Patent Application
20100000479
The invention relates to a method for controlling a device for variably adjusting the control times of gas-exchange valves of an internal combustion engine according to the preamble of Claim 1, to a method for controlling a device for variably adjusting the control times of gas-exchange valves of an internal combustion engine according to the preamble of Claim 6, and to a device for variably adjusting the control times of gas-exchange valves of an internal combustion engine according to the preamble of Claim 11.
In modern internal combustion engines, devices for variably adjusting the control times of gas-exchange valves are used in order to vary the phase relationship between the crankshaft and the camshaft in a defined angular region between a maximum advanced position and a maximum retarded position. For this purpose, the device is integrated into a drive train by which torque is transferred from the crankshaft to the camshaft. This drive train can be realized, for example, as a belt, chain, or gear train.
The device comprises at least two rotors that can rotate opposite each other, wherein one rotor is drivingly connected to the crankshaft and the other rotor is locked in rotation with the camshaft. The device comprises at least one pressure space that is divided by a movable element into two pressure chambers acting against each other. The moving element is in active connection with at least one of the rotors. By supplying pressure medium to the pressure chambers or by withdrawing pressure medium from the chambers, the moving element is shifted within the pressure space, by which a selective rotation of the rotors relative to each other and thus the camshaft to the crankshaft is realized.
The supply of pressure medium to the pressure chambers or the withdrawal of pressure medium from the pressure chambers is controlled by a control unit, usually a hydraulic directional valve (control valve). The control unit is controlled, in turn, by a controller that determines and compares the actual and desired positions of the camshaft in the internal combustion engine. If there is a difference between the two positions, a signal is transmitted to the control unit that adapts the pressure medium flows to the pressure chambers to this signal.
In order to guarantee the function of the device, the pressure in the pressure medium circuit of the internal combustion engine must exceed a certain value. Because the pressure medium is usually provided by the oil pump of the internal combustion engine and the provided pressure thus increases in sync with the rpm's of the internal combustion engine, below a certain rpm number, the oil pressure is still too low to change or maintain the phase position of the rotors. This can be the case, for example, during the startup phase of the internal combustion engine or during idling phases.
During these phases, the device would execute uncontrolled oscillations, which leads to increased noise emissions, increased wear, non-smooth running, and increased raw emissions of the internal combustion engine. In order to be able to prevent this, mechanical locking devices are provided that couple the two rotors with each other locked in rotation during the critical operating phases of the internal combustion engine, wherein this coupling can be cancelled by applying pressure medium to the locking device. In this way, for the locking position it has proven advantageous to select a phase position of the camshaft relative to the crankshaft that lies between the maximum advanced position and the maximum retarded position.
Such a device is known, for example, from US 2003/0121486 A1. In this embodiment, the device has a rotary piston construction, wherein an external rotor is supported such that it can rotate on an internal rotor constructed as an impeller wheel. In addition, two rotational angle limiting devices are provided, wherein a first rotational angle limiting device allows, in the locked state, an adjustment of the internal rotor relative to the external rotor in an interval between a maximum retarded position and a defined middle position (locking position). The second rotational angle limiting device allows, in the locked state, a rotation of the internal rotor relative to the external rotor in an interval between the middle position and the maximum advanced position. If both rotational angle limiting devices are in the locked state, then the phase position of the internal rotor relative to the external rotor is limited to the middle position.
Each of the rotational angle limiting devices is made from a spring-loaded locking pin that is arranged in a receptacle of the external rotor. Each locking pin is loaded with a force by a spring in the direction of the internal rotor. On the internal rotor, a locking groove is formed that stands opposite the locking pins in certain operating positions of the devices. In these operating positions, the pins can engage in the locking groove. In this way, each rotational angle limiting device transitions from the unlocked state into the locked state.
Each of the rotational angle limiting devices can transition from the locked state into the unlocked state by applying pressure medium to the locking groove. In this case, the pressure medium forces the locking pins back into their receptacles, whereby the mechanical coupling of the internal rotor to the external rotor is cancelled.
