JP4982867B2 - Device for changing the control time of a gas exchange valve of an internal combustion engine - Google Patents

Description

The present invention relates to a device for changing the control time of a gas exchange valve, i.e., an intake valve or an exhaust valve, of an internal combustion engine, i.e., an internal combustion engine. A device for changing the control time of the gas exchange valve,
A hydraulic actuating device having first and second interacting pressure chambers is provided,
The supply or derivation of pressure medium to or from both pressure chambers allows the camshaft phase position relative to the crankshaft to be maintained or deliberately changed;
A control valve comprising a first second work connection, one outflow connection and one inflow connection is provided, the first work connection communicating with the first pressure chamber; The second working connection is in communication with the second pressure chamber, the outflow connection is in communication with the tank, and the outflow connection is loaded with a pressure medium,
The control valve is brought into four control positions by an actuating unit;
-In the first control position of the control valve, neither the first work connection nor the second work connection is in communication with the inflow connection;
-In the second control position of the control valve, the first work connection is in communication with the outflow connection and the second work connection is in communication with the inflow connection;
-In the third control position of the control valve, the first work connection and the second work connection are not in communication with either the outflow connection or the inflow connection, or the first work connection And the second work connection portion communicates only with the inflow connection portion,
-In the fourth control position of the control valve, a device of the type in which the second work connection communicates with the outflow connection and the first work connection communicates with the inflow connection.

  In an internal combustion engine, a camshaft is used to operate a gas exchange valve. The camshafts are attached to the internal combustion engine so that the cams provided on these camshafts are in contact with cam followers such as bucket-type tappets, swing arms or rocker arms. When the camshaft is rotated, the cam rolls along the cam follower and this cam follower operates the gas exchange valve. Therefore, depending on the position and shape of the cam, the opening time and opening amplitude of the gas exchange valve, or the opening time and closing time of the gas exchange valve are also defined.

  A recent engine concept trend is to variably design the valve drive. On the other hand, it is desirable that the valve stroke and valve opening time until complete shutoff of each cylinder can be set variably. For this purpose, concepts such as switchable cam followers or electrohydraulic or electric valve actuation are set. Furthermore, it has been found advantageous to be able to influence the opening and closing times of the gas exchange valve during operation of the internal combustion engine. In this case, it is desirable to be able to influence the opening or closing timing of the intake or exhaust valves separately, for example in order to intentionally adjust the defined valve overlap. Adjusting the opening or closing time of the gas exchange valve in relation to the current characteristic map area of the engine, for example, the current rotational speed or the current load, reduces the fuel consumption rate and is advantageous for the exhaust gas characteristics. It can affect and improve engine efficiency, maximum torque and maximum output.

  The variability of the valve control time is achieved by changing the phase position of the camshaft relative to the crankshaft. In this case, the camshaft is usually drive-coupled to the crankshaft via a chain drive, a belt drive, a gear drive or a drive concept having the same effect. A device for changing the control time of the internal combustion engine (hereinafter referred to as “camshaft adjuster”) is installed between the chain transmission device, belt transmission device or gear transmission device driven by the crankshaft and the camshaft. It has been. This device transmits torque from the crankshaft to the camshaft. This device ensures that the phase position between the crankshaft and the camshaft is maintained during operation of the internal combustion engine and, if desired, the camshaft rotates relative to the crankshaft within a certain angular range. It is formed so that it can be done.

  In an internal combustion engine with one camshaft for each of the intake and exhaust valves, one camshaft adjuster can be provided for each of the intake and exhaust valves. Thereby, the opening timing and closing timing of the intake valve and the exhaust valve can be shifted relative to each other in time, and the valve overlap can be adjusted intentionally.

  Modern camshaft adjuster seats are usually located at the drive side of the camshaft, that is, at the input end. However, the camshaft adjuster may be located on the intermediate shaft, non-rotating component or crankshaft. The camshaft adjuster is driven by a crankshaft and has an input vehicle that maintains a fixed phase relationship with the crankshaft, an output vehicle that is drivingly coupled to the camshaft, and torque from the input vehicle to the output vehicle. It consists of an adjusting mechanism that transmits. In the case of a camshaft adjuster not arranged on the crankshaft, the input wheel may be formed as a chain wheel (sprocket), a belt wheel (pulley) or a gear, and the chain transmission, belt transmission or gear transmission Driven by the crankshaft. The adjusting mechanism can be operated electrically, hydraulically or pneumatically.

  Two advantageous configurations of the hydraulically adjustable camshaft adjuster are the so-called axial piston adjuster and the rotary piston adjuster.

  In the case of an axial piston adjuster, the input wheel is connected to the piston, and this piston is connected to the output part via a helical tooth line (helical spline). The piston separates the hollow chamber formed by the output portion and the input wheel into two pressure chambers that are arranged to be opposed to each other in the axial direction. When one pressure chamber is loaded with pressure medium and the other pressure chamber is connected to the tank, the piston moves axially. The axial movement of the piston is converted by the helical spline into the relative rotation of the input wheel with respect to the output part and thus into the relative rotation of the camshaft with respect to the crankshaft.

  The second configuration of the hydraulic camshaft adjuster is a “rotary piston adjuster”. In this rotary piston adjuster, the input wheel is coupled to the stator so as not to be relatively rotatable. The stator and the rotor are arranged concentrically with each other, in which case the rotor is frictionally connected, shape connected (engaged by engagement) or material connected, eg by press fit, screw connection or weld connection. Connected to camshaft, camshaft extension or intermediate shaft. The stator is formed with a plurality of hollow chambers arranged at intervals in the circumferential direction, and these hollow chambers extend radially outward from the rotor. These hollow chambers are partitioned in a pressure-tight manner by side covers in the axial direction. Extending into these hollow chambers are vanes each coupled to a rotor, which divides each hollow chamber into two pressure chambers. By intentionally connecting the individual pressure chambers to a pressure medium pump or tank, the camshaft phase relative to the crankshaft can be adjusted or maintained.

  In order to control the camshaft adjuster, engine characteristic data such as load conditions and rotational speed are detected by sensors. These characteristic data are transmitted to an electronic control unit which controls the inflow and outflow of the pressure medium to the various pressure chambers after comparing these characteristic data with the characteristic data map of the internal combustion engine.

  In order to adjust the camshaft phase position relative to the crankshaft, in the hydraulic camshaft adjuster, one of the two interacting pressure chambers formed in one hollow chamber has a pressure chamber. Connected to the pressure medium pump, the other pressure chamber is connected to the tank. As the pressure medium flows into one pressure chamber and the pressure medium flows out from the other pressure chamber at the same time, the piston separating the two pressure chambers is moved in the axial direction, so that in the axial piston regulator, the helical spline is moved. The camshaft is rotated relative to the crankshaft. In the rotary piston adjuster, the movement of the vane is caused by the pressure load of one pressure chamber and the release pressure of the other pressure chamber, and thus the camshaft is directly rotated relative to the crankshaft. In order to maintain the phase position, both pressure chambers are connected to the pressure medium pump or disconnected from both the pressure medium pump and the tank.

