DE102018206746A1 - DEVICE FOR MOVING AT LEAST ONE VALVE FOR A COMBUSTION CHAMBER OF A COMBUSTION ENGINE - Google Patents

Abstract

An apparatus 7 for moving at least one valve 27a for a combustion chamber 5 of an internal combustion engine 3, comprising apparatus 7: a first piston 23a inside a first chamber 25a configured to drive a first valve 27a for the combustion chamber 5, the first piston 23a is adapted to be driven by a hydraulic control system 21 to move within the first chamber 25a, for moving the first valve 27a; a second piston 23b within a second chamber 25b configured to drive none of the valves for any combustion chamber, the second piston 23b being adapted to be driven by the hydraulic control system 21 to move within the second chamber 25b ; an elastic means 29b adapted to resist the driving of the second piston 23b; and an adjusting device 30b configured to control the resistance of the elastic device 29b.

Description

TECHNICAL AREA

The present disclosure relates to an apparatus for moving at least one valve for a combustion chamber of an internal combustion engine. In particular, but not exclusively, it relates to an apparatus for moving at least one valve for a combustion chamber of an internal combustion engine in a vehicle.

Aspects of the present invention relate to a device, an internal combustion engine, a valvetrain, a vehicle, and a method.

STATE OF THE ART

At a given time during a combustion cycle of an internal combustion engine ("engine"), a valve (eg, a poppet valve) is lifted away from a valve seat and into a combustion chamber to open an intake or exhaust port in the combustion chamber and gas exchange into or out of the combustion chamber through the opening. At a later predetermined time during the combustion cycle, the valve returns to the valve seat to close the opening.

It is known to control the lifting of a valve by devices (eg, a camshaft and a valvetrain). The valvetrain may include a hydraulic control system driven by the camshaft. Displacement of fluid within the hydraulic control system during actuation by the camshaft causes a small piston to move within a cylinder. The piston pushes against a valve stem of a valve that contacts the piston to raise the valve.

A combustion chamber may include a plurality of openings, each opening being opened and closed by a valve.

Devices that allow for better control of valve lift characteristics allow better control of gas exchange parameters that affect engine performance. Examples of such parameters are fuel-air mixing, intake and manifold gas pressure. Such devices therefore provide efficient engine management for increased combustion efficiency and engine torque, as well as reduced NVH (noise, vibration and harshness) values.

It is an object of the present invention to overcome the disadvantages of the prior art.

BRIEF SUMMARY OF THE INVENTION

Aspects and embodiments of the present invention provide an apparatus, an internal combustion engine, a valvetrain and a vehicle according to the following claims. The present invention is defined by the claims in the claims.

• einen ersten Kolben innerhalb einer ersten Kammer, konfiguriert zum Ansteuern eines ersten Ventils für die Brennkammer, wobei der erste Kolben dazu ausgelegt ist, durch ein hydraulisches Steuerungssystem angesteuert zu werden, um sich innerhalb der ersten Kammer zu bewegen, zum Bewegen des ersten Ventils;
• einen zweiten Kolben im Inneren einer zweiten Kammer, der dazu konfiguriert ist, keines der Ventile für irgendeine Brennkammer anzusteuern, wobei der zweite Kolben dazu ausgelegt ist, durch das hydraulische Steuerungssystem angesteuert zu werden, um sich innerhalb der zweiten Kammer zu bewegen;
• eine elastische Einrichtung, die dazu ausgelegt ist, der Ansteuerung des zweiten Kolbens zu widerstehen; und
• eine Einstellungseinrichtung, die dazu ausgelegt ist, den Widerstand der elastischen Einrichtung zu steuern.

According to a first aspect of the present invention, there is provided an apparatus for moving at least one valve for a combustion chamber of an internal combustion engine, the apparatus comprising:

• a first piston within a first chamber configured to drive a first valve for the combustion chamber, the first piston adapted to be driven by a hydraulic control system to move within the first chamber to move the first valve;
• a second piston within a second chamber configured to drive none of the valves for any combustion chamber, the second piston adapted to be driven by the hydraulic control system to move within the second chamber;
• an elastic device adapted to resist the driving of the second piston; and
• an adjustment device configured to control the resistance of the elastic device.

The adjustment means and the elastic means offer the advantage of better control of the stroke characteristics (movement characteristics) of the first valve. When the second piston and the first piston are driven, pumped hydraulic fluid is shared between the two pistons, thereby reducing the total hydraulic displacement of the first piston and correspondingly reducing the lift of the first valve. The second piston is effectively a "lift control piston" as it acts as a hydraulic accumulator to control the lift characteristics of the first valve depending on whether it is being driven. The increase in the resistance of the elastic means causes the second piston to be less displaced (moved) when the second piston is equal to one Amount of energy from hydraulic displacement is supplied. A smaller displacement of the second piston corresponds to a proportionally greater displacement of the first piston. Therefore, increasing the resistance of the elastic means causes an increase in the maximum stroke distance of the first valve.

The elastic device also provides an efficient valvetrain by returning energy to the hydraulic control system as it returns to its original shape following its deformation. The resilient means significantly reduces the need to pump additional hydraulic fluid into the device to maintain pressure.

In some examples, the adjustment device is configured to adjust a bias that acts on the elastic device.

In the examples in which the resistance is the bias of the elastic means, a change in bias advantageously allows limiting the maximum lift of the first valve without significantly delaying or retarding the initial opening of the valve or closure of the valve To maintain the duration of the valve lift event.

In some examples, the elastic means comprises a mechanical spring.

This offers the advantage of an elastic device with a substantially linear force-deformation characteristic, which allows a better calculable resistance to the control and thus a more predictable valve lift.

In some examples, the adjustment device is configured to allow more than two adjustment stages of the resistance of the elastic device.

This offers the advantage of better control of the stroke characteristics of the first valve.

In some examples, the adjustment means comprises a rotating member coupled to the resilient means and having a screw thread for positional adjustment.

This offers the advantage of enabling a fine control of the stroke characteristics of the first valve.

In some examples, the device includes an electronic controller operable to adjust the adjustment device.

This offers the advantage of enabling active control of the lift characteristics of the first valve in order to achieve efficient engine management.

In some examples, the apparatus includes at least one further piston configured to drive none of the valves for any combustion chamber, each of the at least one piston being within a further chamber and configured to be actuated by the hydraulic control system, to move within his other chamber.

This offers the advantage of additional stroke control compared to what would be possible in a device having only a second piston.

In some examples, the apparatus includes the hydraulic control system, wherein the hydraulic control system is configured to control the sequential actuation of the second piston and the at least one further piston.

This offers the advantage of allowing independent control of different stages of the stroke of the first valve.

In some examples, the device comprises a further elastic means adapted to resist the actuation of the at least one further piston, and a further adjustment means arranged to adjust the resistance of the further elastic means.

This offers the advantage of allowing independent fine control of different stages of the stroke of the first valve.

In some examples, the apparatus includes a limiter configured to limit a maximum travel distance of the at least one other piston or the second piston to control the sequential drive of the second piston and the at least one other piston.

The use of a limiter offers the advantage of enabling sequential control without the complexity of directional valves.

In some examples, the device includes a first elastic device configured to resist the driving of the first piston. In some examples, a resistance of the first elastic means differs from a resistance of the elastic means adapted to resist the driving of the second piston. In some examples the first chamber has a first bore sized to accommodate the first piston, the first bore has a first surface, the second chamber comprises a second bore sized to accommodate the second piston, the second bore has a second surface , and the first surface and the second surface are different. In some examples, the further chamber comprises a further bore, the size of which allows the receiving of the further piston, the further bore has a further surface, wherein the second surface and the further surface are different. In some examples, the first piston and the first valve have a first combined mass, the second piston has a second mass, and the first combined mass and the second mass are different. In some examples, the further piston (23d) has a further mass, wherein the second mass and the further mass are different.

This offers the advantage of allowing better control of the stroke change of the first valve in the second mode.

• in einem ersten Modus, zum Steuern der Ansteuerung des ersten Kolbens, nicht aber des zweiten Kolbens; und
• in einem zweiten Modus, zum Steuern der parallelen Ansteuerung des ersten Kolbens und des zweiten Kolbens.

