DE102020119755B4 - Electromagnetic actuation system for a switching valve of a VCR piston or VCR connecting rod - Google Patents

Abstract

Switching valve for actuating a VCR connecting rod (100) or a VCR piston with a valve housing (201, 401), at least one armature (203.4, 403) that can be moved back and forth with a first coil (302), a second coil (303 ) and a magnetic core (301), wherein the switching valve (200, 400) causes an increase in length of the VCR connecting rod or an increase in the compression height of the VCR piston in a first switching state, wherein the switching valve (200, 400) in a second switching state A decrease in length of the VCR connecting rod causes a reduction in the compression height of the VCR piston, the valve housing (201, 401) and the armature (203.4, 403) being arranged on a connecting rod or on a piston of an internal combustion engine, and the valve housing (201 , 401) two arranged permanent magnets (207, 208) are arranged, which hold the armature (203.4, 403) bistable either in a first switching position or in a second switching position.

Description

The invention relates to an electromagnetic switching or directional control valve which is preferably used to control hydraulically supported connecting rods with variable lengths (VCR connecting rods) or pistons with variable compression heights (VCR pistons).

State of the art

VCR connecting rods with hydraulic support are state of the art. For example, in the DE 10 2005 055199 B4 describes a two-stage variable-length connecting rod. This connecting rod has an eccentric in the small connecting rod eye that can be pivoted through a specific angle: the pivoting angle is typically around 60°. The eccentric rotation is kinematically coupled to two support pistons via two crank mechanisms. The support pistons form pressure chambers with the support cylinders in the connecting rod body, which are called "support chambers" in connection with the invention. Both support chambers are each connected to an oil supply groove in the connecting rod bearing via a non-return valve, ie oil can flow into the pressure chambers at any time. In addition, each pressure chamber is connected to a switching valve in the connecting rod via its own line. Depending on the switching position of a directional or switching valve, oil can flow out of the pressure chambers via these fluid connections, which are also referred to as outflow lines.

The switching valve has two switching positions. In the first switching position, the outflow line of a first pressure chamber is open and the outflow line of the second pressure chamber is closed. In the second switching position, the outflow line of the first pressure chamber is closed and the outflow line of the second pressure chamber is open. Open means either that the outflow line is fluidically connected to the environment, i.e. the crankcase (1st alternative) or that the outflow line is fluidically connected to the oil supply groove in the connecting rod bearing (2nd alternative). This implements the function of a switchable freewheel. In the figures, the invention is explained using an exemplary embodiment according to the second alternative.

Due to the fact that the shift valve can only assume two shift positions, the VCR connecting rod (ie if a shift is not currently taking place) can also only assume two lengths. Against this background, in the DE 10 2005 055199 B4 spoken of a two-stage variable-length connecting rod. The switching or directional control valve is located on the connecting rod and must be switched while the engine is running.

Various solutions are known for actuating such a switching valve.

In the DE 10 2005 055 199 B4 and the WO 2014/019 684 A1 mechanical actuation of the switching valve is described. In addition to mechanical actuation, switching valves actuated by fluid pressure are also known. The great advantage of such a hydraulic actuation is that no additional mechanical parts have to be installed in the engine. In the DE 10 2009 048 172 A1 describes a piston with variable compression height (VCR piston) whose pressure chambers are connected or can be connected by means of a fluid pressure-actuated switching valve. The pilot valve is located in the wrist pin and includes a fluid pressure actuated spool. The position of the switching valve is influenced by varying the fluid pressure applied to this valve piston.

The necessary variation of the oil pressure on the valve piston is most simply implemented by varying the oil pressure prevailing in the main oil duct of the reciprocating piston engine. For example, using an oil pump with a variable delivery volume per pump revolution. i.e. the already existing oil supply of the reciprocating engine takes on another function.

Alternatively, in addition to the already existing lubricating oil system, a further fluid line system can be integrated in a crankshaft, which is in fluid connection with the switching valve located on the moving component (connecting rod or piston).

In the DE 10 2009 048 172 A1 such a crankshaft is described, which has an additional line system. This line system, known as the control pressure system, connects a switching valve arranged in the crankshaft with oil outlet openings on each crank pin. The connecting rod bearing shells each have grooves into which these oil outlet openings open. In this way, a fluid connection is created across the connecting rod bearing. The oil pressure in the control pressure system can be specifically varied by means of the switching valve located in the crankshaft. In the simplest case, the ambient pressure is applied or the supply oil pressure. A fluid-operated switching valve located on the connecting rod is connected to the grooves in the connecting rod bearings.

In this way, the switching valve (main valve) located on the connecting rod can be actuated by the switching valve (pilot valve) located in the crankshaft. Similar solutions are the WO 2015/055582 A2 the EP 0 297 903 A2 and the US 2019/0 234 300 A1 known.

• Alle bekannten mechanischen und hydraulischen Betätigungssysteme bewirken zwei Ventilschaltstellungen; Zwischenstellungen können nicht eingestellt werden. Zudem ist keine zylinderindividuelle Betätigung möglich. In Folge dessen können bei VCR-Pleueln und VCR-Kolben auch nur zwei stabile Schaltpositionen und damit Verdichtungsstufen eingestellt werden.

Disadvantages of the known solutions:

• All known mechanical and hydraulic actuation systems bring about two valve switching positions; Intermediate positions cannot be set. In addition, no cylinder-specific actuation is possible. As a result, with VCR connecting rods and VCR pistons, only two stable switching positions and thus compression levels can be set.

If the compression ratio of each cylinder could be adjusted individually and steplessly, further increases in efficiency could be achieved. Or to put it another way: The potential of variable compression to increase the efficiency of a reciprocating internal combustion engine cannot be fully exploited with just two switching positions.

The object of the invention is to provide a directional valve that allows a hydraulically supported VCR connecting rod or a hydraulically supported VCR piston to be controlled/actuated in such a way that these intermediate positions can be held between the two switching positions that were previously possible, in order to thus achieve a to realize continuously adjustable compression.

This object is achieved according to the invention by an electromagnetically actuated switching valve according to claim 1.

The switching valve has two switching states. If the first switching state is active, the fluid connections of a VCR connecting rod are switched by the switching valve according to the invention in such a way that the length of the connecting rod increases. If the second switching state is active, the fluid connections of a VCR connecting rod are switched by the switching valve according to the invention in such a way that the length of the connecting rod decreases.

Due to the means according to the invention, which cause the armature to remain bistable in either its first or second switching position, the armature does not change its switching position even if it is outside the area of influence of the electromagnet. The bistability means that the position of the armature relative to the switching valve or its valve housing does not change “on its own” but only as a result of a targeted control or switching process.

In some cases it is sufficient if the armature is held on the valve housing by hydraulic gluing.

This electromagnetically actuated switching valve allows the two switching positions of the switching valve to be controlled very quickly and with little wear, so that intermediate positions in the length of the switchable connecting rod or the height of the VCR piston can also be set.

As a result, the compression ratio of the internal combustion engine can be continuously regulated. In addition, the compression ratio can be set and controlled individually for each cylinder or for each piston of an internal combustion engine. As a result, for example, a thermally highly stressed cylinder that tends to ring can be operated with a lower compression ratio than other cylinders that do not tend to ring.