  Control of the pressure medium flow into or out of the pressure chamber is effected by a control valve, usually a 4 port 3 position proportional valve. The valve housing is provided with a respective connection (work connection) for each pressure chamber as a port, a connection leading to the pressure medium pump, and at least one connection leading to the tank. . A control piston which is movable in the axial direction is arranged inside a valve housing formed in a substantially hollow cylindrical shape. This control piston can be brought into any position between two defined end positions in the axial direction against the spring force of the spring element by means of an electromagnetic actuator. The control piston further comprises an annular groove and a control edge, whereby the individual pressure chambers can be selectively connected to a pressure medium pump or to a tank. In addition, a position of the control piston may be provided so that the pressure chamber is shut off from both the pressure medium pump and the pressure medium tank.

  German Offenlegungsschrift 100 63 222 discloses such a device. This device is a rotary piston device. The stator that is drivingly connected to the camshaft is rotatably supported by a rotor that is non-rotatably connected to the camshaft. The stator is formed with a notch open to the rotor. A side cover is provided in the axial direction of the device, and the side cover partitions the device. The notch is closed in a pressure-tight manner by the rotor, the stator, and the side cover, thereby forming a plurality of pressure chambers. Axial grooves are provided on the outer peripheral surface of the rotor, and vanes (blades) are arranged in these grooves. The vane extends into the notch. The vanes are formed such that these vanes divide the pressure chamber into two interacting pressure chambers each. By introducing or deriving a pressure medium to or from these pressure chambers, the camshaft phase position relative to the crankshaft can be selectively maintained or adjusted.

  Two lock pins are arranged on the side cover. These lock pins are loaded with a force toward the rotor by spring means. A plurality of grooves extending in the circumferential direction are provided on an end surface of the rotor facing the lock pin. These grooves are arranged such that both locking pins engage in one groove at a defined intermediate position when none of these grooves is loaded with pressure medium. Each lock pin is in contact with the circumferential end of each groove. Thus, the rotor is locked relative to the stator, thereby preventing relative rotation. The pressure medium chamber can be filled with the pressure medium via the first pressure medium line and the second pressure medium line. When the first pressure medium chamber is filled with the pressure medium, one end face of the one lock pin is also loaded with the pressure medium. As a result, the corresponding lock pin is pushed into the receiving hole provided in the side cover, and the rotor can be adjusted relative to the stator in one direction. In this case, the other groove in which the other lock pin is still engaged is formed so that the rotor can be adjusted from the center position to the maximum value. Correspondingly, the rotor is adjusted relative to the stator in the other direction. The device comprises a compensation spring, one end of which is fixed to the rotor and the other end to the stator, and this compensation spring is a drag torque applied to the rotor by the camshaft. Compensate for (Schleppmoment).

  DE 19853670 discloses a control valve which serves to control the pressure medium flow to the pressure chamber in relation to the current load conditions of the internal combustion engine. The control valve comprises an operating unit, a valve housing formed in a substantially hollow cylindrical shape, and a control piston formed in a substantially hollow cylindrical shape. The control piston is accommodated in the valve housing so as to be movable in the axial direction. Has been. The valve housing is formed with two working connections, one inflow connection and one outflow connection. The operating unit may be an electromagnet, for example. The electromagnet moves the control piston against the spring force through the push rod by applying a control current. In relation to the position of the control piston inside the valve housing, the inflow connection is connected to one of the two work connections and the tank connection is connected to the other work connection, respectively. Or both work connections are disconnected from the inflow or outflow connections. Thereby, the pressure medium is supplied to one pressure chamber, and the pressure medium flows out from the other pressure chamber, which causes a change in the phase position of the camshaft with respect to the crankshaft.

  The major drawback of such a control valve combined with a camshaft adjuster with a center position lock is that the pressure medium connection is connected to one of the work connections when not energized. That is the fact. That is, when a malfunction of the actuating member or the actuator occurs, the pressure medium is guided to one of the pressure chambers and simultaneously to one of the lock pins. Thereby, the camshaft adjuster is rotated to one of the two maximum positions after the failure of the operating unit in relation to the arrangement of the control valves, and this phase position is determined by the internal combustion engine. Holds throughout operation. The camshaft adjuster is locked at the center position when the device is in a non-pressure state. This center position is selected so that the internal combustion engine has good starting and running characteristics at this phase position of the camshaft relative to the crankshaft, so the maximum phase shift relative to the center position Will cause worse starting and running characteristics of the internal combustion engine.

SUMMARY OF THE INVENTION Accordingly, the problem underlying the present invention is to avoid these disadvantages mentioned above and thus to lock the camshaft relative to the crankshaft and the hydraulic actuator to be locked. Automatic to the phase position where the hydraulic actuator is in position or when the hydraulic actuator is first rotated on the camshaft without restarting the piston or vane against the end stop It is to provide a method which can be brought to the phase position in which the hydraulic actuator is located in a position such as to be brought to a locked position.

  Furthermore, it is desirable to propose a method for bringing the actuator into the locked position in the unlocked stop position (Abstellposition).

According to the present invention, the above object is carried out in the first method according to the superordinate concept part of claim 1 in the order described:
Achieving the defined phase position ψ + X ° KW (Anfahren) and holding the phase position,
-Shut off the ignition device,
Adjusting the second control position or the fourth control position to hold the phase position ψ + X ° KW until the rotational speed sensor device reports the rotational speed n = 0,
-Detecting the rotational speed n via the rotational speed sensor device;
Holding the taken second or fourth control position at a pre-defined time;
- the working unit is stopped after the lapse of said time,
Is solved.

  In this way, the actuating device is brought from the center lock position to a phase position that is offset by a predetermined amount X ° crankshaft (KW) during the stop process. The X sign of X is related to the adjustment direction of the actuator when it is not yet sufficiently filled with pressure medium. For example, if the device does not have a compensation spring, or if it has a compensation spring that applies only a small torque to the rotor stator system (but this torque is less than the drag torque of the rotating camshaft), this phase position Is positioned in the “early” direction relative to the center lock position. When the compensation spring torque is larger than the camshaft drag torque and in the opposite direction to the camshaft drag torque, this phase position is located in the “slower” direction relative to the center lock position. After the ignition device is shut off, it is desirable to take a control position that prevents the operation unit from moving to the center position until the rotation speed sensor device reports the rotation speed n = 0. The control position taken is subsequently held for a specified time. This is necessary. This is because the rotation speed sensor device already reports the rotation speed n = 0 at the last rotation of the camshaft / crankshaft, and the operating unit is moved beyond the center position to an undesired position based on the alternating moment. This is because there is a risk of losing. By this holding time, the relaxation effect of the internal combustion engine, for example, the relaxation of the piston or the like (which may also cause the wrong position to be taken) is received.

According to the present invention, the above object is carried out in the order of the following method steps in the second method of the form described in the superordinate concept part of claim 2:
The following method steps are carried out in the order given during the stop process of the internal combustion engine:
Achieve and maintain the defined phase position ψ + X ° KW;
-Shut off the ignition device,
Adjusting the second control position or the fourth control position to hold the phase position ψ + X ° KW until the rotational speed sensor device reports the rotational speed n = 0,
-Detecting the rotational speed n via the rotational speed sensor device;
Holding the taken second or fourth control position at a pre-defined time;
- the working unit is stopped after the lapse of said time,
And during the starting process of the internal combustion engine, the following method steps are carried out in the order given:
-Adjusting the first control position;
-Detecting the number of revolutions n in the crankshaft or camshaft;
If the rotational speed n> 0, detect the pressure medium pressure p;
If the pressure medium pressure p is greater than a predefined value, the control position is adjusted based on a characteristic map filed in the control unit;
Is solved.