Applying pressure medium to the pressure chambers and the locking groove is realized by a control valve, wherein on the control valve there are, among other things, two work ports that communicate with the pressure chambers and one control port that communicates with the locking groove. The fact that both rotational angle limiting devices are changed from the locked state into the unlocked state by one and the same control line is a disadvantage in the shown embodiment. In this embodiment, during an adjustment process, both rotational angle limiting devices must be unlocked, that is, loaded with pressure medium, while pressure medium is alternately supplied to the pressure chambers and withdrawn from these pressure chambers. This leads to complicated control logic of the control valve. First, a plurality of control positions are required, wherein the switch points between the control positions must be constantly redefined during the operation of the internal combustion engine due to operating-dependent variations, for example, as a result of temperature changes. In addition, the setting of the individual control states requires a higher precision of the controller system, because the flow supplied to the valve has to lie within tightly bounded flow value intervals due to the plurality of control positions. This produces a plurality of computational and data-processing operations, whereby high requirements are placed on the control electronics. In addition, the phase accuracy of the device suffers, because even small deviations in the control loop have the effect that an undesired control state is set.
In addition, in this embodiment it is provided, during the startup phase of the internal combustion engine, to connect all of the pressure chambers and the locking groove to a tank, which leads to an inadequate supply of lubricant to the device and thus to increased wear.
Alternatively, pressure medium provided in another embodiment is to be supplied to one of the chambers and thus a sufficient lubricant supply is to be guaranteed. However, in this embodiment the internal rotor is clamped hydraulically opposite the external rotor. This can lead to jamming of the locking pins at the edges of the locking groove, by which hydraulic unlocking is made more difficult or optionally even prevented.
The invention is based on the objective of creating a device for the variable adjustment of the control times of gas-exchange valves of an internal combustion engine and specifying a method for controlling this device, wherein the internal rotor can be locked mechanically relative to the external rotor in a middle phase position between the maximum advanced position and the maximum retarded position. In this way, a secure locking shall be guaranteed when the internal combustion engine is stopped or at least during its startup process, undesired automatic unlocking during the startup phase of the internal combustion engine can be avoided, the device is supplied with sufficient lubricant at all times, and a secure adjustment past the locking position can be guaranteed, wherein the individual control states of the control valve shall be easy to determine and maintain.
In one embodiment of a device for variably adjusting the control times of gas-exchange valves of an internal combustion engine with an external rotor and an internal rotor that can rotate relative to this external rotor, wherein one of the components is drivingly connected to a crankshaft and the other component is drivingly connected to a camshaft, wherein at least one pressure space is formed and each pressure space is divided into two pressure chambers acting against each other, wherein one of the pressure chambers of each pressure space acts as an advancing chamber and the other pressure chamber acts as a retarding chamber, wherein by supplying pressure medium to the advancing chambers while simultaneously withdrawing pressure medium from the retarding chambers, the rotor interacting with the camshaft is rotated relative to the rotor interacting with the crankshaft in the direction of a maximum advanced position, wherein by supplying pressure medium to the retarding chambers while simultaneously withdrawing pressure medium from the advancing chambers, the rotor interacting with the camshaft is rotated relative to the rotor interacting with the crankshaft in the direction of a maximum retarded position, wherein at least one first and one second rotational angle limiting device are provided, wherein each rotational angle limiting device can assume an unlocked state and a locked state, wherein the locking state can be set by supplying pressure medium to or withdrawing pressure medium from the respective rotational angle limiting device, wherein for a locked first and second rotational angle limiting device the internal rotor is fixed relative to the external rotor in a locking position, wherein a control valve is provided that can assume several control positions and controls the supply of pressure medium to or the withdrawal of pressure medium from the pressure chambers and the rotational angle limiting devices, wherein the control valve has at least one inflow port, at least one outflow port, at least two work ports, and at least one separate control port, wherein the inflow port communicates with a pressure medium pump, the outflow port communicates with a tank, the first work port communicates with the advancing chambers, the second work port communicates with the retarding chambers, and the control port communicates with at least one of the rotational angle limiting devices, the objective is met according to the invention in that the control valve has a startup position in which one of the work ports is connected neither to the outflow port nor to the inflow port and that the other work port and the rotational angle limiting devices communicate exclusively with the outflow port in the startup phase.
In one embodiment there is an actuator that can move the control valve into various control position, wherein the control valve assumes the startup position for a non-activated or alternatively for a maximum activated actuator.