In some examples, the apparatus includes the hydraulic control system, wherein the hydraulic control system is configured to:

• in a first mode, controlling the driving of the first piston but not the second piston; and
• in a second mode, for controlling the parallel driving of the first piston and the second piston.

This offers the advantage of better control of the lift features (movement characteristics) of the first valve, allowing at least two different lift features. When the second piston is driven, hydraulic fluid is split between the two pistons, thereby reducing the overall hydraulic displacement of the first piston and decreasing the stroke of the first valve accordingly.

In some examples, the hydraulic control system is configured to: in the first mode, control the parallel driving of the first piston and the third piston but not the second piston or the other piston; and in the second mode, controlling the parallel driving of the first piston and the second piston and the third piston and the other piston.

The device can be used for various applications. Advantageously, the device can be used in a Discrete Variable Valve Lift (DWL) application where the first and second modes are DVVL modes. The DVVL modes allow the valve or valves to increase more or less depending on the engine management requirements, resulting in a more efficient and powerful engine.

In another application, the device may be employed with at least one additional valve to be able to operate between Dual Valve Actuation (DVA) (first mode) and Single Valve Actuation (PDM), depending on the engine management requirements , SVA) switch. The SVA mode will be described later.

In some examples, the hydraulic control system is configured to control the parallel actuation of the first piston and the second piston in the second mode by controlling the simultaneous actuation of the first piston and the second piston using a hydraulic pumping device.

This simultaneous parallel drive offers the advantage that the second piston can be used from the time to provide the lift control when the drive starts.

In some examples, the apparatus includes means for blocking hydraulic communication between the second piston and a hydraulic pumping device in the first mode, but not in the second mode.

This offers the advantage of fast hydraulic switching between the first mode and the second mode.

In some examples, in the first mode, the first piston is movable a first maximum distance and movable in the second mode a second maximum distance, the adjustment of the adjustment device controlling the second maximum distance without changing the first maximum distance.

This offers the advantage of better control of the stroke characteristics (movement characteristics) of the first valve, the stroke distance being controllable in the second mode.

In some examples, the apparatus includes a third piston within a third chamber configured to drive a second valve, the third piston adapted to be actuated by the hydraulic control system to move within the third chamber to move the second valve.

This provides the advantage of an efficient device because multiple valves (eg, multiple valves from a combustor) share a hydraulic control system.

• in dem ersten Modus, zum Steuern der parallelen Ansteuerung des ersten Kolbens und des dritten Kolbens, nicht aber des zweiten Kolbens; und
• in dem zweiten Modus, zum Steuern der parallelen Ansteuerung des ersten Kolbens und des zweiten Kolbens und des dritten Kolbens.

The multi-valve device may be configured to provide DVVL modes. In some examples, the hydraulic control system is designed to:

• in the first mode, for controlling the parallel driving of the first piston and the third piston, but not the second piston; and
• in the second mode, for controlling the parallel driving of the first piston and the second piston and the third piston.

In some examples, the hydraulic control system is configured to: in the first mode, control the parallel driving of the first piston and the third piston but not the second piston or the other piston; and in the second mode, controlling the parallel driving of the first piston and the second piston and the third piston and the other piston.

The first and second modes are DVVL modes, because in each mode, both valves are raised, more or less depending on the mode.

In some examples, in the first mode, the first piston is movable a first maximum distance and movable in the second mode a second maximum distance, the third piston is movable in the first mode by a third maximum distance and in the second mode a fourth maximum distance is movable, wherein the first maximum distance is greater than the second maximum distance and wherein the third maximum distance is greater than the fourth maximum distance.

This advantageously allows a high lift mode in the first mode and a low lift mode in the second mode. The low-lift mode is advantageous for smooth and efficient engine operation at light load and in low engine speed environments, such as in urban environments. The high lift mode is advantageous for increased gas exchange, which improves engine torque.

In some examples, the adjustment of the adjustment means controls the second maximum distance and the fourth maximum distance without changing the first maximum distance or the third maximum distance.

This offers the advantage that the valve lift features in the low lift mode can be controlled using the adjustment means to increase engine torque and / or engine efficiency.

• in dem ersten Modus, zum Steuern der parallelen Ansteuerung des ersten Kolbens und des dritten Kolbens, nicht aber des zweiten Kolbens; und
• in dem zweiten Modus, zum Steuern der parallelen Ansteuerung des ersten Kolbens und des zweiten Kolbens, nicht aber des dritten Kolbens.

In some examples, the hydraulic control system is designed to:

• in the first mode, for controlling the parallel driving of the first piston and the third piston, but not the second piston; and
• in the second mode, for controlling the parallel driving of the first piston and the second piston, but not the third piston.

Actuation of the same number of pistons in both modes offers the advantage of compensating for the tendency of the hydraulic control system to raise the first valve further in SVA mode than in DVA mode. This compensation provides better control of gas exchange with respect to the combustion chamber and reduces valve interference with a lift portion of the combustion chamber.

In some examples, the hydraulic control system is configured to: in the first mode, control the parallel driving of the first piston and the third piston but not at least one of the second piston and the another piston; and in the second mode, for controlling the parallel driving of the first piston and the second piston or the other piston, but not the third piston.

In some examples, in the first mode, the first piston is moveable a first maximum distance and movable in the second mode a second maximum distance, the third piston being movable a third maximum distance in the first mode, and wherein the first maximum Distance, the second maximum distance and the third maximum distance are the same.

This offers the advantage of eliminating the tendency of the hydraulic control system to raise the first valve in SVA mode further than in DVA mode.

In some examples, the apparatus includes a closed loop system for adjusting the adjustment means to reduce the differences between the first maximum distance and the second maximum distance.

This offers the advantage of actively eliminating the tendency of the hydraulic Control system to raise the first valve in SVA mode further than in DVA mode.

In some examples, the apparatus includes means for blocking hydraulic communication between the third piston and a hydraulic pumping device of the hydraulic control system in the second mode, but not in the first mode.

This offers the advantage of fast hydraulic switching between the first mode and the second mode.

In some examples, the apparatus includes a movable member that, in the first mode, is movable to a first position in which the movable member blocks actuation of the second piston and enables actuation of the third piston and in a second mode into a second position Position is movable, in which the movable member blocks the control of the third piston and allows the control of the second piston.

This movable element for controlling the driving of both pistons has the advantage of reducing the timing and / or control limitations associated with the switching modes.

In some examples, the movable member in the first position blocks the hydraulic communication between the second piston and a hydraulic pumping device of the hydraulic control system and enables hydraulic communication between the third piston and the hydraulic pumping device, wherein the movable member in the second position controls the hydraulic communication between the third piston and the hydraulic pump means and enables the hydraulic communication between the second piston and the hydraulic pump means. In some examples, the movable member consists of a single slider that is configured to move along a single axis between the first position and the second position.

Blocking and enabling hydraulic communication offers the advantage of fast switching between the first and second modes.

According to another aspect of the present invention, there is provided an internal combustion engine comprising the apparatus.

In some examples, the internal combustion engine has a predetermined number of manifold extensions that open into combustion chambers, each manifold extension having an associated longitudinal center axis, wherein an axis of reciprocation of the second piston does not intersect a longitudinal center axis of one of the manifold extensions.

This offers the advantage of increased design freedom in the arrangement of the second piston, since the second piston is only the stroke control.

According to another aspect of the present invention, a valve train is provided that includes the device.

In some examples, a plurality of the devices is provided, the valvetrain comprises a controller configured to control in parallel the hydraulic control systems of the plurality of devices to switch between the first mode and the second mode.

According to another aspect of the present invention, a vehicle is provided that includes the internal combustion engine.

According to another aspect of the present invention, there is provided a system comprising the apparatus and hydraulic fluid in the hydraulic control system.

• einen ungekoppelten Kolben im Inneren einer Kammer, der dazu konfiguriert ist, keines der Ventile für irgendeine Brennkammer anzusteuern, wobei der ungekoppelte Kolben dazu ausgelegt ist, durch ein Fluidsteuerungssystem angesteuert zu werden, um sich innerhalb der Kammer zu bewegen. Das Fluidsteuerungssystem kann ein hydraulisches Steuerungssystem oder ein pneumatisches Steuerungssystem sein.