  As a result, locking is achieved in the unlocked state, and the pressure medium pressure reaches a specified value, so that the lock can only be released after a sufficient supply of pressure medium to the device is guaranteed. Is guaranteed. This prevents piston or vane abutment as would occur in an unlocked device that is not fully pressurized.

According to the present invention, in the third method of the type described in the superordinate concept part of claim 3, the following method steps are carried out in the order described:
-Adjusting the first control position;
-Detecting the number of revolutions n in the crankshaft or camshaft;
If the rotational speed n> 0, detect the pressure medium pressure p;
If the pressure medium pressure p is greater than a predefined value, the control position is adjusted based on a characteristic map filed in the control unit;
Is solved.

BRIEF DESCRIPTION OF THE DRAWINGS Further features of the present invention will become apparent from the following description and drawings. In the following, embodiments of the present invention will be described with reference to the drawings.

FIG. 1 is a longitudinal sectional view of a hydraulic actuator,
FIG. 2 is a cross-sectional view of the hydraulic actuator shown in FIG.
FIG. 3 is a flow chart relating to a method for starting an internal combustion engine equipped with a device according to the invention for changing the control time of a gas exchange valve,
FIG. 4 is a schematic view of a device according to the invention for changing the control time of a gas exchange valve of an internal combustion engine,
FIG. 5a is a longitudinal sectional view showing the control valve of the device according to the invention for changing the control time of the gas exchange valve of the internal combustion engine in a first control position;
FIG. 5b is a longitudinal sectional view showing the control valve shown in FIG. 5a in the second control position;
FIG. 5c is a longitudinal sectional view showing the control valve shown in FIG. 5a in a third control position;
FIG. 5d is a longitudinal sectional view showing the control valve shown in FIG. 5a in a fourth control position;
FIG. 6 is a diagram showing the relationship between the volumetric flow rate from the inlet connection to the pressure chamber and the position of the control piston relative to the valve housing;
FIG. 7 is a flow chart relating to a method for controlling and shutting off an internal combustion engine equipped with a device according to the invention for changing the control time of a gas exchange valve;
FIG. 8 is a schematic diagram showing an apparatus for changing the control time of a gas exchange valve of an internal combustion engine according to a known prior art.

DETAILED DESCRIPTION OF THE DRAWINGS FIGS. 1 and 2 show a hydraulic actuating device 1a of a device 1 for changing the control time of a gas exchange valve of an internal combustion engine. The hydraulic actuator 1 a mainly includes a stator 2 and a rotor 3 disposed concentrically with the stator 2. An input wheel 4 is coupled to the stator 2 so as not to be relatively rotatable. In the illustrated embodiment, the input wheel 4 is formed as a chain wheel, that is, a sprocket. A configuration in which the input wheel 4 is formed as a belt wheel (pulley) or a gear is also conceivable. The stator 2 is rotatably supported by the rotor 3. In this case, in the illustrated embodiment, five notches 5 arranged at intervals in the circumferential direction are provided on the inner peripheral surface of the stator 2. ing. These notches 5 are respectively formed in the radial direction by the stator 2 and the rotor 3, in the circumferential direction by the two side walls 6 provided on the stator 2, and in the axial direction by the first side cover 7 and the second side cover 8. And are each partitioned by. Thus, each of these notches 5 is closed in a pressure-tight manner. The first side cover 7 and the second side cover 8 are coupled to the stator 2 by coupling elements 9, for example, screws.

  A vane groove 10 extending in the axial direction is formed on the outer peripheral surface of the rotor 3. In this case, one vane 11 extending in the radial direction is arranged in each vane groove 10. In each notch 5, one vane 11 extends and extends. In this case, the vane 11 is in contact with the stator 2 in the radial direction and in contact with the side covers 7 and 8 in the axial direction. Yes. Each vane 11 divides the notch 5 into two pressure chambers 12 and 13 that interact with each other. In order to guarantee the pressure-tight contact of the vane 11 with the stator 2, a leaf spring element 15 is provided between the groove bottom 14 of the vane groove 10 and the vane 11. Is loaded with a predetermined force in the radial direction.

  The first pressure medium line 16 and the second pressure medium line 17 connect the first pressure chamber 12 and the second pressure chamber 13 via a control valve (not shown) to a pressure medium pump (also shown in the figure). Not) or a tank (also not shown). As a result, an actuating drive device that allows the stator 2 to rotate relative to the rotor 3 is formed. In this case, all the first pressure chambers 12 are connected to the pressure medium pump and all the second pressure chambers 13 are connected to the tank, or the reverse connection, that is, all the first pressure chambers 12 are connected. Is connected to the tank, and all the second pressure chambers 13 are connected to the pressure medium pump. When the first pressure chamber 12 is connected to the pressure medium pump and the second pressure chamber 13 is connected to the tank, the first pressure chamber 12 expands at the expense of the second pressure chamber 13. As a result, the vane 11 is moved in the circumferential direction, that is, in the direction indicated by the first arrow 21. The rotor 3 is rotated relative to the stator 2 by the movement of the vane 11.

  In the illustrated embodiment, the stator 2 is driven from the crankshaft by a chain drive (not shown) acting on the input wheel 4. It is also conceivable that the stator 2 is driven by a belt transmission or a gear transmission. The rotor 3 is connected to a camshaft (not shown) in a frictional connection, a shape connection (fitting based on engagement) or a material connection, for example by press fitting or screw connection using a center screw. Based on the relative rotation of the rotor 3 relative to the stator 2, that is, based on the introduction or derivation of the pressure medium with respect to the pressure chambers 12, 13, a phase shift occurs between the camshaft and the crankshaft. Therefore, the control time of the gas exchange valve of the internal combustion engine can be intentionally changed by intentionally introducing or deriving the pressure medium to or from the pressure chambers 12 and 13.

  In the illustrated embodiment, the pressure medium lines 16 and 17 are formed as holes arranged in a substantially radial direction. This hole extends from the center hole 22 provided in the rotor 3 to the outer peripheral surface of the rotor 3. A center valve (not shown) may be disposed inside the center hole 22, and the pressure chambers 12 and 13 can be intentionally connected to a pressure medium pump or a tank via the center valve. Further, a pressure medium distributor can be arranged inside the center hole 22. In this case, the pressure medium distributor connects the pressure medium pipes 16 and 17 to the connection portion of the control valve provided outside via the pressure medium passage and the annular groove.

  The side wall 6 extending substantially in the radial direction of the notch 5 is provided with a work forming portion 23 that protrudes into the notch 5 in the circumferential direction. This work forming portion 23 serves as a stopper for the vane 11. Even if the rotor 3 takes the extreme positions relative to the stator 2, that is, even when the vane 11 is in contact with one of the side walls 6, the processed molding portion 23 is a pressure chamber. 12 and 13 are guaranteed to be supplied with pressure medium.

  For example, when an insufficient pressure medium is supplied to the device 1 at the start stage of the internal combustion engine, the rotor 3 is controlled relative to the stator 2 based on the alternating / strain torque applied to the rotor 3 by the camshaft. Without being exercised. In the first stage, the drag torque of the camshaft presses the rotor 3 relative to the stator 2 in the circumferential direction opposite to the rotational direction of the stator, and in this case, the rotor 3 contacts the side wall 6. Until pressed. Subsequently, the reciprocating oscillation of the rotor 3 is caused by the alternating torque applied to the rotor 3 by the camshaft until at least one of the pressure chambers 12 and 13 is completely filled with the pressure medium. A reciprocating swing of the vane 11 in the notch 5 is generated. This leads to increased wear and noise generation in the apparatus 1. In order to avoid this, the device 1 is provided with two locking elements 24. Each locking element 24 has a pot-shaped piston 26, which is arranged in an axial hole 25 provided in the rotor 3. The piston 26 is loaded with a spring force in the axial direction by a spring 27. The spring 27 is supported by the ventilation element 28 on one side in the axial direction, and the axial end of the spring 27 opposite to the ventilation element 28 is disposed in a piston 26 formed in a pot shape. Yes.