In this way, it can be provided that, in the locked state, the first rotational angle limiting device prevents the rotation of the rotor interacting with the camshaft relative to the rotor interacting with the crankshaft in the direction of the maximum advanced position when the locking position is assumed.
In addition it can be provided that, in the locked state, the first rotational angle limiting device limits the phase position of the rotor interacting with the camshaft relative to the rotor interacting with the crankshaft to an angle region between the maximum retarded position and the locking position.
In one alternative embodiment, in the locked state, the second rotational angle limiting device limits a phase position of the rotor interacting with the camshaft relative to the rotor interacting with the crankshaft to an angle region between the maximum advanced position and the locking position.
Advantageously, the second rotational angle limiting device communicates exclusively with the control port.
In one advantageous refinement of the invention it is provided that the control valve also has an unlocking position in which the control port communicates with the inflow port and the work ports do not communicate with the inflow port.
In addition, it can be provided that the control valve also has a retarding position in which the first work port communicates with the tank and the second work port and the control port communicate with the inflow port.
In addition, the control valve can have an advancing position in which the first work port is connected to the inflow port and the second work port and the control port are connected to the tank.
In this way, with increasing or alternatively decreasing excitation of the actuator, the control positions are assumed in the sequence: startup positions—unlocking position—retarding position—advancing position.
In a first method for controlling a device for variably adjusting the control times of gas-exchange valves of an internal combustion engine with an external rotor and an internal rotor that can rotate relative to this external rotor, wherein one of the components is drivingly connected to a crankshaft and the other component is drivingly connected to a camshaft, wherein at least one pressure space is provided and each pressure space is divided into two pressure chambers acting against each other, wherein one of the pressure chambers of each pressure space acts as an advancing chamber and the other pressure chamber acts as a retarding chamber, wherein by supplying pressure medium to the advancing chambers while simultaneously withdrawing pressure medium from the retarding chambers, the rotor interacting with the camshaft is rotated relative to the rotor interacting with the crankshaft in the direction of a maximum advanced position, wherein by supplying pressure medium to the retarding chambers while simultaneously withdrawing pressure medium from the advancing chambers, the rotor interacting with the camshaft is rotated relative to the rotor interacting with the crankshaft in the direction of a maximum retarded position, wherein at least one first and one second rotational angle limiting device are provided, wherein each rotational angle limiting device can assume an unlocked and a locked state, wherein the locking state can be set by supplying pressure medium to or withdrawing pressure medium from the respective rotational angle limiting device, wherein for a locked first and second rotational angle limiting device, the internal rotor is fixed relative to the external rotor in a locking position, wherein the supply of pressure medium to or the withdrawal of pressure medium from the pressure chambers and the rotational angle limiting devices can be set by a connection to a pressure medium pump or to a tank, the objective according to the invention is met in that during a startup phase of the internal combustion engine, the retarding chambers or the advancing chambers are connected neither to the tank nor to the pressure medium pump and the other pressure chambers and the rotational angle limiting devices are connected to a tank.
In one embodiment of the invention, it can be provided that, in the locked state, the first rotational angle limiting device prevents the rotation of the rotor interacting with the camshaft relative to the rotor interacting with the crankshaft in the direction of the maximum advanced position when the locking position is assumed.
Alternatively, it can be provided that, in the locked state, the first rotational angle limiting device limits the phase position of the rotor interacting with the camshaft relative to the rotor interacting with the crankshaft to an angle region between the maximum retarded position and the locking position.
In this way, in the locked state, the second rotational angle limiting device limits a phase position of the rotor interacting with the camshaft relative to the rotor interacting with the crankshaft advantageously to an angle region between the maximum advanced position and the locking position.
In one embodiment of the invention, it is provided that during a stop process of the internal combustion engine, the advancing chambers are connected to the pressure medium pump and the second rotational angle limiting device and the retarding chambers are connected to the tank.