The switching valve actuated according to the invention has a simple structure, the electromagnetic actuation using an electromagnet, which comprises the first coil, the second coil and the magnetic core, are fixed in place on a structural part of the internal combustion engine (crankcase, oil pan, etc.). It is therefore easily possible to energize the electromagnet even when the internal combustion engine is running. Only the directional control valve and the armature are arranged on the connecting rod and consequently participate in the essentially circular movement of the large connecting rod eye during operation of the internal combustion engine.

With the help of the 3/2-way or switching valve or 4/2-way or switching valve (with two switching positions) according to the invention, it is possible to control the length of the VCR connecting rod or the compression height of the VCR piston in each with sufficient precision any (intermediate) position between the end positions "maximum long" and "maximum short". The switching times of the switching valve according to the invention are so short that a two-point control of the length of a VCR connecting rod or the height of a VCR piston is possible at the usual operating speeds of an internal combustion engine. Controlling the length of the VCR connecting rod or the height of the VCR piston requires a comparison between the actual value of the controlled variable (length of the VCR connecting rod or height of the VCR piston) and the setpoint of the controlled variable.

The actual value is preferably using the from the DE 10 2006 033 062 A1 known method determined. This method is preferably implemented in an electronic engine control unit (ECU=electronic control unit), so that the actual value of the controlled variable is available in the ECU as a calculated variable. The target value is preferably determined in the ECU using characteristic maps or algorithms depending on the current driving situation. If the actual value is above the target value, ie if the actual connecting rod length (actual value) is greater than the target connecting rod length (target value), then the switching valve must be actuated in such a way that a shortening of the VCR connecting rod is initiated.

If the actual value is below the target value, ie the actual length is less than the target length, then the switching valve must be actuated in such a way that an extension of the VCR connecting rod is initiated.

At the in DE 10 2006 033 062 A1 In the method described, the actual value of the connecting rod length on each cylinder is updated once per crankshaft revolution. The two-point controller therefore only needs to carry out a setpoint/actual value comparison for each cylinder once per crankshaft revolution. Accordingly, an adjustment intervention has to be carried out on the switching valve according to the invention only once per crankshaft revolution. In this case, an adjustment intervention is a change in the switching position of the switching valve located on the VCR connecting rod.

The electromagnetically actuated switching valve according to the invention is located on a moving engine part, for example a connecting rod or a piston. It can be switched from one switch position to the other switch position sufficiently “quickly”. "Fast" means that the actuation time is less than the duration of a crankshaft revolution. At a ^maximum speed of 6000 rpm, one revolution takes 0.01 seconds. The adjustment intervention takes place with the help of a stationary installed (ie, for example, on the crankcase or the oil pan) electromagnet.

The switching valve according to the invention can only be switched when the valve housing arranged on the connecting rod and the armature attached thereto are in the area of influence of the stationary installed electromagnet. This can always be the case, for example, when the piston is at bottom dead center (BDC).

This is the case at least once per crankshaft revolution; so that in the directional control valve according to the invention once per crankshaft revolution an adjustment can be made. In this case, an adjustment intervention is a change in the switching position of the switching valve located on the VCR connecting rod. The maximum switching frequency of the switching valve according to the invention therefore does not have to be higher than the rotational frequency of the engine. This requirement is met by the switching valve according to the invention.

With a two-point control, the VCR connecting rod is either in the "increase length" or "reduce length" switching state. VCR connecting rods and VCR pistons with hydraulic support have hydraulic resistances, preferably implemented by orifices, in order to limit the adjustment speeds in the respective directions. These limitations are required for safe operation.

With currently realized VCR connecting rods according to the DE 10 2005 055 199 B4 the aperture diameters are dimensioned in such a way that the adjustment from "maximum long" to "maximum short" takes at least 0.4 seconds.

An increase in the braking or throttling effect of the chokes or orifices present in the VCR connecting rod and, as a result, also a reduction in the adjustment speed of the VCR connecting rod or the VCR piston is always possible in terms of design. The throttle or orifice diameter can therefore not only influence the time for an adjustment from stop to stop, but also the adjustment path within one crankshaft revolution.

If twelve crankshaft revolutions are required to switch from high compression to low compression at a speed of 2000 ^rpm and at full suction load, then it can be assumed that on average 1/12 of the adjustment path is covered within one revolution.

If the switching valve is now switched to "reduce length" for the duration of one revolution and switched to "increase length" for the next revolution, then the actual value of the connecting rod length oscillates by about half the amount of this adjustment path per crankshaft revolution, i.e. by 1/24 of the total adjustment path around the setpoint. This small control deviation from the target value has no negative effects on the operation of the internal combustion engine.

The means which hold the armature bistable either in a first switching position or in a second switching position can comprise two permanent magnets arranged on the valve housing and/or one or more bistable spring elements and/or one or more spring elements.

In other cases, the bistability is achieved using elastic parts such as leaf or coil springs. Constructive solutions are known, e.g. for bistable relays or for electrical toggle switches in residential buildings. However, permanent magnets can also be used in order to achieve the desired bistability.

According to the invention, the switching state of the switching valve can be coupled directly to the switching position of the armature. A direct coupling can be realized in that the armature is kinematically positively coupled mechanically to moving parts of the main switching valve. The armature can also form part of the main switching valve. It can be designed as a valve slide, for example.

The switching state of the switching valve can also be coupled indirectly, in particular by a pilot valve, to the switching position of the armature.

Then the switching valve according to the invention for controlling said fluid connections of a VCR connecting rod comprises a main switching valve for opening, for closing or for connecting fluid lines; it is thus a subsystem of the switching valve according to the invention. The main switching valve can be designed as a hydraulic valve in a slide design, in a rotary slide design or in a seat design.

The main switching valve preferably has a 3/2-way valve function, as shown in DE 10 2005 055 199 B4 described. Alternatively, a 4/2-way valve function is also possible.

In order to achieve a continuous adjustment of the length of a VCR connecting rod or the height of a VCR piston, the main switching valve must be switched back and forth at a significantly higher frequency than is necessary for a 2-stage adjustment between two end positions.

The main switching valve is actuated by a pilot valve. In this configuration, the armature is part of the pilot valve and is actuated by the solenoid.

A switching valve and armature are arranged on each connecting rod of the internal combustion engine and carry out a common movement during operation of the internal combustion engine.

The electromagnet, which actuates the armature, is stationary, on the other hand, for example attached to the crankcase or the oil pan; i.e. H. he does not participate in the movement mentioned above. With every revolution of the crankshaft, the switching valve and the armature come into the sphere of influence of the electromagnet once and only for a very short time. The switching process must take place within this very short time. This requires a smooth-running and little sluggish anchor.

In an advantageous development of the invention, the switching valve according to the invention (ie the entire assembly) includes a valve housing. An armature is movably mounted in the valve housing or in the immediate vicinity of the valve housing.

Claims 5 to 7 claim advantageous configurations of the switching valve.

According to the invention, the armature is moved from one stable position to the other by an electromagnet with two coils. By energizing the first coil, the armature can be transferred to its first switching position. By energizing the second coil, the armature can be transferred to its second switching position.

Said coupling can, however, also take place hydraulically, as in the case of servo valves. Here, the moving component of the main switching valve (valve spool in the case of a main switching valve in spool design) is actuated by varying one or two fluid pressures. The valve slide forms two pressure chambers on its end faces. Depending on the pressures acting on the end faces of the valve spool, or the pressure differences, a resultant hydraulic force is generated, which moves the valve spool into one of its two switching positions and holds it there.