According to another aspect of the present invention, there is provided an apparatus for a valvetrain, the apparatus comprising:

• an uncoupled piston within a chamber configured to drive any of the valves for any combustion chamber, the uncoupled piston configured to be driven by a fluid control system to move within the chamber. The fluid control system may be a hydraulic control system or a pneumatic control system.

• einen Kolben innerhalb einer Kammer, wobei der Kolben dazu ausgelegt ist, sich innerhalb der Kammer zu bewegen;
• ein hydraulisches Steuerungssystem, das dazu ausgelegt ist, die Ansteuerung des Kolbens zu steuern;
• eine elastische Einrichtung, die dazu ausgelegt ist, der Ansteuerung des Kolbens zu widerstehen; und
• eine Einstellungseinrichtung, die dazu ausgelegt ist, den Widerstand der elastischen Einrichtung zu steuern.

According to another aspect of the present invention, there is provided an engine control apparatus, the apparatus comprising:

• a piston within a chamber, the piston being adapted to move within the chamber;
• a hydraulic control system configured to control the actuation of the piston;
• an elastic device adapted to resist the actuation of the piston; and
• an adjustment device configured to control the resistance of the elastic device.

• in einem ersten Modus, das Bewirken der hydraulischen Ansteuerung eines ersten Kolbens, nicht aber eines zweiten Kolbens;
• das Umschalten aus dem ersten Modus in einen zweiten Modus, und in dem zweiten Modus, das Bewirken der gleichzeitigen hydraulischen Ansteuerung des ersten Kolbens und des zweiten Kolbens,
• wobei sich der erste Kolben innerhalb einer ersten Kammer befindet, dazu konfiguriert ist, ein erstes Ventil für die Brennkammer anzusteuern, und dazu ausgelegt ist, sich bei hydraulischer Ansteuerung innerhalb der ersten Kammer (25a) zu bewegen, zum Bewegen des ersten Ventils;
• wobei sich der zweite Kolben innerhalb einer zweiten Kammer befindet, dazu konfiguriert ist, keines der Ventile für irgendeine Brennkammer anzusteuern, und dazu ausgelegt ist, sich bei hydraulischer Ansteuerung innerhalb der zweiten Kammer zu bewegen, wobei der Ansteuerung des zweiten Kolbens durch eine elastische Einrichtung widerstanden wird, wobei der Widerstand der elastischen Einrichtung durch eine Einstellungseinrichtung gesteuert wird.

According to another aspect of the present invention, there is provided a method of moving at least one valve for a combustion chamber of an internal combustion engine, the method comprising the steps of:

• in a first mode, effecting the hydraulic actuation of a first piston but not a second piston;
• switching from the first mode to a second mode, and in the second mode, causing the simultaneous hydraulic driving of the first piston and the second piston,
• the first piston being within a first chamber configured to actuate a first valve for the combustion chamber and configured to move in hydraulic actuation within the first chamber (25a) for moving the first valve;
• wherein the second piston is within a second chamber configured to drive none of the valves for any combustion chamber and configured to move within the second chamber when hydraulically actuated, the driving of the second piston being resisted by resilient means is, wherein the resistance of the elastic device is controlled by an adjusting device.

It is expressly intended, within the scope of this application, that the various aspects, embodiments, examples, and alternatives illustrated in the preceding paragraphs, in the claims, and / or in the following description and drawings, and in particular, their individual features, are independently of each other or in any combination. This means that all embodiments and / or features of any embodiment can be combined in any manner and / or combination, as long as these features are not incompatible. The Applicant reserves the right to change any claim originally filed or to file any new claim, including the right to alter any originally filed claim, to depend on and / or integrate any feature of any other claim although it has not been claimed in this way before.

list of figures

• 1 ein Beispiel ein Fahrzeug zeigt, das einen Motor aufweist;
• 2 ein Beispiel einer Vorrichtung zeigt;
• 3 ein anderes Beispiel einer Vorrichtung zeigt;
• 4 ein anderes Beispiel einer Vorrichtung zeigt;
• 5 beispielhafte Ventilhubkurven für eine Vorrichtung zeigt; und
• 6 ein Beispiel einer Einstellungseinrichtung einer Vorrichtung zeigt.

One or more embodiments of the invention will now be described, by way of example only, with reference to the accompanying drawings, in which:

• 1 an example shows a vehicle having a motor;
• 2 shows an example of a device;
• 3 shows another example of a device;
• 4 shows another example of a device;
• 5 shows exemplary valve lift curves for a device; and
• 6 an example of an adjustment device of a device shows.

DETAILED DESCRIPTION

The pictures show a device 7 for moving at least one valve 27a for a combustion chamber 5 an internal combustion engine 3 , the apparatus 7 comprising: a first piston 23a inside a first chamber 25a configured to drive a first valve 27a for the combustion chamber 5 , where the first piston 23a designed by a hydraulic control system 21 to be directed to get within the first chamber 25a to move, to move the first valve 27a ; a second piston 23b within a second chamber 25b configured to drive none of the valves for any combustion chamber, the second piston 23b is designed by the hydraulic control system 21 to be directed to get inside the second chamber 25b to move; an elastic device 29b , which is designed to control the second piston 23b to resist; and an adjustment device 30b , which is designed to resist the elastic device 29b to control.

1 shows an example of a vehicle 1 in which embodiments of the present invention can be implemented. In some, but not necessarily all, examples is the vehicle 1 a passenger vehicle, also referred to as a car or automobile. Passenger vehicles generally have a curb weight of less than 5000 kg. In other examples, embodiments of the present invention may be implemented for other applications, such as: B. industrial vehicles, aircraft or watercraft or non-vehicle applications.

In 1 includes the vehicle 1 an engine 3 , The motor 3 includes a combustion chamber 5 , In some examples, the engine includes 3 a plurality of combustion chambers 5 , The motor 3 includes a valvetrain 9 for controlling the operation of valves of the engine 3 , The valve train 9 includes a device 7 in which embodiments of the present invention can be implemented.

2 shows a first valve 27a (eg, a poppet valve) configured to have an opening 6 (a section) in a wall of the combustion chamber 5 of the motor 3 out 1 block when the first valve 27a closed, and the opening 6 to open when the first valve 27a is raised (located in an open position) and therefore has a distance to its valve seat.

The opening 6 is an interface between the combustion chamber 5 and a manifold extension 28 , The elbow extension 28 serves the provision or collection of gases related to a combustion process and has in 2 the shape of a pipe. If the first valve 27a through the device 7 is moved (lifted) to an open position, controls the separation distance of the opened first valve 27a from the opening 6 the gas flow into the combustion chamber 5 into it, when the first valve 27a is an inlet valve, or from the combustion chamber 5 out when the first valve 27a an exhaust valve is.

2 also shows an example of a device 7 according to embodiments of the present invention for controlling the movement of the first valve 27a , In some examples, the device is used 7 controlling the movement of more than one valve. In other examples, the number of valves passing through the device includes 7 be controlled, only a single valve.

The device 7 out 2 includes: a hydraulic control system 21 ; a valve actuator in the form of a first piston 23a within a first chamber 25a ; a second piston 23b within a second chamber 25b ; an elastic device 29b ; and an adjustment device 30b ,

The first piston 23a is inside the first chamber 25a movable, for example, by reciprocation, which is caused by displacement of hydraulic fluid. The first piston 23a is configured to the first valve 27a for the combustion chamber 5 To control, via a non-hydraulic coupling between the first piston 23a and the first valve 27a , such as Example, a direct mechanical coupling (surface-to-surface contact) or an indirect mechanical coupling (using one or more engaging mechanical components) or any other form of coupling, which is independent of hydraulic fluid, which is the first piston 23a and the second piston 23b controls. The first piston 23a can therefore be considered a "coupled" piston 23a be considered. The first chamber 25a may be a valve opening for receiving a stem of the first valve 27a include. The movement of the first piston 23a gets directly into the movement of the first valve 27a transfer.