In another method for controlling a device for variably adjusting the control times of gas-exchange valves of an internal combustion engine with an external rotor and an internal rotor that can rotate relative to this external rotor, wherein one of the components is drivingly connected to a crankshaft and the other component is drivingly connected to a camshaft, wherein at least one pressure space is provided and each pressure space is divided into two pressure chambers acting against each other, wherein one of the pressure chambers of each pressure space acts as an advancing chamber and the other pressure chamber acts as a retarding chamber, wherein by supplying pressure medium to the advancing chambers while simultaneously withdrawing pressure medium from the retarding chambers, the rotor interacting with the camshaft is rotated relative to the rotor interacting with the crankshaft in the direction of a maximum advanced position, wherein by supplying pressure medium to the retarding chambers while simultaneously withdrawing pressure medium from the advancing chambers, the rotor interacting with the camshaft is rotated relative to the rotor interacting with the crankshaft in the direction of a maximum retarded position, wherein at least one first and one second rotational angle limiting device are provided, wherein each rotational angle limiting device can assume an unlocked and a locked state, wherein the locking state can be set by supplying pressure medium to or withdrawing pressure medium from the respective rotational angle limiting device, wherein for the locked first and second rotational angle limiting device, the internal rotor is fixed relative to the external rotor in a locking position, wherein the supply of pressure medium to or the withdrawal of pressure medium from the pressure chambers and the rotational angle limiting devices can be set by a connection to a pressure medium pump or to a tank, and wherein, in the locked state, the second rotational angle limiting device limits the phase position of the rotor interacting with the camshaft relative to the rotor interacting with the crankshaft to an angle region between the maximum advanced position and the locking position, the object according to the invention is met in that during a stopping process of the internal combustion engine, the advancing chambers are connected to the pressure medium pump and the second rotational angle limiting device and the retarding chambers are connected to the tank.
In this way, it can be advantageously provided in both methods that the locking state of the second rotational angle limiting device is controlled exclusively by a separate control line that does not communicate with the pressure chambers.
In this way, it can be advantageously provided that the locking state of the first rotational angle limiting device is controlled by the pressure prevailing in at least one of the advancing chambers.
Advantageously, a control valve is provided that controls the supply of pressure medium to and the withdrawal of pressure medium from both the pressure chambers and also the second rotational angle limiting device.
In one development of the invention it is provided that the connections of the pressure chambers and the second rotational angle limiting device to the pressure medium pump or to the tank during the stop process of the internal combustion engine are maintained for a defined time span past the completed engine stop.
In the embodiment of the device according to the invention, a locking device is provided by which the external rotor can be coupled mechanically with the internal rotor in a locking position between a maximum advanced position and a maximum retarded position. Advantageously, two rotational angle limiting devices can be provided, wherein, in the locked state, one of the rotational angle limiting devices limits the relative phase position of the internal rotor relative to the external rotor to a region between the maximum advanced position and the locking position. In the locked state, the other rotational angle limiting device permits a phase position between the locking position and the maximum retarded position. Alternatively, this can be constructed as a locking element, wherein, in the locking position, a locking pin of the locking element engages in a recess or a blind hole adapted to the locking pin. Thus it is guaranteed that the internal rotor can be fixed mechanically relative to the external rotor in a middle phase position.
Each of the rotational angle limiting devices can be changed from the locked state to the unlocked state by applying pressure medium. In this way, the rotational angle limiting device that limits the relative rotation of the internal rotor to the external rotor in the locked state to a region between the maximum advanced position and the locking position communicates with a control line. The control line communicates neither with the pressure chambers nor with the pressure medium lines and the pressure medium channels that supply the pressure chambers with pressure medium.
Thus, the locking state of this rotational angle limiting device can be influenced independent of the pressure state of the pressure chambers. Through the separate control of one of the rotational angle limiting devices by a control line, it is thus possible to stop the device during the shutdown process in a defined interval that contains the locking position. During the shutdown process or alternatively during the restart of the internal combustion engine, the internal rotor is led automatically into the locking position, wherein the mechanical connection between the rotors is created by the rotational angle limiting devices. The locking position can be achieved, for example, by the drag moment acting on the camshaft. In this case, the internal rotor is brought relative to the external rotor into an interval between the locking position and the maximum advanced position. Alternatively, a spring element can be provided that exerts a torque acting against the drag moment on the internal rotor. If the spring torque exceeds the drag moment, then the targeted interval extends between the maximum retarded position and the locking position.