1. 1. Möglichkeit: Dem ersten Druckraum wird ein erster Steuerdruck p_st1 aufgeprägt. Dem zweiten Druckraum wird ein zweiter Steuerdruck p_st2 aufgeprägt. Ist p_st2 größer als p_st1, nimmt der Ventilschieber aufgrund der daraus resultierenden Druckkräfte seine erste Schaltposition ein. Ist p_st1 größer als p_st2, nimmt der Ventilschieber aufgrund der dann resultierenden Druckkräfte seine zweite Schaltposition ein.
2. 2. Möglichkeit: Dem ersten Druckraum wird ein Steuerdruck p_st aufgeprägt. Der zweite Druckraum ist dauernd mit der Umgebung verbunden, so dass in ihm der Umgebungsdruck herrscht. Zusätzlich wirkt an dieser zweiten Stirnfläche noch eine Federkraft. Ist p_st kleiner als ein erster Druckgrenzwert, befindet sich der Ventilschieber in seiner ersten Position. Übersteigt der Druck p_st einen zweiten Druckgrenzwert, wird die Federkraft überwunden und der Ventilschieber nimmt seine zweite Schaltposition ein.
3. 3. Möglichkeit: Dem ersten Druckraum wird ein Steuerdruck p_st aufgeprägt. Der zweite Druckraum ist dauernd mit dem Ölversorgungssystem (Motoröldruck) verbunden, so dass ihm der Motoröldruck aufgeprägt wird. Zusätzlich wirkt an der ersten Stirnfläche noch eine Federdruckkraft. Ist der Steuerdruck p_st geringer als ein ersten Druckgrenzwert, befindet sich der Ventilschieber in seiner ersten Position. Übersteigt der Steuerdruck p_st einen zweiten Druckgrenzwert, nimmt der Ventilschieber seine zweite Position ein.

There are three options for shifting the valve slide from one switch position to the other switch position.

1. 1st possibility: A first control pressure p _st1 is applied to the first pressure chamber. A second control pressure p _st2 is applied to the second pressure chamber. If p _st2 is greater than p _st1 , the valve spool assumes its first switching position due to the resulting compressive forces. If p _st1 is greater than p _st2 , the valve spool assumes its second switching position due to the resulting compressive forces.
2. 2nd possibility: A control pressure p _st is applied to the first pressure chamber. The second pressure chamber is permanently connected to the environment, so that the ambient pressure prevails in it. In addition, a spring force acts on this second end face. If p _st is less than a first pressure limit, the valve slide is in its first position. If the pressure p _st exceeds a second pressure limit value, the spring force is overcome and the valve slide assumes its second switching position.
3. 3rd possibility: A control pressure p _st is applied to the first pressure chamber. The second pressure chamber is permanently connected to the oil supply system (engine oil pressure), so that the engine oil pressure is applied to it. In addition, a spring pressure force acts on the first end face. If the control pressure p _st is lower than a first pressure limit value, the valve slide is in its first position. If the control pressure p _st exceeds a second pressure limit value, the valve spool assumes its second position.

The additional springs can be used to represent a fail-safe position, ie the valve slide assumes this position when the oil pressure in both pressure chambers has reached ambient pressure drops, for example when starting the engine, until the oil pump has built up sufficient oil pressure.

The already mentioned pilot valve is used to set or vary the mentioned control pressures p _st , p _st1 and/or p _st2 . This pilot valve is also a switching valve with two switching positions.

The pilot valve is coupled to the armature of the electromagnet. This coupling can be realized in that the armature is kinematically positively coupled mechanically to moving parts of the pilot control valve. The armature can also form part of the pilot valve. It can be designed as a valve slide, for example.

To implement option 1 (to move the valve slide of the main switching valve), the pilot valve must have a 4/2-way valve function or a 3/2-way valve function. With options 2 and 3, the pilot valve must have a 3/2-way valve function.

In an advantageous embodiment of the invention, the armature has an elongate central part, at the ends of which a first closing surface and a second closing surface are formed, which protrude beyond the central part.

The valve housing is arranged between the first closing surface and the second closing surface of the armature. The first outflow conduit of the valve body is located opposite the first closing surface of the armature and the second outflow conduit is located opposite the second closing surface.

This means that by a short movement of the armature in the direction of its longitudinal axis, either the first closing surface of the armature closes the first outflow line of the valve housing or, assuming an opposite movement of the armature, the second closing surface of the armature closes the second outflow line of the valve housing.

The stroke of the armature can be very small, for example it can be a millimeter or even less. Very fast switching movements are possible, among other things because of this short stroke movement of the armature and the support of the stroke movement by the permanent magnets embedded in the valve housing. They allow the length of the VCR connecting rod or the height of a VCR piston to be regulated with sufficient precision, even in intermediate positions between the design-specified end positions of a VCR connecting rod or a VCR piston.

In a further advantageous embodiment of the invention, the magnetic core of the electromagnet has a first axial flux conducting core, a second axial flux conducting core and a connecting core, the first coil being wound around the first axial flux conducting core and the second coil being wound around the second axial flux conducting core. The armature is arranged such that it can move back and forth between a part of the first axial flux conducting core that projects beyond the first coil and a part of the second axial flux conducting core that projects beyond the second coil.

This means that whenever the armature arranged on the connecting rod moves through the space formed between the two axial flux conducting cores, the armature can be moved into one of its two switching positions by either the first coil or the second coil.

In this way, either the first outflow line or the second outflow line is closed in the valve housing. When the first coil is energized, the armature moves towards the first coil and as a result the second outflow line in the valve body is closed. When the second coil is energized, the armature moves toward the second coil or axial flux conducting core, and the first outflow conduit in the valve body is closed.

It can further be provided that the magnet core has a rib-shaped radial flux conducting core, and this radial flux conducting core is arranged between the first axial flux conducting core and the second axial flux conducting core. This results in the moment when the armature is located between the first axial flux conducting core and the second axial flux conducting core, a closed magnetic circuit with only very small air gaps through the magnetic core and the armature. As a result, the voltage applied to one of the coils is converted very effectively into an electromagnetic force acting on the armature.

As a result, a small pulse from one of the coils is sufficient to move the armature from its current switching position to the other switching position. As already mentioned, this also changes the switching position of the switching valve according to the invention. As a result, the armature rests with the closing surface on the first or second permanent magnet. As a result, the outflow line is permanently closed next to the corresponding permanent magnet.

In other words: It is not necessary to permanently energize one of the two coils. In addition, it is not necessary for the armature to be permanently in the magnetic field of the first or second coil. Even if on both When there is no voltage applied to the coils, the armature maintains its switching position. Thus, the switching valve according to the invention is a bistable switching valve with very short switching times.

In order to be able to withstand positioning of the armature in the event of centrifugal forces occurring during operation and at the same time to enable the armature to move as easily as possible in the direction of its longitudinal axis, the armature is fastened to the valve housing on the first closing surface and the second closing surface via a flexible strip.

The band is flexible in the direction of the adjustment path of the armature (usually in the direction of the longitudinal axis of the armature. This band can be made in one piece with the armature and its mechanical properties are ultimately adjusted constructively via the cross-sectional dimensions and its length.

In a further advantageous embodiment, the valve housing has an inlet and a receiving bore in which a valve slide is movably received.

The inlet in the valve housing opens into the receiving bore, and in an advantageous embodiment the valve slide has a groove on its outside diameter, which is dimensioned such that there is a hydraulic connection between the inlet and the groove, completely independent of the position of the valve slide in the receiving bore.

This allows the inside of the valve body to be supplied with oil from the inlet regardless of the position of the valve spool.