In some, but not necessarily all, examples, all coupled pistons are each at a respective manifold extension of the engine 3 aligned when the device 7 in the engine 3 is installed. Alignment on a manifold extension means that an axis in which a piston reciprocates substantially intersects a longitudinal centerline of the manifold extension for proper valve alignment and minimum side loading.

The second piston 23b is inside the second chamber 25b and is movable within the second chamber 25b For example, by reciprocation caused by displacement of hydraulic fluid. The second piston 23a is configured not to drive any of the valves for any combustion chamber, for example the first valve 27a , The second chamber 25b does not include a valve port for receiving a stem of a valve. The second piston 23b can therefore be considered as a "dummy" piston or "uncoupled" piston. The second piston 23b in the second chamber 25b defines a hydraulic accumulator that expands in volume as it moves by moving the second piston 23b filled with hydraulic fluid.

Uncoupled pistons can be arranged so that they do not stick to a manifold extension of the engine 3 are aligned when the device 7 in the engine 3 is installed, since uncoupled pistons serve only the stroke control of other coupled pistons.

The elastic device 29b (eg, an elastic element) in the device 7 out 2 is designed to control the second piston 23b to resist. The elastic device 29b is designed to control the second piston 23b withstand by deformation in response to the movement of the second piston 23b , The elastic device 29b is designed to provide power to the hydraulic control system 21 when returning to its original shape following its deformation.

In some, but not necessarily all, examples, the elastic device comprises 29b (elastic element) a mechanical spring. In some, but not necessarily all, examples, the elastic device comprises 29b a compression spring. In some, but not necessarily all, examples, the elastic device comprises 29b a coil spring. In other examples, the elastic device 29b another material or system designed to have a substantially linear restoring force characteristic against deformation.

The adjustment device 30b (Adjustment element) in the device 7 out 2 is designed to resist the elastic device 29b to control. In some examples, the adjustment device is 30b is adapted to a plurality of adjustment stages of the resistance of the elastic device 29b to enable. For example, the adjustment device 30b be designed to allow more than two levels of adjustment.

In some, but not necessarily all, examples, the resistor refers to a bias, and is the adjuster 30b operable to adjust the preload on the elastic device 29b acts. The bias voltage is a background level of the internal stress in the elastic device 29b which is present even while the second piston 23b not controlled. If, for example, the elastic device 29b a spring, a bias voltage comprises a first extension or compression of the spring from its rest length (free length), even during the second piston 23b not controlled. In use, if by driving the second piston 23b Driving force on the prestressed elastic device 29b acts, this driving force must exceed the bias before the second piston 23b starts to move. Until the preload is exceeded, there is no movement of the second piston 23b , Therefore, until the bias voltage is exceeded, the entire hydraulic displacement in the first piston occurs 23a , As soon as the preload is exceeded, the hydraulic displacement is divided between the pistons 23a . 23b on, eliminating any further displacement of the first piston 23a is reduced.

5 shows exemplary valve lift curves for a valve (such as the first valve 27a ) of the device 7 , The x-axis corresponds to the normalized time t such as. B. the crank displacement. The y-axis corresponds to the distance d of the first valve 27a from his seat. The line 501 is a first valve lift curve leading to the second piston 23b belongs, which is immovable due to a bias (there is no hydraulic accumulation). The line 501 therefore has a normal bell shape, as is familiar to one of ordinary skill in the art. The line 503 is a second valve lift curve leading to the second piston 23b belongs, which is movable due to a predefined finite bias. The second valve lift curve has a truncated bell shape. This will be described below.

The second valve lift curve 503 corresponds to a first shoulder point 505 on the second valve lift curve 503 the first valve lift curve 501 , The on the second piston 23b acting driving force does not exceed the bias, therefore, the second piston moves 23b before the first shoulder point 505 Not. The first shoulder point 505 corresponds to the beginning of the movement of the second piston 23b if that on the second piston 23b acting driving force exceeds the bias voltage. Part of the displaced hydraulic fluid is now in the second chamber 25b accumulated. As a result, the first valve slows down 27a after the first shoulder point 505 , The first valve 27a then reaches its hub point 507 , which is lower than its maximum possible Hubspitze 509 as in the first valve lift curve 501 is shown. The first valve 27a then moves back to its seat at an initially low speed, then - as soon as the preload is not exceeded - the valve returns 27a at the second shoulder point 511 back to his seat at a high speed. After the second shoulder point 511 corresponds to the second valve lift curve 503 the first valve lift curve 501 ,

In other examples, the resistance may be a spring rate rather than a bias voltage.

6 shows an exemplary implementation of the adjustment means 30b on the elastic device 29b acts. The adjustment device 30b includes a cup-like sliding element 601 in which one end of the elastic device 29b sitting. The adjustment device 30b includes a cam 603 to the cam guide of the cup-like sliding element 601 to the bias of the elastic device 29b adjust. The cam 603 can by a worm gear 605 or another suitable connection rotatable. The worm gear 605 is a rotating element comprising a screw thread 607 , which by an actuator such. B. a stepper motor 609 can be rotated, and a helical toothing 611 on the cam 603 or on a separate component with the cam 603 connected is. The helical toothing 611 engages in the screw thread 607 one.

• - eine Pumpeneinrichtung zum Verdrängen von Hydraulikflüssigkeit zur Ansteuerung des ersten Kolbens 23a und zur Ansteuerung des zweiten Kolbens 23b, zum Beispiel ein nockenangesteuerter Master-Kolben, der Hydraulikflüssigkeit innerhalb des Hydraulikkreises in Abhängigkeit von der Rotation der Motornockenwelle pumpt;
• - einen Vorratsbehälter für Hydraulikflüssigkeit, zum Beispiel ein Motor-Hauptölkanal, der dazu konfiguriert ist, je nach Anforderungen Hydraulikflüssigkeit zum Hydraulikkreis hinzufügen oder aus diesem zu entfernen;
• - eine oder mehrere Passagen, welche die hydraulische Kommunikation (hydraulische Kopplung) zwischen den Komponenten des Kreises ermöglichen; und
• - Steuerungsventile, wie z. B. Wegeventile zum Steuern der hydraulischen Kommunikation zwischen den Komponenten des Hydraulikkreises und der Pumpeneinrichtung. Die Steuerungsventile sind Beispiele für hydraulische Verschaltung, die in der Lage ist, die Ansteuerung eines Kolbens zu steuern.

The hydraulic control system 21 includes a suitable hydraulic interconnection (in 2 not shown) for controlling the driving of the first piston 23a and the second piston 23b , The "activation" of a piston refers to the movement of a piston caused by hydraulic displacement. An exemplary hydraulic interconnection includes:

• - A pump means for displacing hydraulic fluid for driving the first piston 23a and for driving the second piston 23b for example, a cam-driven master piston that pumps hydraulic fluid within the hydraulic circuit in response to rotation of the engine camshaft;
• a hydraulic fluid reservoir, for example an engine main oil passage, configured to add or remove hydraulic fluid from the hydraulic circuit as required;
• - One or more passages, which enable the hydraulic communication (hydraulic coupling) between the components of the circle; and
• - Control valves, such. B. Directional valves for controlling the hydraulic communication between the components of the hydraulic circuit and the pump means. The control valves are examples of hydraulic circuitry capable of controlling the actuation of a piston.

Referring now to the control aspects of the hydraulic control system 21 , is the hydraulic control system 21 in some, but not necessarily all, of the examples: in a first mode, controlling the driving of the first piston 23a but not the second piston 23b ; and in a second mode, for controlling the parallel driving of the first piston 23a and the second piston 23b , The hydraulic control system 21 depending on whether in the first mode or in the second mode, whether the second piston 23b is controlled.

The parallel actuation of pistons refers to allowing a hydraulic displacement to simultaneously reach both of the pistons in parallel branches of the hydraulic circuit, without the actuation of one of the pistons being dependent on or presupposing any previous actuation (in series) of the other of the pistons , The coupled piston (s) and uncoupled piston (s) are configured to be exposed to an equal volume of continuous hydraulic fluid within the hydraulic circuit.