  The first side cover 7 is formed with one slide guide portion (Kulisse) 29 per lock element. In this case, the rotor 3 is relatively to the stator 2 at the start of the internal combustion engine. It can be locked in a position corresponding to the position. In this position, the piston 26 is pressed against the slide guide portion 29 by the spring 27 when insufficient pressure medium is supplied to the device 1. Furthermore, means are provided for pushing the piston 26 back into the axial hole 25 and thus releasing the lock when the pressure medium supply to the device 1 is sufficient. This is normally performed by a pressure medium introduced into a notch 30 formed in the end face on the cover side of the piston 26 via a pressure medium pipe (not shown). When the phase position ψ corresponding to the start position of the internal combustion engine corresponds to the center position of the vane 11 between the side walls 6, the two lock elements 24 and the corresponding corresponding slide guide portions 29 are used. This makes it possible to lock the hydraulic actuator 1a at this position.

  In order to allow leakage oil to be led out from the spring chamber of the axial hole 25, the ventilation element 28 is provided with grooves extending in the axial direction, and the pressure medium is supplied to the second side cover 8 along these grooves. It can guide to the provided hole.

  FIG. 8 shows a device 101 for changing the control time of a gas exchange valve of an internal combustion engine according to the known prior art. The apparatus 101 includes a hydraulic actuator 102 and a control valve 103.

  The actuating device 102 has a pressure chamber 104 which is divided by a movable element 105 into two interacting pressure chambers 106, 107. The movable element 105 is coupled to the camshaft or crankshaft in a non-rotatable manner, and another component is coupled to the pressure chamber 104 in a relatively non-rotatable manner. The movable element 105 is coupled to the two slide guide portions 108 and 109 so as not to move relative to each other. Further, one lock pin is indicated by reference numerals 110 and 111, respectively. These lock pins 110 and 111 are provided at fixed positions with respect to the pressure chamber 104. Each slide guide part 108, 109 corresponds to one lock pin 110, 111, respectively. Alternatively, the lock pins 110, 111 can be moved together with the movable element 105, and the slide guide portions 108, 109 are in a fixed position with respect to the pressure chamber 104. It may be formed.

  The control valve 103 includes an operation unit 112, a first spring element 113, and a valve body 114. The actuation unit 112 may be formed, for example, in the form of an electrical or hydraulic actuation unit 112. In the following, the case of using the electrical operation unit 112 formed as an electromagnet without limiting the generality will be described. The valve body 114 is formed with a first work connection portion A, a second work connection portion B, an inflow connection portion P, and an outflow connection portion T as ports. The first work connection A is connected to the first pressure chamber 106 via the first pressure medium line 115, and the second work connection B is connected to the second pressure via the second pressure medium line 116. Each is connected to the chamber 107. Furthermore, the outflow connection T is connected to the pressure medium reservoir 117. Via the pressure medium pump 118, the filter 119 and the check valve 120, the inflow connection P is loaded with a pressure medium, that is, the pressure medium is supplied to the inflow connection P. The first slide guide unit 108 is connected to the first pressure medium pipe line 115 via the third pressure medium pipe line 121. The second slide guide portion 109 is also connected to the second pressure medium conduit 116 via the fourth pressure medium conduit 122. The first slide guide portion 118 and the second slide guide portion 109 are each formed as one groove, and in this case, the dimension of the groove in the movement direction of the movable element 105 is the lock pin 110. 111, that is, the dimension in the moving direction of the movable element 105 is made larger. Both lock pins 110 and 111 are engaged in the slide guide portions 108 and 109 at the center position of the movable element 105 shown in the figure, and are arranged at one end of each groove in the movement direction of the movable element 105. Is arranged.

  By means of the actuation unit 112, the valve can be brought into the second control position 130, the third control position 131 and the fourth control position 132 against the spring force of the first spring element 113. When the valve is located at the second control position 130 (corresponding to when the operating unit 112 is low energized to non-energized), the second work connection B is connected only to the inflow connection P, The first work connection A is connected only to the outflow connection T.

  When the valve is located at the third control position 131 (corresponding to when the operation unit 112 is energized during low energization to medium energization), the first and second work connection portions A and B are also connected to the inflow connection portion P. It is not connected to the outflow connection T. In an alternative configuration, both work connections A, B may be connected only to the inflow connection P in order to compensate for leakage losses.

  When the valve is located at the fourth control position 132 (corresponding to the middle energization to the maximum energization of the operating unit 112), the first work connection A is connected only to the inflow connection P, The second work connection B is connected only to the outflow connection T.

  In order to achieve adjustment of the movable element 105 in the “slow” direction (indicated by the second arrow 126) in the controlled operation of the internal combustion engine, the control valve 103 is brought into the second control position 130. It is. The pressure medium is guided from the inflow connection P to the second pressure chamber 107 via the second work connection B and the second pressure medium line 116. At the same time, the pressure medium is also introduced into the second slide guide portion 109 via the fourth pressure medium pipe line 122. As a result, the second lock pin 111 is pushed out from the second slide guide portion 109 against the spring force of the second spring 129. At the same time, the first pressure chamber 106 is connected to the pressure medium reservoir 117 via the first pressure medium line 115 and the outflow connection T. Based on the outflow of the pressure medium from the first pressure chamber 106 and the inflow of the pressure medium into the second pressure chamber 107, the movable element 105 is moved in the “slow” direction. At the same time, the first slide guide portion 108 and the second slide guide portion 109 are also moved in the “late” direction. At this time, the first lock pin 110 moves inside the first slide guide portion 108, and the second lock pin 111 is located outside the second slide guide portion 109.

  In order to maintain the phase position ψ of the hydraulic actuator 102, the control valve 103 is brought to the third control position 131. Both work connections A and B are not connected to the inflow connection P or the outflow connection T. The pressure medium does not flow into or out of the pressure chambers 106 and 107, and the phase position ψ is kept constant. In order to achieve adjustment (indicated by the third arrow 128) of the movable element 105 in the “early” direction, the control valve 103 is brought into the fourth control position 132. The pressure medium is guided from the inflow connection P to the first pressure chamber 106 via the first work connection A and the first pressure medium line 115. At the same time, the pressure medium is also introduced into the first slide guide portion 108 via the third pressure medium conduit 121. Thereby, the first lock pin 110 is pushed out from the first slide guide portion 108 against the spring force of the first spring 127. At the same time, the second pressure chamber 107 is connected to the pressure medium reservoir 117 via the second pressure medium line 116 and the outflow connection T. Due to the outflow of the pressure medium from the second pressure chamber 107 and the inflow of the pressure medium into the first pressure chamber 106, the movable element 105 is moved in the “early” direction. At the same time, the first slide guide portion 108 and the second slide guide portion 109 are also moved in the “early” direction. At this time, the second lock pin 111 moves inside the second slide guide portion 109, and the first lock pin 110 is located outside the first slide guide portion 108.