In order to enable the simplest and most effective control of the two support cylinders in the VCR connecting rod or a VCR piston, a further advantageous embodiment of the invention provides that the valve slide delimits a first pressure chamber and a second pressure chamber. The first pressure chamber is hydraulically connected to the groove via a first throttle bore, the second pressure chamber is hydraulically connected to the groove via a second throttle bore, and the first outflow line opens into the first pressure chamber and the second outflow line opens out into the second pressure chamber.

This configuration makes it possible to change the pressures in the first pressure chamber and in the second pressure chamber in a targeted manner by closing or opening one of the outflow lines, so that a resultant hydraulic force is set that brings the valve slide into a first switching position or a second switching position.

In this switching position, one connection of the switching valve is then hydraulically connected to the inlet of the valve housing or the oil supply groove, so that one of the two support cylinders in the connecting rod or in the VCR piston is hydraulically connected to the inlet or the oil supply groove. This allows oil to flow out of the corresponding support cylinder. As a result, the eccentric of the VCR connecting rod rotates in a manner known per se.

Further advantages and advantageous configurations of the invention can be found in the following figures, their description and the patent claims.

character list

• 1 eine Frontansicht eines Systems bestehend aus einem VCR-Pleuel und einem elektromagnetischen Aktuator;
• 1a eine Ansicht von unten des VCR-Pleuels aus 1,
• 2 eine erste Schnittansicht des Systems aus 1 entlang der Linie B - B;
• 3 eine zweite Schnittansicht des Systems aus 1 entlang der Linie A-A, ohne den oberen Teil des VCR-Pleuels;
• 4 eine perspektivische Ansicht des elektromagnetischen Aktuators aus 1;
• 5 eine perspektivische Ansicht des Schaltventils des VCR-Pleuels;
• 6 eine erste Schnittansicht des Schaltventils entlang der Linie A-A;
• 7 zeigt zweite Schnittansicht des Schaltventils entlang der Linie B-B;
• 8 eine dritte Schnittansicht des Schaltventils entlang der Linie C-C;
• 9 eine vierte Schnittansicht des Schaltventils entlang der Linie D-D und
• 10 eine weitere vorteilhafte Ausgestaltung des pilotbetätigten Schaltventils.

Show it:

• 1 a front view of a system consisting of a VCR connecting rod and an electromagnetic actuator;
• 1a a bottom view of the VCR connecting rod 1 ,
• 2 a first sectional view of the system 1 along line B - B;
• 3 a second sectional view of the system 1 along line AA, excluding the upper part of the VCR connecting rod;
• 4 Figure 12 shows a perspective view of the electromagnetic actuator 1 ;
• 5 a perspective view of the switching valve of the VCR connecting rod;
• 6 a first sectional view of the switching valve along the line AA;
• 7 shows a second sectional view of the switching valve along the line BB;
• 8th a third sectional view of the switching valve along the line CC;
• 9 a fourth sectional view of the switching valve along the line DD and
• 10 another advantageous embodiment of the pilot-actuated switching valve.

The invention is based on two advantageous structural configurations based on the 1 until 10 illustrated and described. The actual switching or directional control valve is located on a moving engine part (e.g. connecting rod, piston). It is actuated contact-free by an electromagnet that is installed in a fixed location (e.g. on the crankcase or the oil pan). The invention is described as an example for a VCR connecting rod.

The switching valve has a movable pick-up element, which conducts the magnetic flux. This movable element causes a change in the switching position of the switching valve.

The VCR connecting rod 100 is provided with a shift valve 200 . This switching valve 200 is preferably, as in 1 shown, screwed to the lower part 102 of the connecting rod.

As an alternative to a screw-on solution, the switching valve can also be integrated directly into the lower part of the connecting rod.

An electromagnet 300 is located below the crankshaft (not shown). This electromagnet 300 is firmly connected to the stationary engine structure. For example, the electromagnet can be connected to the main bearing caps (not shown) or to the crankcase (not shown). It is also possible to attach the electromagnet 300 to the oil pan or another structural part.

This in 1 The VCR connecting rod 100 shown is in the lowest possible position (bottom dead center "UT"), ie the crank pin of the crankshaft (not shown) is exactly below the main bearing journal.

The construction of the VCR connecting rod 100 is not discussed in detail here. VCR connecting rods are state of the art. Details can be found in the Scriptures DE 102005055199 B4 , which is hereby incorporated by reference. Only the fluid interfaces between the VCR connecting rod 100 and the switching valve 200 are discussed in detail below.

1a FIG. 12 shows a bottom view of the VCR connecting rod 100. FIG. without switching valve 200 to enable a view of the fluid interfaces.

The connecting rod lower part 102 has a flange surface 102.3. This flange surface 102.3 is divided into two flange areas by a recess 102.8. This recess 102.8 only has advantages in terms of manufacturing technology and has no further significance for the description of this invention. Each flange area has a threaded hole 102.7 for the purpose of fastening the switching valve. One of the two flange areas is penetrated by two fluid lines. These penetrations represent the high-pressure connections of the VCR connecting rod 100. The first high-pressure connection 102.4 is the connection for the “MKS support cylinder” of the VCR connecting rod 100. The second high-pressure connection 102.5 is the connection for the “GKS support cylinder. The supporting pistons belonging to the supporting cylinders are moved by filling and emptying the supporting cylinders. The support pistons are coupled to an eccentric in the small connecting rod eye via two slider-crank gears and, by twisting the eccentric, cause the length of the connecting rod to be adjusted, as shown in Fig DE 10 200505 5199 B4 is described in detail. The abbreviations "MKS" and "GKS" stand for "mass force side" and "gas force side".

The recess 102.8 is penetrated by a third fluid line 102.6. This third fluid line 102.6 is a supply connection. The switching valve 200 according to the invention is connected to the oil circuit of the internal combustion engine via it. The oil flowing out of the support cylinders is controlled by the switching valve 200 according to the invention and is routed to the supply connection 102.6.

In this exemplary embodiment, the supply connection 102.6 is fluidically connected to a supply groove 103.1 in the lower bearing shell 103 of the VCR connecting rod 100, as in FIG 2 and 3 you can see.

For the structural design shown here, the fluid connection from the “supply” port 102.6 to the switching valve 200 is via an oil transfer sleeve 205.

In the 2 the connecting rod 100 and the switching valve 200 connected thereto are shown in a position (e.g. in BDC) in which they are in the area of influence of a stationary electromagnet 300 . This only happens once per crankshaft revolution. The switching valve 200 can only be actuated/switched with the aid of the electromagnet 300 in this position. The actuation is explained in more detail below.

Based on 7 and 8th structure and switching function of the switching valve 200 are explained. The switching valve 200 has a valve housing 201 and a valve spool 204 (see FIG 7 and 8th ). The valve slide 204 is guided in an axially displaceable manner in a receiving bore 201.1. The direction of movement of the valve spool 204 is preferably parallel to the axis of rotation of the crankshaft. The valve spool 204 has a peripheral groove 204.1 on its cylinder jacket surface.

The groove 204.1 is designed in such a way that it is in fluid communication with the bore 201.2 in every possible position of the valve spool 204, as in FIG 7 to see.

In this way, approximately the same pressure level prevails in the groove 204.1 at all times as in the supply groove 103.1. Since the supply groove 103.1 from the oil pump of the reciprocating piston machine is supplied with oil, the oil pressure in the supply groove 103.1 and in the groove 204.1 roughly corresponds to the delivery pressure of the oil pump.

