/US5113812A/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0341440A1 (en) * | 1988-05-07 | 1989-11-15 | Robert Bosch Gmbh | Valve operating device with a magnetic valve for an internal-combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH04501594A (en) | 1992-03-19 |
| DE59002946D1 (en) | 1993-11-04 |
| DE3929072A1 (en) | 1991-03-07 |
| EP0441909A1 (en) | 1991-08-21 |
| JP3142555B2 (en) | 2001-03-07 |
| WO1991003627A1 (en) | 1991-03-21 |
| US5113812A (en) | 1992-05-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0441909B1 (en) | Valve control device with magnetic valve for internal combustion engines | |
| EP0341440B1 (en) | Valve operating device with a magnetic valve for an internal-combustion engine | |
| EP0196438B1 (en) | Valve control for a reciprocating internal-combustion engine | |
| EP0196441B1 (en) | Valve control system | |
| EP1029158A1 (en) | Device for controlling a gas shuttle valve for internal combustion engines | |
| DE3929134C2 (en) | ||
| DE19757475C2 (en) | Servo-controlled solenoid valve | |
| DE3728817A1 (en) | FUEL INJECTION PUMP FOR AN INTERNAL COMBUSTION ENGINE | |
| DE2836226A1 (en) | FUEL INJECTION DEVICE FOR COMBUSTION MACHINERY | |
| DE3532549A1 (en) | VALVE CONTROL DEVICE | |
| EP0455761B1 (en) | Hydraulic control device for valves of internal combustion engines | |
| WO2011009879A1 (en) | Method for controlling delivery quantity, and reciprocating compressor having delivery quantity control | |
| DE4337070A1 (en) | Solenoid operated valve for fuel injection system - determines duration of fuel injection phase in conjunction with reciprocating fuel feed pump having cylinder indexing sensor | |
| EP0149598B1 (en) | Injection nozzle for injection internal combustion engines | |
| EP0451227B1 (en) | Fuel injection pump | |
| EP0455763B1 (en) | Hydraulic control device for the valves of a multi-cylinder internal-combustion engine | |
| WO1991008382A1 (en) | Hydraulic control device for an internal-combustion engine valve | |
| EP0282508B1 (en) | Fuel injection device for a diesel internal combustion engine with preinjection | |
| DE2647744A1 (en) | ELECTROMAGNETIC INJECTION VALVE FOR COMBUSTION MACHINES WITH AN ELECTROMAGNETIC CONTROLLED DIRECTIONAL VALVE FOR LOADING AND RELEASING THE REAR NEEDLE | |
| DE3604233A1 (en) | Valve control device for a reciprocating piston internal combustion engine | |
| EP1247983B1 (en) | Piston pump for hydraulic systems | |
| WO2000039460A1 (en) | Fuel metering pump for a heater, especially an additional heater or a parking heater of a motor vehicle | |
| DE3016543A1 (en) | FUEL INJECTION SYSTEM | |
| DE3929073A1 (en) | Valve control having magnet valve for IC engines | |
| DE19755276A1 (en) | Electromagnetic actuator for controlling gas changeover valve in IC engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| 17P | Request for examination filed |
Effective date: 19901219 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB |
|
| RAP3 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: ROBERT BOSCH GMBH |
|
| 17Q | First examination report despatched |
Effective date: 19920817 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
| ET | Fr: translation filed | ||
| REF | Corresponds to: |
Ref document number: 59002946 Country of ref document: DE Date of ref document: 19931104 |
|
| GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 19931015 |
|
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed | ||
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20030825 Year of fee payment: 14 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20040716 Year of fee payment: 15 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20040819 Year of fee payment: 15 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050201 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050728 |
|
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20050728 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20060331 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20060331 |