In some, but not necessarily all, examples is the hydraulic control system 21 in the first mode, when the first piston 23a at the beginning of a pump cycle (eg, at the beginning of the cam run of the pump means by a cam lobe) in hydraulic communication with a pump means while the second piston 23b hydraulically isolated from the pumping device. The hydraulic control system 21 is in the second mode when the first piston 23a and the second piston 23b at the beginning of the pumping cycle to be in simultaneous hydraulic communication with the pumping device. Therefore, in the second mode, the first piston becomes 23a and the second piston 23b controlled in parallel.

If the second piston 23b parallel to the first piston 23a is activated (second mode), pumped hydraulic fluid between the two pistons 23a . 23b divided, resulting in the total hydraulic displacement of the first piston 23a decreases and corresponding to the stroke of the first valve 27a reduced. The second piston 23b is a "lift control piston" as it acts as a hydraulic accumulator to control the lift characteristics of the first valve 27a depending on whether its driving takes place.

The device 7 is, in the first mode, for controlling the actuation of the first piston 23a configured, but not the second piston 23b by moving the first piston 23a in response to the hydraulic displacement and the movement of the second piston 23b is prevented in response to the hydraulic displacement. Enabling the movement of the first piston 23a may include closing a drain valve for draining hydraulic fluid from the hydraulic control system 21 to ensure that the hydraulic displacement by the pump means the first piston 23a emotional. Preventing the movement of the second piston 23b in response to the hydraulic displacement may include driving a directional control valve to the hydraulic Communication between the second piston 23b and the pump device to block.

The device 7 is, in the second mode, for controlling the parallel control of the first piston 23a and the second piston 23b configured by the movement of the first piston 23a in response to the hydraulic displacement and the movement of the second piston 23b in response to the hydraulic displacement. Enabling the movement of the second piston 23b in response to the hydraulic displacement may include driving a directional control valve to the hydraulic communication between the second piston 23b and to enable the pumping device. Enabling the movement of the first piston 23a and the big butt 23b may further include closing a drain valve for draining hydraulic fluid from the hydraulic control system 21 to ensure that the hydraulic displacement by the pump means the first piston 23a and the second piston 23b emotional.

The device 7 is not limited to having exactly one uncoupled piston, or to having exactly one coupled piston, like the one in FIG 2 is shown. 3 shows an exemplary device 7 comprising a further third, "coupled" piston 23c and another fourth, "uncoupled" piston 23d in addition to the first, "coupled" piston 23a and the second, "uncoupled" piston 23b out 2 , The device 7 is not even limited to having two coupled pistons, two uncoupled pistons, or even the same number of coupled and uncoupled pistons as that in FIG 3 is shown.

The device 7 out 3 is operable to drive a plurality of valves in parallel, wherein a plurality of uncoupled pistons (second piston 23b and fourth piston 23d ) serve as a separate Hubsteuerkolben.

The device 7 out 3 also includes all elements of the device 7 out 2 namely, the first valve 27a , the first piston 23a , the first chamber 25a , the second piston 23b , the second chamber 25b , the elastic device 29b , the adjustment device 30b and the hydraulic control system 21 , The device 7 out 3 is therefore a dual-valve device 7 ,

The third piston 23c is inside a third chamber 25c , The third piston 23c is inside the third chamber 25c movable, for example, by reciprocation, which is caused by displacement of hydraulic fluid. The third piston 23c is configured to have a second valve 27c (eg a poppet valve) for the combustion chamber 5 to drive, via a non-hydraulic coupling between the third piston 23c and the second valve 27c , such as Example, a direct mechanical coupling (surface-to-surface contact) or an indirect mechanical coupling (using one or more engaging mechanical components) or any other form of coupling, which is independent of hydraulic fluid, which is the first piston 23a , the second piston 23b and the third piston 23c controls. The third piston 23c can therefore be considered as a "coupled" piston. The third chamber 25c may be a valve opening for receiving a stem of the second valve 27c include. The movement of the third piston 23c is directly and only via mechanical forces in the movement of the second valve 27c transfer.

The other piston 23d is a fourth piston 23d the device 7 , The fourth piston 23d is located within the (further) fourth chamber 25d the device 7 and is movable within the fourth chamber 25d For example, by reciprocation caused by displacement of hydraulic fluid. The fourth piston 23d is configured not to drive any of the valves for any combustion chamber, for example the first valve 27a and the second valve 27c , The fourth chamber 25d does not include a valve port for receiving a stem of a poppet valve. The fourth piston 23d can therefore be considered as a "dummy" piston or "uncoupled" piston. The fourth piston 23d in the fourth chamber 25d defines a hydraulic accumulator that expands in volume as it moves through the fourth piston 23d filled with hydraulic fluid.

In the presentation of 3 is the first piston 23a mechanically with the first elastic device 29a coupled and is the third piston 23c mechanically with a third elastic device 29c coupled. In some examples, the first elastic means are 29a and the third elastic device 29c Valve return springs configured to the first valve 27a or the second valve 27c to bring back to their valve seats. In 3 is the second piston 23b mechanically with the (second) elastic device 29b coupled, which is the same as the elastic device 29b the device 7 out 2 , and the fourth piston 23d is mechanical with the fourth elastic device 29d coupled. The fourth elastic device 29d is designed to control the fourth piston 23b resist by deformation in response to the movement of the fourth piston 23d , The fourth elastic device 29d may have the same construction as the second elastic means 29b For example, the fourth elastic device 29b comprise a compression spring. The second elastic device 29b and the fourth elastic device 29d are designed to provide power to the hydraulic control system 21 when returning to their original shape following their deformation in the second mode.

In 3 but not necessarily in all examples is another adjustment means 30d intended. The further adjustment device 30d is designed to resist the fourth elastic device 29d to control. The structure of the other adjustment device 30d may be the same as the setup of the adjustment device 30b ,

In 3 becomes the adjustment device 30b and / or the further adjustment device 30d by an electronic control device 300 controlled, like that in 3 is shown. The electronic control device 300 can an electronic control module such. B. comprise an engine control unit, for controlling the adjusting device in response to the engine management requirements. In some, but not necessarily all, examples, the control of the adjustment means occurs 30b using a closed-loop control in which a measured output (eg, a measured maximum valve lift) is measured and fed back into the electronic control module to recalculate the adjustment required by the adjustment device.

In the picture of 3 are components of an exemplary hydraulic control system 21 shown in detail. In 3 is the hydraulic pumping device in the form of a master piston 31 provided, which is adapted to be controlled by a camshaft or other suitable actuator (not shown). The master piston 31 displaces hydraulic fluid in the hydraulic control system 21 when driven in use. It is this displacement of hydraulic fluid which controls the first to fourth pistons 23a - 23d causes. The first to fourth pistons 23a - 23d can therefore be considered a "slave" piston.

A reservoir drain valve 38 allows hydraulic communication between the device 7 and an external reservoir 36 (eg, a relatively low pressure main oil passage) when the reservoir drain valve 38 is open. When the reservoir drain valve 38 is opened, any displacement energy of the hydraulic fluid is discharged into the reservoir, so that none of the piston 23a - 23d is controlled. In use, the reservoir drain valve 38 be opened on demand to provide a zero valve lift if required.

A feed valve 34 supplies hydraulic fluid to the device 7 for filling of lost hydraulic fluid by hydraulic fluid from the reservoir 36 to provide a required hydraulic pressure in the device 7 maintain.

The hydraulic control system 21 further includes a directional control valve 33b configured to move (toggle) between two switch positions that control the hydraulic communication between the second piston 23b and the master piston 31 block or enable.

The construction of directional control valves is here indicated by the nomenclature np / nc, where np is the number of openings (sum of inlet and outlet openings), which with the directional control valve 33b and nc is the number of shift positions. The illustrated directional valve 33b is a 2/2-way valve (analogous to a one-way electric switch).

The hydraulic control system 21 further includes a directional control valve 33d configured to move (toggle) between two shift positions which control the hydraulic communication between the fourth piston 23d and the master piston 31 block or enable. The illustrated additional directional valve 33d is a 2/2 way valve. In other examples, the directional control valves 33b and 33d mechanically interconnected to form a single directional valve (eg, a 4/2-way directional control valve).