The location hole 201.1 is penetrated by two other holes, as in 8th to see. The first of these holes is the control hole 201.3. The second of these holes is the control hole 201.4. in the in 8th In the illustrated position of the valve slide 204, the groove 204.1 is in fluid connection with the control bore 201.4, which is connected to the second port 201.6 (see 5 ) connected is. In this way, the "GKS support cylinder" connection 102.5 (see 2 ) of the VCR connecting rod 100 with the connection "supply" 102.6 of the VCR connecting rod 100 in fluid connection.

The control bore 201.3 is closed in this switch position (see 8th ). This also closes the "MKS support cylinder" connection 102.4 of the VCR connecting rod.

When the valve spool 204 assumes its other position (i.e. in 8th shifted to the right as much as possible), the groove 204.1 is in fluid connection with the control bore 201.3, which is connected to the first connection 201.5 (see 5 ) connected is. Then the “MKS support cylinder” connection 102.4 is in fluid connection with the “supply” connection 102.6 of the VCR connecting rod 100 and the “GKS support cylinder” connection 102.5 is closed.

The two control bores 201.3 and 201.4 are preferably positioned in such a way that the groove 204.1 of the valve slide 204 cannot establish a direct connection between these two control bores 201.3 and 201.4 at any time. That is, when the valve slide 204 is in a central position, both control bores 201.3 and 201.4 are closed.

Based on 7 the operation of the valve spool 204 will now be explained. The actuation takes place hydraulically, ie by changing the fluid pressures acting on the end faces of the valve slide 204 .

The valve housing 201 is surrounded by a closure box 202 in this exemplary embodiment. The function of this locking box 202 is to close the receiving bore 201.1 at the end. It would also be possible to replace the locking box 202 with locking screws (not shown). In this way, a first pressure chamber 1 and a second pressure chamber 2 are formed. The first pressure chamber 1 is in fluid communication with the circumferential groove 204.1 via a first throttle bore 204.2 in the valve slide 204. The second pressure chamber 2 is in fluid communication with the circumferential groove 204.1 via a second throttle bore 204.3.

Is the one in the second (right in 7 ) Pressure chamber 2 prevailing pressure is greater than the pressure in the first (on the left in 7 ) Pressure chamber 1, the force resulting on the valve slide 204 acts to the left, ie the valve slide 204 is pressed against the left stop surface 202.1.

If the pressure in the first (left) pressure chamber 1 is greater than the pressure in the second (right) pressure chamber 2, the resulting force acts to the right, i.e. the valve slide 204 is pressed against the right stop surface 202.2.

The fluid pressures in the pressure chambers 1, 2 are changed by the alternate closing of the outflow lines 201.7, 201.8 from these pressure chambers 2 and 2. A first outflow line 201.7 is connected to the first pressure chamber 1. A second outflow line 201.8 is connected to the second pressure chamber 2.

The valve housing 201 and the closure box 202 are surrounded by a tapping element 203 designed as a closed frame. This frame-like pick-off element 203 has, as in 7 visible, areas with greatly differing wall thicknesses.

The lower area of the tapping element 203 has the greatest wall thickness. This peripheral section of the pick-up element is referred to as the anchor area 203.4, or anchor for short. Closing surfaces are formed directly adjoining this anchor region 203.4. A first closing surface 203.1 is formed to the left of the armature 203.4. A second closing surface 203.2 is formed to the right of the armature 203.4.

Above the first closing surface 203.1, the cross section of the pick-off element 203 tapers to form a first band 203.5. Above the second closing surface 203.2, the cross section of the pick-off element 203 tapers to form a second band 203.6. In the upper area of the pick-off element 203, the cross section widens again to the clamping area 203.7.

This clamping area 203.7 engages in a form-fitting manner in corresponding recesses in the valve housing 201 and in the closure box 202. In this way, the pickup element 203 is positioned in the switching valve 200 in a form-fitting manner. The strips 203.5 and 203.6 are designed in such a way that their longitudinal rigidity enables them to dissipate all the forces acting on the anchor area 203.4 in the section plane AA without significant deformation. At the same time, the bands have a slight possible flexural rigidity in order to oppose the lowest possible restoring forces to forces acting normal to the section plane AA. This minimizes the influence of the ligaments 203.5 and 203.6 on the anchor.

This results in a bearing or suspension of the armature 203.4, which largely works as if friction-free joints were attached between the clamping area 203.7 and the armature 203.4.

The pick-off element 203 is made of a ferromagnetic material if it is made in one piece.

Permanent magnets 207, 208 are embedded in the valve housing 201, as in 9 to see. A first permanent magnet 207 exerts an attractive force on the first closing surface 203.1. A second permanent magnet 208 exerts an attractive force on the second closing surface 203.2.

In all figures (except the 10 ) the tapping element 203 is shown in the neutral position. This neutral position represents an unstable state of equilibrium. The magnetic forces exerted by the permanent magnets 207, 208 on the armature 203.4 cancel each other out.

The smallest forces acting on the armature 203.4 normal (perpendicular) to the plane AA cause a movement of the armature 203.4 in the direction of the first or the second axial flux conducting core 301.1, 301.2. As soon as one of the two closing surfaces 203.1 or 203.2 of the tapping element 203 is in contact with the valve housing 201 and one of the (optional) permanent magnets 207 or 208, which are preferably embedded flush in the valve housing 201, one of the two outflow lines 201.7 or 201.8 is closed. In short: When the anchor 203.4 is in the 2 or the 7 moved to the left, then the outflow line on the right side of the valve body 201 is closed; and vice versa.

Due to the continuously acting magnetic force of the permanent magnets 207, 208, the state of deformation of the pick-up element 203 or the position of the armature 203.4 is retained, even if no external forces are acting on the armature 203.4. The bands 203.5 and 203.6 are so soft in the longitudinal direction of the armature 203.4 that they do not impede these movements of the armature 203.4 and do not exert any significant restoring force on the armature 203.4 in the direction of the neutral central position. In this way, a bistable switching function is implemented.

The fluid pressures in the pressure chambers 1, 2 are changed in a targeted manner by the mutual closing of the outflow lines. When the first outflow line 201.7 is closed, oil no longer flows into the first pressure chamber 1 via the first throttle bore 204.2, and the pressure difference between the groove 204.1 and the first pressure chamber 1 is equal to zero. As a result, the pressure in the first pressure chamber 1 assumes the fluid pressure prevailing in the supply groove 103.1. Oil can flow out of the second pressure chamber 2 through the open outflow line 201.8 into the crank chamber, i.e. into the environment.

As a result of the flow through the second throttle bore 204.3, a pressure difference builds up across the second throttle bore 204.3, so that the pressure in the second pressure chamber 2 is lower than the pressure in the first pressure chamber 1.

As a result, a (in 7 ) resulting force directed to the right, which causes a movement of the valve slide 204 towards the right-hand stop 202.2.

When the second outflow line (201.8) is closed, the valve slide 204 is pressed against the left stop 202.1 accordingly. The hydraulic resistance of the throttle bores 204.1, 204.2 is preferably greater than the hydraulic resistance of the outflow lines 201.7, 201.8. In the ideal case, the hydraulic resistance of the outflow line is 201.7 or 201.8. compared to the hydraulic resistance of the corresponding throttle bore 204.1 or 204.2, because then there is almost ambient pressure in the open pressure chamber 1 or 2 and the resulting force is maximum.