  When the movable element 105 is adjusted beyond the center position shown in FIG. 8 beyond the center position, the lock pin 110; 111 not loaded with the pressure medium is connected to each slide guide portion. Snap into 108 and 109 and lock. At the same time, the other lock pin 111; 110 is loaded with a pressure medium. In this case, the lock pin 111; 110 is located outside the corresponding slide guide portion 109; This movement is limited only by the snap-in lock pins 110,111.

  When the hydraulic actuator 102 is located at the center position shown in FIG. 8 and sufficient pressure medium is not supplied to the device 101 (for example, when the internal combustion engine is started), both lock pins 110 are used. 111 are snapped into the slide guides 108 and 109 and locked. At this time, the lock pins 110 and 111 are arranged so that the lock pins 110 and 111 are positioned at the ends of the slide guide portions 108 and 109 which are arranged with the largest mutual distance. The guide portions 108 and 109 are also formed so that the lock pins 110 and 111 are located at the ends of the slide guide portions 108 and 109 that are arranged with the largest mutual distance. Thereby, the movable element 105 is fixed in position relative to the pressure chamber 104. Alternatively, the lock pins 110 and 111 may be located at the end portions of the slide guide portions 108 and 109 that are closest to each other. In this alternative configuration, the first slide guide portion 108 is loaded with the pressure medium through the second pressure medium conduit 116 and the second slide guide portion 109 is loaded with the pressure medium through the first pressure medium conduit 115, respectively. There must be. Similarly, it is conceivable that the slide guide portions 108 and 109 are loaded through the pressure chambers 106 and 107, for example, by worm grooves.

  In the stop process of the internal combustion engine, there is a possibility that the movable element 105 is positioned relatively late with respect to the center position. When the internal combustion engine is restarted, the device 101 is not yet sufficiently filled with the pressure medium. Based on the camshaft drag torque, the movable element 105 is driven in the direction of the retard stopper 133 and abuts against the retard stopper 133. This leads to increased component wear and unpleasant noise generation.

  When the operation unit 112 of the control valve 103 fails, the current supply is interrupted, for example, due to an electromagnet failure or a current connection path failure, so that the control valve 103 is shifted to the second control position 130. As a result, the second lock pin 111 is unlocked, and the camshaft is adjusted in the “slower” direction relative to the crankshaft. As a result, the start / running characteristics of the internal combustion engine which are optimum at the center position shown in FIG. 8 are deteriorated.

  The hydraulic actuator 102 shown schematically may be, for example, an axial piston regulator or a rotary piston regulator. In the following, only the embodiment of the rotary piston regulator will be taken up and described without limiting its generality. The pressure chamber 104 corresponds to the notch 5 shown in FIG. The movable element 105 corresponds to the vane 11. In the embodiment shown in FIG. 1, the lock pins 110, 111 are components of either the side cover of the rotary piston adjuster or the rotor of the rotary piston adjuster, and are located in the bore, preferably the blind hole. It may be arranged. Each slide guide part 108 and 109 is formed in the other component part, respectively.

  In FIG. 4, a device 101 according to the invention is schematically illustrated as in FIG. This device 101 is for the most part identical to the device shown in FIG. 8, and therefore the same reference numerals are used for the same components. The difference of the device 101 according to the invention is that the control valve 103 additionally has a first control position 140. The first control position 140 is made effective when the operation unit 112 takes a state corresponding to low energization to no energization. The first spring element 113 serves in this case so that the first control position 140 is achieved. At this position, neither the first work connection portion A nor the second work connection portion B is connected to the inflow connection portion P. Depending on the arrangement of the hydraulic actuator 102, either the first work connection A or the second work connection B can be connected to the outflow connection T. On the other hand, the other work connection B; A does not communicate with the outflow connection T. Further, at the first control position 140, the first work connection portion A and the second work connection portion B do not communicate with the inflow connection portion P or the outflow connection portion T, or both work connection portions A, A configuration in which B is connected only to the outflow connection T is also conceivable.

  In addition to the first control position 140, the control valve 103 has the second control position 130, the third control position 131, and the fourth control position 132 shown in FIG. In this case, the second control position 130 is taken when the operating unit 112 is low-powered to medium-powered, the third control position 131 is taken when the working unit 112 is medium-powered to high-powered, and the fourth control position 132 is It is taken when the operation unit 112 is highly energized to maximum energized.

  When the operating unit 112 fails or when the current supply to the operating unit 112 is interrupted, the control valve 103 automatically switches to the first control position 140. In this case, the control valve 103 holds this position until the repair of the operation unit 112 or the repair of the current supply unit to the operation unit 112 is completed. After the internal combustion engine is restarted, the movable element 105 is movable when the internal combustion engine is shut off based on the drag torque and the alternating torque based on insufficient pressure medium supply to the hydraulic actuator 102. Regardless of the position of the element 105, it is moved to the center position in the middle. At the center position in the middle, both lock pins 110 and 111 can be engaged and locked in the slide guide portions 108 and 109. As a result, the position of the movable element 105 in the pressure chamber 104 is fixed. Based on the arrangement of the first control position 140, the pressure medium is not guided to the pressure chambers 106 and 107 during operation of the internal combustion engine, and consequently the pressure medium is not guided to the slide guide portions 108 and 109. As a result, the movable element 105 is held in a fixed position relative to the pressure chamber 104. As a result, the phase position ψ between the camshaft and the crankshaft is kept constant at the emergency travel position. At such an emergency running position, the internal combustion engine has a good start / running characteristic.

  5a to 5d exemplarily illustrate the valve body 114 of the control valve 103 of the device 101 according to the present invention. The valve body 114 includes a valve housing 141 and a control piston 142. The valve housing 141 is formed in a substantially hollow cylindrical shape. In this case, three annular grooves 143, 144, and 145 are formed on the outer peripheral surface of the valve housing 141 at intervals in the axial direction. Yes. Each of these annular grooves 143, 144, 145 forms a connecting portion that is a port of the valve. In this case, both the outer annular grooves 143 and 145 in the axial direction form work connection portions A and B, and the middle annular groove 144 forms an inflow connection portion P. The outflow connection portion T is formed by an opening provided on one end surface of the valve housing 141. The annular grooves 143, 144, 145 are each connected to the interior of the valve housing 141 via a first radial opening 146. Inside the valve housing 141, a control piston 142 formed in a substantially hollow cylindrical shape is disposed so as to be axially movable. One end face of the control piston 142 is loaded with a force by the second spring element 147, and the other end face on the opposite side is loaded with a force by a push rod 148 provided in the operating unit 112. By energizing the operating unit 112, the control piston 142 can be moved to an arbitrary position between the first end stopper 149 and the second end stopper 150 against the spring force of the second spring element 147. .

  The control piston 142 includes a first annular web 151 and a second annular web 152. The outer diameters of both annular webs 151 and 152 are adapted to the inner diameter of the valve housing 141. Further, a second radial opening 146 a is formed in the control piston 142 between the end portion on the end face side on which the push rod 148 acts and the second annular web 152. Thereby, the inside of the control piston 142 is connected to the inside of the valve housing 141. The first annular web 151 and the second annular web 152 are associated with the position of the control piston 142 relative to the valve housing 141 with the first to fourth control edges 153, 154, 155, 156. Open or cut off the connection between the inflow connection P and the work connection A, B and open or cut off the connection between the work connection A, B and the outflow connection T And is arranged on the outer peripheral surface of the control piston 142. The outer diameter of the control piston 142 is larger than the inner diameter of the valve housing 141 in the range between the push rod 148 and the second annular web 152 and in the range between the first annular web 151 and the second annular web 152. Is also formed small. As a result, a fourth annular groove 157 is formed between the first annular web 151 and the second annular web 152. A third annular web 158 is formed inside the fourth annular groove 157. The outer diameter of the third annular web 158 is adapted to the inner diameter of the valve housing 141. Furthermore, the third annular web 158 is such that the third annular web 158 blocks the connection between the inflow connection P and the second work connection B at the first control position 140 of the control valve 103. It is positioned.