In some, but not necessarily all, examples is a drain valve 39 between the second piston 23b and its associated directional valve 33b intended. The drain valve 39 is configured to drain residual hydraulic fluid in the second chamber 25b is included while the directional control valve 33b the hydraulic communication between the second piston 23b and the master piston 31 blocked. This reduces the discharge of hydraulic fluid after a seal between the second piston 23b and the second chamber 25b , A drain valve 39 is also between the fourth piston 23d and its associated directional valve 33d provided to perform the same function.

Performing a switch between the above-described first mode and the second mode includes switching by the controller at least one or, optionally, all available directional control valves (eg, 33b, 33d) 37 ,

The directional valves 33b and 33d may be of the type slide valves, and the controller 37 out 3 can hydraulic actuators such. B. magnetic switch (not shown) to bias the slides in their working positions, as well as springs to bias the slider to its normal positions. The hydraulic actuators may be in selective hydraulic communication with an engine main oil passage, wherein the control of the hydraulic communication by at least one solenoid-operated directional control valve with electronic Control by an electronic control module (not shown) takes place.

In some, but not necessarily all, examples includes the valvetrain 9 a plurality of the devices 7 , And the solenoid valve controlled directional control valve is designed to be parallel to each other, the hydraulic control systems 21 the majority of the devices 7 to switch between the first mode and the second mode. Every device 7 therefore simultaneously switches between the first mode and the second mode.

Referring again to the device 7 in both 2 as well as 3 , the device can 7 Advantageously, in a Discrete Variable Valve Lift (DVVL) application, the first and second modes are DVVL modes. The DVVL modes allow the first valve 27a or more or less, depending on the engine management requirements, resulting in a more efficient and powerful engine 3 results.

Referring to both 2 as well as 3 are in a first, a high valve lift mode, the directional control valves 33b . 33d It is designed to control the actuation of the coupled piston (s) but not that of the uncoupled piston (s), for example by blocking the passage of hydraulic fluid to the uncoupled piston (s). The valve lift is high because the displaced hydraulic fluid is not shared between the coupled and uncoupled pistons. In a second, low valve lift mode, the directional control valves are 33b . 33d designed to control the parallel actuation of the coupled piston (s) and uncoupled piston (s). The valve lift is low in the second mode because the displaced hydraulic fluid is shared between the coupled and uncoupled pistons.

With special reference to 3 , in the first mode are the directional valves 33b . 33d designed to be the parallel control of the first piston 23a and the third piston 23c to control, but not the second piston 23b or the fourth piston 23c , In the second mode are the directional valves 33b . 33d designed to be the parallel control of the first piston 23a , the second piston 23b , the third, uncoupled piston 23c and the fourth, uncoupled piston 23c to control.

In the above examples, a total of more slave pistons are driven in the second mode than in the first mode. More specifically, to provide DVVL, in the second mode, a larger total slave-piston area is displaced by a given amount of displacement energy provided by the pumping means.

In the DVVL example described above, the first piston moves 23a in the first mode by a first maximum distance, and moves in the second mode by a second maximum distance, wherein the first maximum distance is greater than the second maximum distance. The third piston 23c moves in the first mode by a third maximum distance and moves in the second mode by a fourth maximum distance, wherein the third maximum distance is greater than the fourth maximum distance. The setting of the adjustment device 30b and / or the further adjustment device 30d controls the second maximum distance and the fourth maximum distance without changing the first maximum distance or the third maximum distance. This is because the first maximum distance and the third maximum distance occur in the first mode when the uncoupled piston and the uncoupled pistons are not in hydraulic communication with the master piston 31 located or located.

The various temporal and physical characteristics associated with each of the slave pistons may be adjustable to adjust the valve lift response, such as, for example, as shown in FIG. B. the valve acceleration behavior and the maximum stroke distance.

A time characteristic is the timing of switching the directional control valves 33b . 33d , In some, but not necessarily all, examples is the controller 37 configured to the directional valves 33b and 33d switch simultaneously (not sequentially). In other examples, the directional valves 33b and 33d switched sequentially. For example, one of the directional valves 33b . 33d switched to perform switching between the first mode and the second mode. The other of the directional valves 33b . 33d is then switched to a certain part of the valve lift event to deflect some hydraulic fluid energy from lifting the valves. The sequential switching allows a multi-stage valve lift control.

In another example of the timing control, the controller is 37 configured to switch individual directional control valves of the device 7 independent of other directional valves of the device 7 to control. If this approach is up 3 the device would be applied 7 have four DVVL modes (four discrete valve lift tips). In the first DVVL mode, both valves are on 33b . 33d opened to minimize the valve lift. In the second DVVL mode, only the directional valve is 33b opened to achieve a first medium valve lift. In the third DVVL mode, only the directional valve is 33d opened to achieve a second medium valve lift. In the fourth DVVL mode, both valves are on 33b . 33d closed to maximize the valve lift. The number of possible DVVL modes is 2 ^ n, where n is the number of uncoupled pistons of the device 7 is. Each DVVL mode allows a different valve lift tip when each of the uncoupled pistons has a different physical characteristic. In the following, various exemplary physical features are listed.

An exemplary physical feature is another resistance feature of the elastic device 29b . 29d , such as B. the spring constant. In some, but not necessarily all, examples, the resistance of the second elastic means differs 29b from the resistance of the fourth elastic device 29d , In some, but not necessarily all, examples, the resistances of the elastic device differ 29b . 29d that the uncoupled piston 23b . 23d are assigned by the resistors of the elastic device 29a . 29c that the coupled piston 23a . 23c For example, they are larger than these.

Another physical feature is the cross section (area) of the bores of the chambers for receiving the pistons. The driven surface of each piston is about the same size (slightly smaller to allow for thermal effects) as the bore of its chamber. The pistons in chambers with a larger bore displace less when they are supplied with the same amount of energy from hydraulic displacement. In some, but not necessarily all, examples, the bore of the second chamber is different 25b from the hole of the fourth chamber 25d , In some, but not necessarily all, of the examples, the bores of the chambers of the uncoupled pistons differ from the bores of the chambers of the coupled pistons, for example, they are larger than these.

Another physical feature is the maximum travel distance (stroke) of the pistons. In some, but not necessarily all, examples, the device includes 7 a limiter 35 (a stroke limiter) designed to limit a maximum travel distance of at least one of the uncoupled pistons. In some examples, the limiter 35 as a base of the chamber or as a restriction in the bore of the chamber. A limiter 35 disturbs the stroke of at least one of the uncoupled pistons, so that the uncoupled piston against the limiter 35 abuts before the maximum valve lift occurs (eg, before a cam lobe hits the master piston 31 adjusted). A limiter 35 can be used to limit the stroke of one of the uncoupled pistons relative to the other of the uncoupled pistons. This leads to the sequential control of the uncoupled pistons to allow a multi-stage valve lift control.

Another physical feature is the masses of the pistons. The larger mass pistons have greater inertia effects when supplied with the same amount of energy (hydraulic displacement). In some, but not necessarily all, examples, the mass of the second piston is different 23b from the mass of the fourth piston 23d , In some, but not necessarily all, examples, the masses of the uncoupled pistons differ from the masses of the coupled pistons, for example, they are larger than these.

The adjustment device 30b and the other adjustment device 30d out 3 can be controlled separately. The device 7 may be provided with additional separately controllable uncoupled pistons, each uncoupled piston being provided with resilient means and a control means to provide additional different valve lift curves for the valve (s) of the device 7 to allow each Ventilhubkurve has a different shape.

In some, but not necessarily all, examples, the temporal and / or physical characteristics are selected so that in addition to the intended difference in the maximum stroke distance, the acceleration and deceleration behavior of the valve can be controlled in the first and second modes.

In some, but not necessarily all, examples, the temporal and / or physical characteristics are selected to ensure that the valves begin to lift before the uncoupled pistons begin to move.

4 shows an example of the device 7 comprising at least two coupled pistons. In the example of 4 is the hydraulic control system 21 , in combination with at least one uncoupled piston 23b , configured it to the device 7 to allow a plurality of valves to be raised in the first mode and less valves to be raised in the second mode. In the 4 illustrated device 7 has two coupled pistons, which is why in this example the first mode is a DVA mode (Dual Valve Actuation) and the second mode is SVA (Single Valve Actuation) mode.