A compromise solution must be found when dimensioning the throttle bores 204.1 or 204.2. The throttle bores 204.1 and 204.2 must not be too large in order to avoid an inadmissibly high permanent oil volume flow from the supply groove 103.1. On the other hand, the throttle bores 204.1 and 204.2 must be dimensioned large enough to cause rapid filling of the respective pressure chamber 1 and 2 and thus rapid movement of the valve slide 204.

The flow cross-section of the outflow lines 201.7 or 201.8, especially directly at the exit from the valve housing 201, must not be too large, otherwise the holding force that has to be applied by the permanent magnet 207 or 208 will be very large. In the event of an external switchover, this high holding force would have to be compensated by the electromagnet 300 (see 2 , 3 and 4 ) to be overcome.

In order to minimize the size and power requirements of the electromagnet 300, it is desirable to use as little holding force as possible. In a design example, a diameter of 0.5 mm for the throttle bores 204.1 or 204.2 and a diameter of 1.0 mm for the outflow lines 201.7 or 201.8 is proposed. Assuming a maximum relative oil pressure to be expected in the supply groove 103.1 of 10 bar, the required holding force is 0.78 N.

Based on 2 , 3 and 4 the electromagnetic actuation of the tapping element 203 and thus of the switching valve 200 is explained.

First shows 4 the structure of the stationary arranged in the reciprocating internal combustion engine electromagnet 300. This consists of a magnetic core 301, a first coil 302 and a second coil 303.

The magnetic core 301 has four areas. These are a first axial flux conducting core 301.1, a second axial flux conducting core 301.2, a radial flux conducting core 301.3 and a connecting core 301.4.

In 2 a dashed line 3 is drawn in to delimit said areas 301.1 to 301.4 of magnetic core 301. Magnetic core 301 can be manufactured in one piece. Alternatively, it can be composed of different parts, for example by means of screw; Bonded or welded joints are held together.

The magnet core 301 must be made of a material with good magnetic conductivity. The first coil 302 encloses the first axial flux conducting core 301.1. The second coil 303 encloses the second axial flux conducting core 301.2. The radial flow exit surface 301.3.1 (See 4 ) of the radial flux conducting core 301.3 is shaped in such a way that there is a constant minimum radial distance between this radial flux outlet surface 301.3.1 and the radial flux outlet surface 203.4.1 of the armature 203.4 when the armature 203.4 is guided past the magnet core 301.

Preferably the in 3 The section contour of the flow outlet surface 203.4.1 that can be seen is not flat, but rounded or chamfered. In this way, a small radial air gap 4 (between 203.4.1 and 301.3.1 can be realized.

The upper end faces 301.1.1 and 301.2.1 of the two axial flux guide cores 301.1 and 301.2 are preferably contoured in such a way that the axial flux outlet faces 203.4.2 and 203.4.3 of the armature 203.4 in the axial direction completely separate from the axial flux outlet faces 301.1.2 and 301.2.1 of the axial flow guide cores 301.1 and 301.2 are covered. To a good approximation, this is achieved in that the end faces 301.1.1 and 301.2.1 each have a constant radial distance from the radial flow outlet face 301.3.1.

In order to achieve the greatest possible magnetic actuating forces, the air gaps should be dimensioned as small as possible. The achievable manufacturing and assembly tolerances primarily determine the air gap heights.

The radial air gap 4 is independent of the switching position of the armature 203.4. If the tolerances are narrowed accordingly, a nominal gap height of 1 mm is recommended here. The heights of the axial air gaps 5 and 6 (see 2 ) are dependent on the switching position of the armature 203.4. Here, too, a nominal gap height of 1 mm is recommended when the armature 203.4 is tightened.

At the beginning of the armature attraction process, the axial gap height, referred to as the initial air gap height, is larger by the stroke of the armature 203.4. The stroke of the armature 203.4, i.e. the armature travel between the mechanical stops, should be selected to be as small as possible to ensure that the armature stroke can be safely completed in one run. On the other hand, the opening widths 7 and 8 in front of the outflow lines 201.7 and 201.8 must be so large that no outflow resistance worth mentioning can arise.

The opening widths are in 7 to see. The opening widths when the discharge lines are open correspond to the armature lift. A value of 0.3 mm is recommended for the armature stroke.

In 2 the main flow lines are drawn. If the first coil 302 is energized, the course of the main flux line 9 will be established. The flux lines must flow through the radial air gap 4 and the axial air gap 5. Magnetic flux always causes a force on the flux-conducting parts, which tends to reduce the height of the air gap.

The armature 203.4 can be moved in the axial direction and is thus attracted to the axial flux guide core through which the current flows. If the first coil 302 is energized and the second coil 303 is de-energized, then the armature 203.4 (in 2 and 7 ) pulled to the left. If the second coil 303 is energized and the first coil 302 is de-energized, then the armature 203.4 (in 2 and 7 ) dragged to the right.

In order to obtain the highest possible magnetic actuation force, ideally only the armature 203.4 is made of magnetically conductive material. The valve housing 201, the closure box 202, the valve slide 204 and, if possible, also the fastening screws 206 are made of magnetically non-conductive material, for example stainless steel 1.4301 or 1.4401.

In the embodiment shown, the pick-off element 203 forms a closed frame. This is disadvantageous for the formation of a magnetic actuating force, since a (magnetic) secondary flux will appear in the closed frame. However, the bands 203.5 and 203.6 have small cross-sectional areas, so that this (magnetic) secondary flux is small compared to the main flux. This secondary flow can be prevented by interrupting the clamping area 203.7.

In addition, a magnetically non-conductive element must then be introduced between the pick-up element 203 and the lower part 102 of the connecting rod in order to keep these two magnetically conductive parts at a distance.

The energization of the coils 302, 303 is preferably started during an actuation process before the armature 203.4 reaches the area of influence of the electromagnet. Thus, the flooding is built up in good time.

In order to save cable lengths and to reduce the number of contacts, the beginning of the winding of a coil 302, 303 is connected to an electrically conductive motor structure part. This means that each cylinder unit only needs two electrical connections to a control unit with corresponding output stages located outside the crankcase.

In the 10 a further exemplary embodiment of a switching valve 400 according to the invention is shown. The representation is analogous to 7 . Both exemplary embodiments have a fluid-pressure-actuated main switching valve of spool design, with the valve spool delimiting two pressure chambers in both exemplary embodiments. The exemplary embodiments differ in the type of pilot control (ie how the two control pressures p _st1 and p _st2 are set) and in the way the armature 203.4 is guided. In the first exemplary embodiment, the pilot valve has a 3/2-way valve function. In the second exemplary embodiment, the pilot valve has a 4/2-way valve function.

The switching valve 400 has a valve housing 401 and a valve spool 404 . Pressure chambers 410 and 411 are formed on the end faces of the valve slide 404 . Supply oil and its pressure can be applied to these pressure chambers alternately via supply port 401.2.

in the in 10 shown switching position, the pressure chamber 411 is fluidically connected to the supply connection 401.2 via the pocket 403.4 and the pressure chamber 410 is short-circuited to the environment; i.e. h the (excess) pressure provided by an oil pump prevails in the pressure chamber 411; while ambient pressure prevails in the pressure chamber 410 . Thus, a (in 10 to the left) hydraulic force on the valve spool 404 effective. The valve spool 404 is pushed to its left stop.

The pick-up element 403 (hereinafter also referred to as armature 403) of the second exemplary embodiment has a first outlet opening 403.2, which can release the first outflow line 401.7 of the valve housing 401 to the environment or connect it to the environment.