In FIG. 5a, a first control position 140 of the control valve 103 is shown. In the first control position 140, the control piston 142 is loaded with a force between the small force F ₁ and minimum force through the push rod 148 by the actuation unit 112. The end surface on the push rod side of the control piston 142 is located in a range between the first terminal stopper 149 (movement distance = 0 mm) and a predetermined movement distance s ₁ . The connection between the inflow connection P and the second work connection B is interrupted by the third annular web 158, and the connection between the inflow connection P and the first work connection A is the first. Are interrupted by the annular web 151. Furthermore, the connection between the second work connection B and the outflow connection T is interrupted by the second annular web 152, whereas the pressure medium passes from the first work connection A to the outflow connection T. Can flow to. Since the pressure medium flow to both lock pins 110, 111 and both pressure chambers 106, 107 is blocked, active adjustment cannot be made at the first control position 140. Due to the connection between the first pressure chamber 106 and the pressure medium reservoir 117, the first pressure chamber 106 is exhausted. In relation to the position of the hydraulic actuator 102, the movable element 105 is immediately or after a certain amount of time required to empty the second pressure chamber 107 due to leakage. Based on camshaft dragging or alternating torque, it is driven to the center position and is permanently locked to this center position. This control position corresponds to the arrangement configuration of the control valve 103 when the operation unit 112 is not energized, that is, the arrangement configuration in which the control piston 142 is moved to the first terminal stopper 149 by the second spring element 147. That is, it corresponds to an arrangement configuration in which the movement distance is zero. This position is taken by the control valve 103 when the operating unit 112 has failed or the current supply to the operating unit 112 is interrupted.

In FIG. 5b, the second control position 130 of the control valve 103 is shown. In the second control position 103, the control piston 142 is loaded with a force between the small force _{F 1} and the intermediate force _{F 2} through the push rod 148 by the actuation unit 112, in this _case, F 2> _{F 1} It is. As a result, the control piston 142 is moved from the first end stopper 149 on the push rod side by the moving distances S _{1 to} S ₂ . In this case, S ₂ > S ₁ . The first annular web 151 further interrupts the connection between the first work connection A and the inflow connection P and the pressure medium can continue to flow from the first work connection A to the outflow connection T. . Furthermore, the second annular web 152 breaks the connection between the second working connection B and the outflow connection T, whereas the second annular web 152 and the third annular web 158 are inflow connections. The connection between the part P and the second work connection part B is released. In this position, the pressure medium is supplied to the second pressure medium line 116 and the fourth pressure medium line 122 of the second pressure chamber 107 and the second slide guide part 109 via the second work connection part B. Supplied. As a result, the second lock pin 111 is unlocked and the hydraulic actuator 102 is adjusted in the “late” direction. At the same time, the pressure medium flows from the first pressure chamber 106 via the first pressure medium line 115 to the first work connection A and from this first work connection A to the outflow connection T. .

In FIG. 5c, a third control position 131 of the control valve 103 is shown. In the third control position 131, the control piston 142 is loaded with a force between the intermediate force _{F 2} with a large force _{F 3} through the push rod 148 by the actuation unit 112, in this _case, F 3> _{F 2} It is. Accordingly, the control piston 142 is moved from the first end stopper 149 on the push rod side by the moving distances S _{2 to} S ₃ , and in this case, S ₃ > S ₂ . In this position of the switching valve, the first tubular web 151 and the second annular web 152 are connected between the work connections A, B and the inflow connection P and the work connections A, B and the outflow connection T. Block the connection between In this position of the control valve 103, no pressure medium can be supplied to the pressure chambers 106, 107 and no pressure medium can flow out of the pressure chambers 106, 107. That is, this control position corresponds to a holding position where the phase position ψ between the camshaft and the crankshaft is held.

In FIG. 5d, a fourth control position 132 of the control valve 103 is shown. In the fourth control position 132, the control piston 142 is loaded with a force between the large force _{F 3} and a maximum force _{F 4} through the push rod 148 by the actuation unit 112, in this _case, F 4> _{F 3} It is. As a result, the control piston 142 is moved from the first end stopper 149 on the push rod side by the moving distances S _{3 to} S ₄ , and in this case, S ₄ > S ₃ . In this arrangement, the first annular web 151 interrupts the connection between the first work connection A and the outflow connection T, while the inflow connection P and the first work connection A are connected to each other. The connection between them is opened by both the first annular web 151 and the third annular web 158. Furthermore, the connection between the inflow connection P and the second work connection B is interrupted by the second annular web 152, whereas the pressure medium is connected to the second work connection B and the second radial opening. 146a can flow into the control piston 142 and from the control piston 142 into the outflow connection T. In this position of the control valve 103, pressure medium is guided from the second pressure chamber 107 via the second pressure medium line 116 to the second work connection B and from this second work connection B. Guided to outflow connection T. At the same time, the pressure medium passes through the first work connection part A, the first pressure medium pipe line 115, and the third pressure medium pipe line 121, and the first pressure chamber 106 and the first slide guide part. 108. As a result, the first lock pin 110 is unlocked and the hydraulic actuator 102 is adjusted in the “early” direction.

  By using the four-port four-position valve as the control valve 103 of the device 101 according to the invention, an additional device is formed to form a device 101 having a center position locking mechanism that automatically starts at the locked center position. Modules such as additional control valves are not required. In this case, the element 105 (vane in the case of a vane type regulator) does not contact the stopper. Neither the configuration space nor the manufacturing or assembly costs are increased compared to the configurations described in the known prior art. At the same time, the device 101 is brought to the center position when the working unit 112 fails and is locked to this center position until the working unit 112 is repaired.

FIG. 6 is a diagram showing the relationship between the volume flow rate from the inflow connection P to the pressure chambers 106 and 107 and the on / off ratio (TV ) of the operating unit 112. The actuation unit 112 can be loaded with a predetermined voltage. In this case, zero volts or a maximum value is applied. The on / off ratio represents the percentage of time that the maximum value of voltage is applied to the actuation unit 112. The higher the on / off ratio, the greater the force applied by the actuation unit 112 to the control piston 142 via the push rod 148. Thus, the on / off ratio is a measure of the amount of movement of the control piston 142 within the valve housing 141 relative to the first end stopper 149.

  In a first range where the on / off ratio is between zero and the first value TV1, the control valve 103 takes the first control position 140. In the first control position 140, the connection between the inflow connection portion P and the work connection portions A and B is cut off, and the volumetric flow is 0 except for the leakage flow rate.

  When the on / off ratio is between the first value TV1 and the second value TV2, the control valve 103 is located in the second control position 130. The pressure medium can flow from the inflow connection P to the second work connection B, whereas the connection between the inflow connection P and the first work connection A is interrupted. The volumetric flow gradually increases as the on / off ratio increases from the first value TV1 to the third value TV3, and gradually decreases while the on / off ratio continues to increase to the second value TV2. Eventually, it becomes almost zero at the second value TV2. Advantageously, only a range between the third value TV3 and the second value TV2 is used for the second control position 130.