The device 7 out 4 includes all elements of the device 7 out 2 , In some, but not necessarily all, examples, the device includes 7 out 4 most elements of the device 7 out 3 , however, is the optional fourth piston 23d not shown for reasons of clarity, and the directional control valves 33b . 33d are replaced by another 4/2-way directional control valve 41 , The common elements include at least: the first valve 27a , the first piston 23a , the first chamber 25a , the first elastic device 29a , the adjustment device 30b , the second piston 23b , the second chamber 25b , the second elastic device 29b , the third valve 27c , the third piston 23c , the third chamber 25c , the third elastic device 29c , the hydraulic control system 21 , including the master piston 31 , of the storage container 36 , the reservoir drain valve 38 , the feed valve 34 and a drain valve 39 for the second piston 23b ,

The device 7 out 4 includes a first device, such. B. a directional control valve, to block the hydraulic communication between the third piston 23c and the master piston 31 in the second mode and for enabling hydraulic communication between the third piston 23c and the master piston 31 in the first mode. Therefore, the second valve becomes 27c raised only in the second mode. The first valve 27a is raised in both modes. The directional control valve may be a 2/2-way directional valve similar to that in relation to 3 or a section of a 4/2-way directional control valve 41 as it is in 4 is shown. The directional control valve can therefore be operated to the device 7 switch between the first, the DVA mode and the second, the SVA mode.

The device 7 also includes a second device, such. B. a directional control valve, to block the hydraulic communication between the second piston 23b and the master piston 31 in the first mode and for enabling hydraulic communication between the second piston 23b and the master piston 31 in the second mode. The directional control valve may be a 2/2-way directional valve similar to that in relation to 3 or any other portion of the 4/2-way directional control valve 41 as it is in 4 is shown.

In some, but not necessarily all examples, the first device and the second device, in 4 embodied in only one way valve 41 , activated in use to switch between a DVA mode and an SVA mode, which compensates for the tendency, the first valve 27a continue to raise hydraulically in SVA mode. In the first mode (DVA) is the directional control valve 41 designed to be the parallel control of the first piston 23a and the third piston 23c to control, but not the second piston 23b , In the first mode, a total of two pistons are driven. In the second mode (SVA) is the directional control valve 41 designed to be the parallel control of the first piston 23a and the second piston 23b to control, but not the third piston 23c , The combination of pistons driven in the second mode is different from the combination of pistons driven in the first mode. In the second mode, a total of two pistons are driven.

In the above example, but not necessarily in all examples, the same total number of slave pistons are driven in the second mode (SVA) and in the first mode (DVA). In particular, the compensation occurs in SVA mode because in the second mode, an equal amount of displacement energy displaces an equal slave-piston total area, although one of the slave pistons (the third piston 23c ) is no longer activated. Therefore, it should be understood that deviations from the illustrated examples are possible, for example, in SVA mode, a different number of slave pistons may be driven compared to the DVA mode, while still providing compensation when the slave pistons Total surfaces or other features of the slave pistons are adequately controlled.

In some, but not necessarily all, of the examples relating to a DVA-SVA implementation, the features associated with the second piston 23b are chosen so that they coincide as much as possible with the characteristics that the third piston 23c belong. The features can be chosen so that the first piston 23a is moved in use by a first maximum distance and moved in the second mode by a second maximum distance, wherein the third piston 23c in the first mode by a third maximum distance, and wherein the first maximum distance, the second maximum distance and the third maximum distance are equal (within the procedural tolerances). The features include, but are not limited to, one or more of: piston mass; Chamber bore; stroke; Timing of switching the directional control valve 41 or the directional valves 41 ; Resistance of the elastic device. Each of these features has been referred to above 3 described in detail.

The setting of the adjustment device 30b controls the second maximum distance without the to change the first maximum distance or the third maximum distance. This is because the first maximum distance and the third maximum distance occur when the second piston 23b not in hydraulic communication with the master piston 31 located. A closed loop may be used to control the second maximum distance to reduce the differences between the first maximum distance and the second maximum distance.

In some, but not necessarily all, examples, all of the above features are identical to the first piston 23a , the second piston 23b and the third piston 23c

In the presentation of 4 includes the only 4/2-way directional valve 41 the first device and the second device. The directional valve 41 consists of a single movable element (eg a slide) designed to be moved along a single axis to switch between a normal position and at least one first working position. In the first mode, the movable member is in a first position, in which the movable member controls the hydraulic communication between the second piston 23b and the master piston 31 blocked and the hydraulic communication between the third piston 23c and the master piston 31 allows. In the second mode, the movable member is in a second position, in which the movable member controls the hydraulic communication between the third piston 23c and the master piston 31 blocked and the hydraulic communication between the second piston 23b and the master piston 31 allows.

In some, but not necessarily all, examples, the first position is the normal position of the directional control valve 41 and the second position is the working position, so that the device 7 works normally in DVA mode.

The directional valve 41 It may have any structure based on a single movable element that provides the first device and the second device.

In the example of 4 but not necessarily in all examples, performing switching between the first mode and the second mode includes switching by the controller 43 , the first device and the second device. The first device and the second device are in 4 as a 4/2-way directional valve 41 embodied, which includes a slider. The control device 43 may include a hydraulic actuator (or a plurality of hydraulic actuators) to bias the slider (s) to its working position, and a spring (s) to bias the slider (s) to its normal position. The hydraulic actuator (s) may be in selective hydraulic communication with a main engine oil passage, wherein the hydraulic communication is controlled by at least one solenoid-operated directional control valve by an electronic control module (not shown) ,

In some, but not necessarily all, examples includes a valvetrain 9 a plurality of the devices 7 , And the solenoid valve controlled directional control valve is designed to be parallel to each other, the hydraulic control systems 21 the majority of the devices 7 to switch between the first mode and the second mode. Every device 7 As a result, it simultaneously switches between the first mode and the second mode.

Alternative construction variants for the device 7 compared to 4 may include additional coupled valves and / or additional uncoupled valves. In such construction variants, the directional control valve 41 or additional directional control valves can be used to control the activation of at least one uncoupled valve for each coupled valve, which is no longer controlled.

• in einem ersten Modus, das Bewirken der hydraulischen Ansteuerung eines ersten Kolbens 23a, nicht aber eines zweiten Kolbens 23b;
• das Umschalten aus dem ersten Modus in einen zweiten Modus, und in dem zweiten Modus, das Bewirken der gleichzeitigen hydraulischen Ansteuerung des ersten Kolbens 23a und des zweiten Kolbens 23b,
• wobei sich der erste Kolben 23a innerhalb einer ersten Kammer 25a befindet, dazu konfiguriert ist, ein erstes Ventil 27a für die Brennkammer 5 anzusteuern, und dazu ausgelegt ist, sich bei hydraulischer Ansteuerung innerhalb der ersten Kammer 25a zu bewegen, zum Bewegen des ersten Ventils 27a;
• wobei sich der zweite Kolben 23b innerhalb einer zweiten Kammer 25b befindet, und dazu konfiguriert ist, keines der Ventile für irgendeine Brennkammer anzusteuern, und dazu ausgelegt ist, sich bei hydraulischer Ansteuerung innerhalb der zweiten Kammer 25b zu bewegen, wobei der Ansteuerung des zweiten Kolbens 23b durch die elastische Einrichtung 29b widerstanden wird, wobei der Widerstand der elastischen Einrichtung durch die Einstellungseinrichtung 30b gesteuert wird.

According to some, but not necessarily all, examples of the present disclosure, a method of moving at least one valve is disclosed 27a for a combustion chamber 5 an internal combustion engine 3 provided, the method comprising the following steps:

• in a first mode, effecting the hydraulic actuation of a first piston 23a but not a second piston 23b ;
• switching from the first mode to a second mode, and in the second mode, causing the simultaneous hydraulic actuation of the first piston 23a and the second piston 23b .
• where the first piston 23a within a first chamber 25a is configured to a first valve 27a for the combustion chamber 5 to drive, and designed to do so is located at hydraulic control within the first chamber 25a to move, to move the first valve 27a ;
• wherein the second piston 23b within a second chamber 25b is configured and configured to drive none of the valves for any combustion chamber, and is configured to be in hydraulic actuation within the second chamber 25b to move, the control of the second piston 23b through the elastic device 29b is resisted, wherein the resistance of the elastic means by the adjusting means 30b is controlled.