A second outlet opening 403.3 can release the second outflow line 401.8 of the valve housing 401 to the environment or connect it to the environment.

The armature 403 is made of a ferromagnetic material and functions as part of a magnetic circuit as in the first embodiment of the switching valve. Permanent magnets are preferably used to lock the armature 403 in the end position, analogous to that in 9 proposed for the first embodiment of the switching valve.

The valve housing 401 has a (flat) sealing surface 401.9, which is preferably produced by surface grinding. The armature 403 also has a flat sealing surface 403.1, which is also preferably produced by flat grinding.

A retaining clip 402 is screwed to the valve housing 401 or connected detachably in some other way, with the screw connection in 10 is not recognizable. The retaining bracket 402 has a sliding surface 402.1. The sliding surface 402.1, together with the sealing surface 401.9 of the valve housing 401, forms a linear guide which guides the armature 403 in the vertical direction and in the direction normal to the drawing view.

The cross section of the tunnel-like, prismatic linear guide is preferably rectangular.

The fit between pick-off element 403 and linear guide should have as little play as possible in the vertical direction in order to ensure adequate sealing with valve housing 401 guarantee. On the other hand, the fit must be sufficiently “smooth” so that the armature 403 can be moved from one switch position to the other switch position by means of small electromagnetic actuating forces.

The anchor 403 takes in the 10 not shown other switching position when the other of the two coils is energized; analogous to the first embodiment.

Then the anchor 403 moves in the 10 to the left, so that the pressure chamber 410 is fluidically connected to the supply connection 401.2 via the pocket 403.4 and the pressure chamber 411 is short-circuited to the environment; i.e. h the (excess) pressure provided by an oil pump prevails in the pressure chamber 410; while ambient pressure prevails in the pressure chamber 411 . The resultant force acting on valve spool 404 is in 10 directed to the right, so that the valve spool 404 is pressed to its right stop.

This embodiment is even more compact; among other things, because the pick-off element 403 is reduced to the armature and is ultimately a rod, at the ends of which two end stops 403.5 and 403.6 are formed, which limit the travel of the armature 403.

reference list

1

erster Druckraum 7

2

zweiter Druckraum 7

3

Trennebene Kernbereiche 2

4

radialer Luftspalt 3

5

erster axialer Luftspalt 2

6

zweiter axialer Luftspalt 2

7

erste Öffnungsweite 7

8

zweite Öffnungsweite 7

9

erster Flusslinienverlauf 2

10

zweiter Flusslinienverlauf 2

100

VCR-Pleuel-Baugruppe

101

Pleueloberteil 1

102

Pleuelunterteil 1

102.1

Versorgungsnut 3

102.2

Versrgungsbohrung 3

102.3

Flanschfläche la

102.4

Anschluss „MKS-Stützzylinder“ la

102.5

Anschluss „GKS-Stützzylinder“ la

102.6

Anschluss „Versorgung“ la

102.7

Befestigungsgewindebohrung la

102.8

Ausnehmung la

103

Lagerschale unten 3

103.1

Versorgungsnut 3

103.2

Öffnung 3

200

Schaltventil-Baugruppe

201

Ventilgehäuse 5

201.1

Aufnahmebohrung 7

201.2

Einlass/Bohrung 7

201.3

teuerbohrung („MKS-Stützzylinder“) 8

201.4

Steuerbohrung („GKS-Stützzylinder“) 8

201.5

erster Anschluss („MKS-Stützzylinder“) 5

201.6

zweiter Anschluss („GKS-Stützzylinder“) 5

201.7

erste Ausflussleitung 7

201.8

zweite Ausflussleitung 7

202

Verschlusskasten 5

202.1

erster Anschlag 7

202.2

zweiter Anschlag 7

203

Abgriffselement 5

203.1

erste Schließfläche 7

203.2

zweite Schließfläche 7

203.4

Ankerbereich 7

203.4.1

radiale Flussaustrittsfläche 3

203.4.2

erste axiale Flussaustrittsfläche 7

203.4.3

zweite axiale Flussaustrittsfläche 7

203.5

erstes Band 7

203.6

zweites Band 7

203.7

Einspannbereich 7

204

Ventilschieber 6

204.1

Nut 8

204.2

erste Drosselbohrung 7

204.3

zweite Drosselbohrung 7

205

Ölübergabehülse 2

206

Schraube 6

207

Erster Dauer- oder Permanentmagnet 9

208

Zweiter Dauer- oder Permanentmagnet 9

300

Elektromagnet-Baugruppe

301

Magnetkern 4

301.1

erster Axialflussleitkern 4

301.1.1

obere Stirnfläche 2

301.1.2

axiale Flussaustrittsfläche 4

301.2

zweiter Axialflussleitkern 4

301.2.1

obere Stirnfläche 2

301.2.2

axiale Flussaustrittsfläche 4

301.3

Radialflussleitkern 4

301.3.1

radiale Flussaustrittsfläche 3

301.4

Verbindungskern 4

302

Erste Spule 4

303

Zweite Spule 4

400

Schaltventil-Baugruppe, zweite Ausführungsform 10

401

Ventilgehäuse 10

401.1

Aufnahmebohrung 10

401.2

Versorgungsanschluss 10

401.7

erste Ausflussleitung 10

401.8

zweite Ausflussleitung 10

401.9

Dichtfläche 10

402

Haltebügel 10

402.1

Gleitfläche 10

403

Abgriffselement 10

403.1

Dichtfläche 10

403.2

erste (Austritts-)Öffnung 10

403.3

zweite (Austritts-)Öffnung 10

403.4

Tasche 10

403.5

Endanschlag 10

403.6

Endanschlag 10

404

Ventilschieber

404.1

Nut 10

410

erster Druckraum 10

411

zweiter Druckraum 10

(the number after the designation indicates in which figure the respective reference number can be found first)