Because the control line is constructed independent of the pressure medium lines supplying the device, during the startup phase both rotational angle limiting devices can be connected to the tank, wherein a group of pressure chambers are connected neither with the tank nor with the pump. Thus, automatic unlocking of the device can be stopped. Simultaneously, the leakage oil entering the pressure medium lines via the control valve can be suctioned through a small, oscillating movement of the internal rotor relative to the external rotor. Therefore a sufficient supply of lubricant to the device is guaranteed even during the startup phase. The small, oscillating movement of the internal rotor relative to the external rotor results from the alternating moments acting on the camshaft in combination with a small locking play of the rotational angle limiting devices.
Additional features of the invention emerge from the following description and from the drawings in which an embodiment of the invention is shown simplified. Shown are:
a is a cross-sectional view through an embodiment according to the invention of a device for changing the control times of gas-exchange valves of an internal combustion engine including an attached hydraulic circuit,
b is a longitudinal section view through the device from
c is a cross-sectional view through the device from
a-6g are longitudinal section views through the essential parts of the control valve from
In
a and 2b show an embodiment of a device 10 according to the invention in cross section and in longitudinal section, respectively.
The device 10 has an external rotor 22, an internal rotor 23, and two side covers 24, 25. The internal rotor 23 is constructed in the form of an impeller wheel and has an essentially cylindrical hub element 26 from whose outer cylindrical lateral surface extend five vanes 27 outwardly in the radial direction in the shown embodiment. In this way, the vanes 27 can be formed integrally with the hub element 26. Alternatively, the vanes 27, as shown in
Starting from an outer peripheral wall 29 of the external rotor 22, several projections 30 extend radially inwardly. In the shown embodiment, the projections 30 are formed integrally with the peripheral wall 29. Also conceivable, however, are embodiments in which instead of the projections 30 there are vanes that are attached to the peripheral wall 29 and extend radially inwardly. The external rotor 22 is supported on the internal rotor such that it can rotate relative to the internal rotor 23 by radially inwardly lying peripheral walls of the projections 30.
On an outer lateral surface of the peripheral wall 29 there is a chain wheel 21 by which torque can be transmitted from the crankshaft 2 to the external rotor 22 by a not-shown chain drive. The chain wheel 21 can be constructed as a separate component and locked in rotation with the external rotor 22 or can be constructed integrally with this internal rotor. Alternatively, a belt drive or gear drive can also be provided.
Each of the side covers 24, 25 is arranged on one of the axial side surfaces of the external rotor 22 and locked in rotation on this external rotor. In each of the projections 30 there is an axial opening 31 for this purpose, wherein each axial opening 31 is penetrated by an attachment element 32, for example, a bolt or a screw that is used for rotational fixing of the side covers 24, 25 on the external rotor 22.
Within the device 10, between every two projections 30 adjacent in the peripheral direction there is a pressure space 33 that is bounded in the peripheral direction by opposing, essentially radial boundary walls 34 of adjacent projections 30, in the axial direction by the side covers 24, 25, radially inwardly by the hub element 26, and radially outwardly by the peripheral wall 29. A vane 27 projects into each of the pressure spaces 33, wherein the vanes 27 are constructed such that these vanes contact both the side walls 24, 25 and also the peripheral wall 29. Each vane 27 thus divides the respective pressure space 33 into two pressure chambers 35, 36 acting against each other.
The external rotor 22 is arranged in a defined angular region so that it can rotate relative to the internal rotor 23. The angular region is bounded in one rotational direction of the external rotor 22 such that each vane 27 comes to lie against a boundary wall 34 of the pressure space 33 formed as an advance stop 34a. Analogously, the angular range in the other rotational direction is bounded such that each vane 27 comes to lie against the other boundary wall 34 of the pressure space 33 that acts as a retard stop 34b. Alternatively, a rotational angle limiting device can be provided that limits the rotational angle region of the external rotor 22 relative to the internal rotor 23.
By pressurizing one group of pressure chambers 35, 36 and depressurizing the other group, the phase position of the external rotor 22 relative to the internal rotor 23 can be varied. By pressurizing both groups of pressure chambers 35, 36, the phase position of the two rotors 22, 23 can be held constant relative to each other. Alternatively, it can be provided to pressurize none of the pressure chambers 35, 36 with pressure medium during phases of constant phase position. The lubricating oil of the internal combustion engine 1 is typically used as the hydraulic pressure medium.