An electronic control module may include means for causing the device 7 performs the procedure. The apparatus may include at least one processor, at least one memory containing computer program code, the at least one memory and the computer program code configured to cause the at least one processor to operate 7 at least perform the procedure. The electronic control module may be configured to control the driving of the above-described directional control valves to the device 7 in the DVVL modes described above (see 3 ) and / or DVA / SVA modes (see 4 ) to operate.

For purposes of this disclosure, it should be understood that the electronic control module (s) may each comprise a control unit or computer device having one or more electronic processors. A corresponding vehicle and / or system may comprise a single control unit or, alternatively, various functions of the control module (s) may be embodied or hosted in various control units or control modules. A set of instructions could be provided that, when executed, cause the control module (s) or control unit (s) to implement the control techniques described herein (including the described method (s)). The set of instructions may be embedded in one or more electronic processors, or alternatively, the set of instructions could be provided as software to be executed by one or more electronic processors. For example, a first control module may be implemented in software executing on one or more electronic processors, and one or more other control modules may also be implemented in software executing on one or more electronic processors, which may be optional the same processor or processors as the first control module. It should be understood, however, that other arrangements are also feasible, and therefore, the present disclosure should not be limited to any particular arrangement. In any event, the above-described set of instructions may be embedded in a computer-readable storage medium (eg, a non-volatile storage medium) which may include any mechanism for storing information in a form that is provided by a machine or electronic processors / computing devices readable, including, but not limited to: a magnetic storage medium (eg floppy disk); an optical storage medium (eg, CD-ROM); a magneto-optical storage medium; a read-only memory (ROM); a Random Access Memory (RAM); an erasable programmable memory (eg EPROM and EEPROM); a flash memory or electrical or other types of media for storing such information / instructions.

Although in the foregoing paragraphs embodiments of the present invention have been described with reference to various examples, it should be understood that changes may be made to the present examples without departing from the scope of the present invention as defined in the following claims. For example, independently controllable directional control valves may be provided to control the actuation of a plurality of coupled pistons and to control the actuation of one or more uncoupled pistons to a device 7 to provide at different times in DVVL modes (see 3 ) and DVA / SVA modes (see 4 ) can be operated. Further, although the above description relates to a hydraulic control system, an alternative practical implementation is a pneumatic control system in which the various pistons described above are not driven by hydraulic fluid but by pneumatic gases.

The features described in the foregoing description may also be used in other combinations than the combinations explicitly described herein.

Although functions have been described with reference to certain features, these functions may also be practicable through other features, whether described herein or not.

Although functions have been described with reference to particular embodiments, these functions may also be present in other embodiments, whether described herein or not.

While the foregoing description has sought to draw attention to those features of the present invention which are believed to be of particular importance; however, it should be understood that Applicant claims protection with respect to any patentable feature or combination of features referred to above and / or illustrated in the drawings, whether or not of particular value was laid or not.

Claims (14)

Device for moving at least one valve for a combustion chamber of an internal combustion engine, the device comprising a first piston within a first chamber configured to drive a first valve for the combustion chamber, the first piston adapted to be driven by a hydraulic control system to move within the first chamber to move the first valve; a second piston within a second chamber configured to drive none of the valves for any combustion chamber, the second piston adapted to be driven by the hydraulic control system to move within the second chamber; an elastic device adapted to resist the driving of the second piston; and an adjustment device configured to control the resistance of the elastic device. Apparatus according to any one of the preceding claims, wherein the adjustment means is adapted to adjust a bias acting on the elastic means. Apparatus according to any one of the preceding claims, wherein the adjustment means is arranged to allow more than two adjustment stages of the resistance of the elastic means. Apparatus according to any one of the preceding claims, wherein the adjustment means comprises a rotating member coupled to the resilient means and having a screw thread for positional adjustment. Apparatus according to any one of the preceding claims, comprising at least one further piston configured to actuate none of the valves for any combustion chamber, at least one further piston being within a further chamber and being adapted to be actuated by the hydraulic control system. to move within his other chamber; optionally comprising the hydraulic control system, wherein the hydraulic control system is configured to control the sequential actuation of the second piston and the at least one further piston; and / or optionally comprising a further elastic device, which is designed to resist the actuation of the at least one further piston, and a further adjustment device, which is designed to set the resistance of the further elastic device; and / or optionally comprising a limiter adapted to limit a maximum travel distance of the at least one further piston or the second piston in order to control the sequential activation of the second piston and the at least one further piston. Apparatus according to any one of the preceding claims, comprising the hydraulic control system, the hydraulic control system being configured to: in a first mode, controlling the driving of the first piston but not the second piston; and in a second mode, controlling the parallel driving of the first piston and the second piston by controlling the simultaneous driving of the first piston and the second piston; optionally comprising means for blocking hydraulic communication between the second piston and a hydraulic pump means in the first mode, but not in the second mode; and / or optionally wherein in the first mode the first piston is movable a first maximum distance and in the second mode is movable a second maximum distance, the adjustment of the adjustment means controlling the second maximum distance without changing the first maximum distance , Apparatus according to any one of the preceding claims, comprising a third piston within a third chamber configured to drive a second valve, the third piston being adapted to be actuated by the hydraulic control system to move within the third chamber to move the second valve. Apparatus according to any one of the preceding claims, comprising a first elastic means adapted to resist the actuation of the first piston; optionally, a resistance of the first elastic means differs from a resistance of the elastic means adapted to resist the driving of the second piston. Apparatus according to any one of the preceding claims, wherein the first chamber includes a first bore sized to accommodate the first piston, the first bore has a first surface, the second chamber including a second bore sized to accommodate the second piston in that the second bore has a second surface, and wherein the first surface and the second surface are different. The apparatus of any one of the preceding claims, wherein the first piston and the first valve have a first combined mass, the second piston having a second mass, and wherein the first combined mass and the second mass are different. Device after Claim 7 , depending on Claim 6 or 7 wherein the hydraulic control system is configured to: in the first mode, control the parallel driving of the first piston and the third piston but not the second piston; and in the second mode, for controlling the parallel driving of the first piston and the second piston, but not the third piston; wherein, optionally, the first piston is movable a first maximum distance in the first mode and is movable a second maximum distance in the second mode, wherein the third piston is movable a third maximum distance in the first mode, and wherein the first maximum Distance, the second maximum distance and the third maximum distance are equal, the device optionally comprising a closed loop system for adjusting the adjusting means to reduce the differences between the first maximum distance and the second maximum distance; and / or optionally comprising means for blocking the hydraulic communication between the third piston and a hydraulic pumping device of the hydraulic control system in the second mode, but not in the first mode; and / or optionally comprising a movable element, which in the first mode is movable to a first position, in which the movable element blocks the actuation of the second piston and enables the actuation of the third piston, and in a second mode to a second position is movable, in which the movable member blocks the driving of the third piston and allows the driving of the second piston, wherein optionally the movable member in the first position blocks the hydraulic communication between the second piston and a hydraulic pump means of the hydraulic control system and the hydraulic communication between the third piston and the hydraulic pump means, and wherein the movable member in the second position blocks the hydraulic communication between the third piston and the hydraulic pump means and the hydraulic communication between the second piston and the hydraulic pump means, and / or optionally wherein the movable member consists of a single slider which is adapted to move along a single axis between the first position and the second position. An internal combustion engine comprising the device according to any one of the preceding claims; the internal combustion engine optionally having a predetermined number of manifold extensions opening into combustion chambers, each manifold extension having an associated longitudinal center axis, an axis of reciprocation of the second piston not intersecting a longitudinal center axis of one of the manifold extensions. Valve gear, comprising the device according to one of Claims 1 to 11 ; and optionally comprising a plurality of the devices, the valvetrain comprising a controller configured to control in parallel the hydraulic control systems of the plurality of devices to switch between the first mode and the second mode. Vehicle, including the internal combustion engine Claim 12 ,

Images