In the third range between the second value TV2 and the fourth value TV4, the volume flow rate is substantially zero. The on / off ratio located in the third range is hereinafter referred to as “holding on / off ratio TV _Halte ”. This third range corresponds to the third control position 131 of the control valve 103, and in this third control position 131, both work connection portions A and B are not connected to the inflow connection portion P.

  When the value of the on / off ratio continues to be increased to 100% starting from the value TV4, the volumetric flow rate from the inflow connection P to the pressure chambers 106 and 107 gradually increases for the time being. The volumetric flow rate can be increased continuously to an on / off ratio of 100%, or it can be structurally limited to pass a predetermined maximum. This range corresponds to the fourth control position 132 of the control valve 103. In this fourth control position 132, the pressure medium is guided from the inflow connection P to the first work connection A, whereas the connection between the inflow connection P and the second work connection B is interrupted. Has been.

  In addition to the advantage that when the internal combustion engine is restarted when the operating unit 112 has failed, the hydraulic actuator 102 is locked in the center position and this lock is maintained, the device 101 according to the invention comprises: If the operating unit 112 has not failed, it is possible to lock the hydraulic actuator 102 in the center position when the internal combustion engine is shut off, or hydraulically when the internal combustion engine is restarted. Allows the hydraulic actuator 102 to be positioned such that the hydraulic actuator 102 is brought to and locked in the center position. This has the following advantages. That is, during the start-up process when the device 101 is not yet sufficiently filled with pressure medium, the hydraulic actuator 102 is securely locked in the center position and is thereby movable relative to the side wall of the pressure chamber 104. The contact of the element 105 is avoided, thereby avoiding increased wear and noise generation.

For the operation of the internal combustion engine, various on / off ratios, in particular TV1 to TV3 and the holding on / off ratio TV _Halte, must be known to the engine controller. The retention on / off ratio is determined by the engine controller according to the standard and is filed in the storage unit. Two means are conceivable for obtaining TV1, TV2 and TV3. Through the structural design and the resulting valve characteristics, TV1, TV2 and TV3 can be determined directly in relation to the holding on / off ratio TV _Halte . The difference angles Y1, Y2, Y3 are always filed in the storage unit. The engine controller determines the holding on / off ratio TV _Halte at an early stage of operation of the internal combustion engine. In that case, the following can be said for TV1, TV2 and TV3:
TV1 = TV _Halte -Y1
TV2 = TV _Halte- Y2
TV3 = TV _Halte- Y3
The second method is to have TV1 and TV2 determined by the engine controller and filed in a characteristic map, possibly after each restart. In order to determine TV1 and TV3, the camshaft angle signal and the crankshaft angle signal can be used. For this purpose, the relative phase position of both shafts and the temporal change of the phase position can be used, among others. For example, the following method can be used. The on / off ratio is ramped up from 0%. The value TV1 is achieved when the adjustment process starts (at this point one of the pressure chambers 106, 107 and the corresponding lock pin 110, 111 are loaded with pressure medium, and the hydraulic type Actuator 102 is adjusted, which can be detected via a camshaft angle sensor and a crankshaft angle sensor). The value TV3 is achieved when the maximum adjustment speed is exceeded. The value TV2 is achieved when the phase position is kept constant. The determined value is subsequently filed in memory.

  FIG. 7 shows a flowchart of a method for controlling the device 101 according to the invention during the stop process of the internal combustion engine. In this way, the hydraulic actuator 102 is brought into a position where the hydraulic actuator 102 is locked after the internal combustion engine is stopped, or the hydraulic actuator 102 is restarted after the internal combustion engine is restarted. It is located at a position serving as a starting point for moving 102 directly to the center position and locking to the center position.

At the introduction of the stop process of the internal combustion engine, the rotational speed n is n> 0. The phase position ψ between the camshaft and the crankshaft is brought to the stop phase position (Abstellphasenlage) by the control valve 103. This stop phase position _deviates from the lock phase position ψ _Mitte by a specified amount X. The stop phase position is shifted in the “early” direction relative to the lock phase position ψ _Mitte for the device 101 formed without a compensating spring. The same can be said for the device 101 equipped with a compensation spring, but the torque of this compensation spring is smaller than the drag torque of the camshaft. In the device 101 having a compensation spring that applies a torque larger than the camshaft drag torque, the stop phase is shifted relative to the lock phase position ψ _{Mitte in the} “slower” direction. When the predefined stop phase position is achieved, the ignition device is shut off (ignition off), and the value of the on / off ratio is adjusted to ensure that this phase position ψ is maintained. That is, in the case of adjusting the stop phase position shifted in the “early” direction, the on / off ratio is between TV2 and 100%, and in the “late” direction relative to the lock phase position ψ _Mitte . In the case of the shifted stop phase position, the on / off ratio is between TV4 and TV3. This on / off ratio is maintained until the rotational speed sensor reports that the rotational speed is zero. Thereafter, the adjusted on / off ratio is held at a specified time Y, after which the operating unit 112 is finally held in a no-current state. Due to the holding time of time Y, the rotation speed sensor already reports the rotation speed n = 0, and the lock pins 110 and 111 are unlocked and movable based on the pressure fluctuation due to the alternating torque during the final rotation of the internal combustion engine. The element 105 is prevented from being moved to an incorrect position beyond the center position. The hydraulic actuator 102 is located in a locked state based on the last rotation of the crankshaft, or is activated at the start of the internal combustion engine by the camshaft drag torque or by the compensation spring torque. The hydraulic actuator 102 is automatically and immediately positioned at the starting point when driven to the locked position.

FIG. 3 shows a flow chart of a method for starting an internal combustion engine using the device 101 according to the invention. This method ensures that the already existing lock of the movable element 105 or the lock formed during the first rotation of the crankshaft is retained. In this case, this lock is held until the oil pressure inside the internal combustion engine increases to a value required for reliable operation of the device 101. At the start of the start process, the speed n and the on / off ratio are equal to zero. As long as the rotational speed sensor reports the rotational speed n = zero, the on / off ratio is maintained between zero% and the value TV1. When the rotation speed sensor notifies that the rotation speed n> zero, the value of the oil pressure sensor is read. As long as the value of the oil pressure p is smaller than the specified minimum value p _min required to operate the device 101 according to the invention reliably, the value of the on / off ratio is kept between zero% and the value TV1. The When the oil pressure p exceeds the specified pressure, the device 101 moves to a controlled operation and the on / off ratio is adjusted between TV3 and 100% depending on the load condition of the internal combustion engine.

  The examples given above are only given as examples. Of course, the work connections A and B can be interchanged. The device 101 having the center position locking mechanism of the hydraulic actuator 102 is also within the frame of the present invention. In this case, only one lock pin can be engaged in one slide guide or stepped slide guide. Devices having any lock phase position with one or more lock pins are also within the scope of the present invention. With regard to volume flow and connections between the various connections of the switching valve, pressure losses due to leakage are ignored.