1

first pressure room 7

2

second pressure chamber 7

3

Separation level core areas 2

4

radial air gap 3

5

first axial air gap 2

6

second axial air gap 2

7

first opening width 7

8th

second opening width 7

9

first flow line course 2

10

second flow line course 2

100

VCR connecting rod assembly

101

upper part of connecting rod 1

102

Connecting rod lower part 1

102.1

Supply groove 3

102.2

supply hole 3

102.3

flange surface la

102.4

"MKS support cylinder" connection la

102.5

Connection "GKS support cylinder" la

102.6

"Supply" connection la

102.7

Threaded mounting hole la

102.8

recess la

103

Bearing shell below 3

103.1

Supply groove 3

103.2

opening 3

200

Shift Valve Assembly

201

valve body 5

201.1

Mounting hole 7

201.2

Inlet/Hole 7

201.3

expensive bore (“MKS support cylinder”) 8

201.4

Control hole ("GKS support cylinder") 8

201.5

first connection ("MKS support cylinder") 5

201.6

second connection ("GKS support cylinder") 5

201.7

first outflow line 7

201.8

second outflow line 7

202

lock box 5

202.1

first stop 7

202.2

second stop 7

203

pick-up element 5

203.1

first closing surface 7

203.2

second closing surface 7

203.4

anchor area 7

203.4.1

radial flow exit surface 3

203.4.2

first axial flow exit surface 7

203.4.3

second axial flow exit surface 7

203.5

first volume 7

203.6

second volume 7

203.7

Clamping area 7

204

Valve spool 6

204.1

slot 8

204.2

first throttle hole 7

204.3

second throttle hole 7

205

Oil transfer sleeve 2

206

screw 6

207

First permanent or permanent magnet 9

208

Second permanent or permanent magnet 9

300

electromagnet assembly

301

Magnetic core 4

301.1

first axial flux guide core 4

301.1.1

upper face 2

301.1.2

axial flow exit surface 4

301.2

second axial flux guide core 4

301.2.1

upper face 2

301.2.2

axial flow exit surface 4

301.3

Radial flux conduction core 4

301.3.1

radial flow exit surface 3

301.4

connection core 4

302

First coil 4

303

Second coil 4

400

Shift valve assembly, second embodiment 10

401

valve body 10

401.1

Mounting hole 10

401.2

Supply connection 10

401.7

first outflow pipe 10

401.8

second outflow line 10

401.9

sealing surface 10

402

bracket 10

402.1

sliding surface 10

403

pick-up element 10

403.1

sealing surface 10

403.2

first (exit) opening 10

403.3

second (exit) opening 10

403.4

bag 10

403.5

end stop 10

403.6

end stop 10

404

valve spool

404.1

slot 10

410

first pressure chamber 10

411

second pressure chamber 10

Claims (18)

Switching valve for actuating a VCR connecting rod (100) or a VCR piston with a valve housing (201, 401), at least one armature (203.4, 403) that can be moved back and forth with a first coil (302), a second coil (303 ) and a magnetic core (301), wherein the switching valve (200, 400) causes an increase in length of the VCR connecting rod or an increase in the compression height of the VCR piston in a first switching state, wherein the switching valve (200, 400) in a second switching state A decrease in length of the VCR connecting rod causes a reduction in the compression height of the VCR piston, the valve housing (201, 401) and the armature (203.4, 403) being arranged on a connecting rod or on a piston of an internal combustion engine, and the valve housing (201 , 401) two arranged permanent magnets (207, 208) are arranged, which hold the armature (203.4, 403) bistable either in a first switching position or in a second switching position. switching valve after claim 1 , characterized in that the switching state of the switching valve (200, 400) is coupled directly to the switching position of the armature (203.4, 403). switching valve after claim 1 or 2 , characterized in that the switching state of the switching valve (200, 400) is coupled indirectly to the switching position of the armature (203.4, 403). switching valve after claim 3 , characterized in that the valve housing (201, 401) has at least a first outflow line (201.7, 401.7) and a second outflow line (201.8, 401.8), that the armature (203.4, 403) assumes the first switching position when the first coil (302) is energized , wherein the armature (203.4, 403) assumes the second switching position when the second coil (303) is energized, and wherein a first permanent magnet (207) and next to the second outflow line (201.8, 401.8) a second permanent magnet (208) are arranged, which hold the armature (203.4, 403) in the first or second switching position. switching valve after claim 4 , characterized in that the armature (203.4) has an elongated middle part, at the ends of which a first closing surface (203.1) and a second closing surface (203.2) are formed, which project beyond the middle part, that the valve housing (201) between the first closing surface (203.1) and the second closing surface (203.2) of the armature (203.4), that the first outflow line (201.7) is arranged opposite the first closing surface (203.1), and that the second outflow line (201.8) is opposite the second closing surface (203.2). is arranged. switching valve after claim 4 , characterized in that a pocket (403.4) is formed in the armature (403), that the pocket (403.4) in the first switching position of the armature (403) hydraulically connects the first outflow line (401.7) to an inlet (401.2), that the pocket (403.4) in the second switching position of the armature (403) hydraulically connects the second outflow line (401.8) to the inlet (401.2), that in the first switching position of the armature (403) the second outflow line (401.8) is connected to the environment , and that in the second switching position of the armature (403), the first outflow line (401.7) is connected to the environment. switching valve after claim 6 , characterized in that at the ends of the armature (403) end stops (403.5, 403.6) are formed, which protrude beyond the armature (403), and that the armature (403) has a sealing surface (403.1), a first opening (403.2) and a second opening (403.3). Switching valve according to one of the preceding claims, characterized in that the magnetic core (301) has a first axial flux conducting core (301.1), a second axial flux conducting core (301.2) and a connecting core (301.4), that the first coil (302) around the first axial flux conducting core (301.1 ) is wound, that the second coil (303) is wound around the second axial flux conducting core (301.2), and that the armature (203.4, 403) projects beyond the first coil (302) part of the first axial flux conducting core (301.1) and the second Coil (303) superior part of the second Axialfluxleitkern (301.2) is arranged back and forth. switching valve after claim 8 , characterized in that the magnetic core (301) has a rib-shaped radial flux conducting core (301.3), and that the radial flux conducting core (301.3) is arranged between the first axial flux conducting core (301.1) and the second axial flux conducting core (301.2). Switching valve according to one of Claims 8 or 9 provided he is up claim 5 is backward-related, characterized in that the armature (203.4) is pulled in the direction of the first axial flux conducting core (301.1) when the first coil (302) is energized, so that the second closing surface (203.2) closes the second outflow line (201.8). Switching valve according to one of Claims 8 or 9 provided he is up claim 5 is backward-related, characterized in that the armature (203.4) is pulled in the direction of the second axial flux conducting core (301.2) when the second coil (303) is energized, so that the first closing surface (203.1) closes the first outflow line (201.7). Switching valve according to one of Claims 8 until 11 , provided he clicks on one of the Claims 1 until 5 is retracted, characterized in that the armature (203.4) is movably held in its position between the first axial flux conducting core (301.1) and the second axial flux conducting core (301.2) by two straps (203.5, 203.6). Switching valve according to one of Claims 8 until 12 , provided on claim 6 related, characterized in that the armature (403) is movably held in its position between the first axial flux conducting core (301.1) and the second axial flux conducting core (301.2) by a linear guide. Switching valve according to one of the preceding claims, characterized in that the valve housing (201, 401) has an inlet (201.2, 401.2) and a receiving bore (201.1, 401.1) in which a valve slide (204, 404) is movably received. switching valve after Claim 14 , characterized in that the inlet (201.2, 401.2) opens into the receiving bore (201.1, 401.1), that the valve slide (204, 404) has a groove (204.1, 404.1) on its outer diameter, which is dimensioned such that - independently from the position of the valve slide (204, 404) in the receiving bore (201.1. 410.1) - there is a hydraulic connection between the inlet (201.2, 401.2) and the groove (204.1, 404.1). switching valve after Claim 14 or 15 , characterized in that the valve slide (204, 404) delimits a first pressure chamber (1, 410) and a second pressure chamber (2,411), that the first pressure chamber (1,410) has a first throttle bore (204.2) or pocket 403.4) with the groove (204.1, 404.1) is hydraulically connected, that the second pressure chamber (2, 411) is hydraulically connected to the groove (204.1, 404.1) via a second throttle bore (204.3) or pocket (403.4), that the first outflow line (201.7, 401.7 ) opens into the first pressure chamber (1, 410), and that the second outflow line (201.8, 401.8) opens into the second pressure chamber (2, 411). Switching valve according to one of Claims 14 until 16 , characterized in that a first connection and a second connection are present in the valve housing (201), that the first connection and the second connection open into the receiving bore (201.1, 401.1). switching valve after Claim 17 , characterized in that depending on the position of the valve slide (204, 404) in the receiving bore (201.1, 401.1) a hydraulic connection either between the inlet (201.2, 401.2) and the first port or between the inlet (201.2) and the second port.

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