It is a longitudinal cross-sectional view of a hydraulic actuator. It is a cross-sectional view of the hydraulic actuator shown in FIG. 5 is a flow chart relating to a method for starting an internal combustion engine with a device according to the invention for changing the control time of a gas exchange valve. 1 is a schematic view of a device according to the invention for changing the control time of a gas exchange valve of an internal combustion engine. It is a longitudinal cross-sectional view which shows the control valve of the apparatus by this invention for changing the control time of the gas exchange valve of an internal combustion engine in a 1st control position. FIG. 5b is a longitudinal sectional view showing the control valve shown in FIG. 5a in a second control position. FIG. 5b is a longitudinal sectional view showing the control valve shown in FIG. 5a in a third control position. FIG. 5b is a longitudinal sectional view showing the control valve shown in FIG. 5a in a fourth control position. FIG. 6 is a diagram showing the relationship between the volumetric flow rate from the inlet connection to the pressure chamber and the position of the control piston relative to the valve housing. 5 is a flow chart relating to a method for controlling and shutting off an internal combustion engine equipped with a device according to the invention for changing the control time of a gas exchange valve. It is the schematic which shows the apparatus for changing the control time of the gas exchange valve of the internal combustion engine by a well-known prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Apparatus 1a Hydraulic type actuator 2 Stator 3 Rotor 4 Input wheel 5 Notch 6 Side wall 7 1st side cover 8 2nd side cover 9 Connection element 10 Vane groove 11 Vane 12 1st pressure chamber 13 2nd Pressure chamber 14 groove bottom portion 15 leaf spring element 16 first pressure medium conduit 17 second pressure medium conduit 21 first arrow 22 center hole 23 machining section 24 lock element 25 axial hole 26 piston 27 spring 28 Ventilation element 29 Slide guide portion 30 Notch 101 Device 102 Hydraulic actuator 103 Control valve 104 Pressure chamber 105 Element 106 First pressure chamber 107 Second pressure chamber 108 First slide guide portion 109 Second slide Guide part 110 First lock 111 Second lock pin 112 Actuating unit 113 First spring element 114 Valve body 115 First pressure medium line 116 Second pressure medium line 117 Pressure medium reservoir 118 Pressure medium pump 119 Filter 120 Check valve 121 Third pressure medium conduit 122 Fourth pressure medium conduit 126 Second arrow 127 First spring 128 Third arrow 129 Second spring 130 Second control position 131 Third control position 132 Fourth Control position 133 retard stopper 140 first control position 141 valve housing 142 control piston 143 annular groove 144 annular groove 145 annular groove 146 first radial opening 146a second radial opening 147 second spring element 148 push Rod 149 First end stopper 150 Second end stopper 1 51 1st annular web 152 2nd annular web 153 1st control edge 154 2nd control edge 155 3rd control edge 156 4th control edge 157 4th annular groove 158 3rd annular web P inflow Connection part T Outflow connection part A 1st work connection part B 2nd work connection part ψ phase position ψ _mitte lock phase position X amount Y ₁ difference angle Y ₂ difference angle Y ₃ difference angle TV _Halte holding on / off ratio p _min oil Pressure

Claims (2)

An apparatus (101) for changing a control time of a gas exchange valve of an internal combustion engine during a stop process of the internal combustion engine,
A hydraulic actuating device (102) having first and second interacting pressure chambers (106, 107) is provided;
The supply or derivation of pressure medium to both pressure chambers (106, 107) allows the camshaft phase position (ψ) relative to the crankshaft to be maintained or deliberately changed. And
A control valve (103) comprising a first second work connection (A, B), one outflow connection (T) and one inflow connection (P) is provided; One work connection (A) is in communication with the first pressure chamber (106), the second work connection (B) is in communication with the second pressure chamber (107), and the outflow connection is (T) is in communication with the tank, and the outflow connection (P) is loaded with a pressure medium,
The control valve (103) is brought into four control positions (103, 131, 132, 140) by the actuating unit (112);
-In the first control position (140) of the control valve (103), neither the first work connection (A) nor the second work connection (B) is in communication with the inflow connection (P). ,
-In the second control position (130) of the control valve (103), the first work connection (A) communicates with the outflow connection (T) and the second work connection (B) is inflow connection. Part (P),
-In the third control position (131) of the control valve (103), the first work connection (A) and the second work connection (B) are also connected to the outflow connection (T). The first work connection part (A) and the second work connection part (B) are in communication only with the inflow connection part (P).
-In the fourth control position (132) of the control valve (103), the second work connection (B) communicates with the outflow connection (T) and the first work connection (A) is inflow connection. In a method for controlling a device (101) of the type in communication with a part (P),
The following method steps are performed in the order listed:
- achieving a defined stop phase position location of a hydraulic actuating device (102) by a predetermined amount X offset from the lock phase to the locked position and holds the stop phase position,
-Shut off the ignition device,
- Adjust the up speed sensor device informs the rotational speed n = 0, a second control position in order to hold the stop phase position location (130) or fourth control position (132),
-Detecting the rotational speed n via the rotational speed sensor device;
Holding the taken second or fourth control position (130, 132) at a pre-defined time;
-Put the operating unit (112) in a stopped state after the elapse of time;
A method for controlling a device for changing the control time of a gas exchange valve of an internal combustion engine, characterized in that An apparatus (101) for changing the control time of a gas exchange valve of an internal combustion engine,
A hydraulic actuating device (102) having first and second interacting pressure chambers (106, 107) is provided;
The supply or derivation of pressure medium to both pressure chambers (106, 107) allows the camshaft phase position (ψ) relative to the crankshaft to be maintained or deliberately changed. And
A control valve (103) comprising a first second work connection (A, B), one outflow connection (T) and one inflow connection (P) is provided; One work connection (A) is in communication with the first pressure chamber (106), the second work connection (B) is in communication with the second pressure chamber (107), and the outflow connection is (T) is in communication with the tank, and the outflow connection (P) is loaded with a pressure medium,
The control valve (103) is brought into four control positions (103, 131, 132, 140) by the actuating unit (112);
-In the first control position (140) of the control valve (103), neither the first work connection (A) nor the second work connection (B) is in communication with the inflow connection (P). ,
-In the second control position (130) of the control valve (103), the first work connection (A) communicates with the outflow connection (T) and the second work connection (B) is inflow connection. Part (P),
-In the third control position (131) of the control valve (103), the first work connection (A) and the second work connection (B) are also connected to the outflow connection (T). The first work connection part (A) and the second work connection part (B) are in communication only with the inflow connection part (P).
-In the fourth control position (132) of the control valve (103), the second work connection (B) communicates with the outflow connection (T) and the first work connection (A) is inflow connection. In a method for controlling a device (101) of the type in communication with a part (P),
The following method steps are carried out in the order given during the stop process of the internal combustion engine:
- achieving a defined stop phase position location of a hydraulic actuating device (102) by a predetermined amount X offset from the lock phase to the locked position and holds the stop phase position,
-Shut off the ignition device,
- Adjust the up speed sensor device informs the rotational speed n = 0, a second control position in order to hold the stop phase position location (130) or fourth control position (132),
-Detecting the rotational speed n via the rotational speed sensor device;
Holding the taken second or fourth control position (130, 132) at a pre-defined time;
-Put the operating unit (112) in a stopped state after the elapse of time;
And during the starting process of the internal combustion engine, the following method steps are carried out in the order given:
-Adjusting the first control position;
-Detecting the number of revolutions n in the crankshaft or camshaft;
If the rotational speed n> 0, detect the pressure medium pressure p;
If the pressure medium pressure p is greater than a predefined value, the control position is adjusted based on a characteristic map filed in the control unit;
A method for controlling a device for changing the control time of a gas exchange valve of an internal combustion engine, characterized in that

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