For supplying pressure medium to or withdrawing pressure medium from the pressure chambers 35, 36, a pressure medium system is provided that comprises a not-shown pressure medium source, for example, a pressure medium pump, a similarly not-shown tank, a control valve 37, and several pressure medium lines 38a, 38b, 38p. Pressure medium fed from the pressure medium pump is supplied to the control valve 38 via the third pressure medium line 38p. According to the control state of the control valve 37, the third pressure medium line 38p is connected to the first pressure medium line 38a, the second pressure medium line 38b, or to both or none of the pressure medium lines 38a, 38b.
The internal rotor 23 is formed with two groups of pressure medium channels 39a, 39b, wherein each pressure medium channel 39a, 39b extends from an inner lateral surface of a receptacle 40 of the internal rotor 23 to one of the pressure chambers 35, 36. The first pressure medium line 38a communicates with the first pressure medium channels 39a. The second pressure medium line 38b communicates with the second pressure medium channels 39b. For this purpose, for example, a pressure medium distributor can be provided that is arranged in a receptacle 40. In one alternative embodiment, the control valve 37 is constructed as a central valve and is arranged in the receptacle 40, wherein, in this case, the control valve 37 connects the third pressure medium line 38p directly to the pressure medium channels 39a, 39b.
In order to shift the control times (opening and closing times) of the gas-exchange valves 9a, 9b in the advanced direction, the pressure medium supplied to the control valve 37 via the third pressure medium line 38p is led to the group of first pressure chambers 35 (advancing chambers) via the first pressure medium channels 39a and optionally the first pressure medium line 38a. Simultaneously, pressure medium is led out of the group of second pressure chambers 36 via the second pressure medium channels 39b and optionally the second pressure medium line 38b to the control valve 37 and is ejected into the tank. Therefore, the vanes 27 are shifted in the direction of the advance stop 34a, whereby a rotational movement of the internal rotor 23 relative to the external rotor 22 is achieved in the rotational direction of the device 10.
In order to shift the control times of the gas-exchange valves 9a, 9b in the retarded position, the pressure medium supplied to the control valve 37 via the third pressure medium line 38p is led via the second pressure medium channels 39b and optionally the second pressure medium line 38b to the group of second pressure chambers 36 (retarding chambers). Simultaneously, pressure medium is led out of the group of first pressure chambers 35 via the first pressure medium channels 39a and optionally the first pressure medium line 38a to the control valve 37 and is ejected into the tank. In this way, the vanes 27 are shifted in the direction of the retard stop 34a, whereby a rotational movement of the internal rotor 23 relative to the external rotor 22 is achieved against the rotational direction of the device 10.
In order to maintain the control times constant, the pressure medium supply to all of the pressure chambers 35, 36 is either stopped or permitted. Therefore, the vanes 27 are clamped hydraulically within each pressure space 33 and thus a rotational movement of the internal rotor 23 relative to the external rotor 22 is prevented.
During the startup of the internal combustion engine 1 or during idling phases, the pressure medium supply to the device 10 cannot be sufficient, in order to guarantee the hydraulic clamping of the vanes 27 within the pressure spaces 33. In order to prevent uncontrolled oscillation of the internal rotor 23 relative to the external rotor 22, there is a locking mechanism 41 that creates a mechanical connection between the two rotors 22, 23. For this, a locking pin is arranged in one of the rotors 22, 23, while a connecting passage is formed in the other rotor 22, 23. If the internal rotor 23 is located in a defined phase position (locking position) relative to the external rotor 22, then the locking pin can engage in the connecting passage and thus a mechanical, rotationally locked connection can be created between the two rotors 22, 23.
It has proven advantageous to select the locking position such that the vanes 27 in the locked state of the device 10 are located in a position between the advance stop 34a and the retard stop 34b. Such a locking mechanism 41 is shown in
Analogously, the connecting passage 45 of the second rotational angle limiting device 43 is designed such that for a locked section rotational angle limiting device 43, the phase position of the internal rotor 23 relative to the external rotor 22 is limited to a region between a maximum advanced position and the locking position.
In order to move the rotational angle limiting devices 42, 43 from the locked state into the unlocked state, it is provided that the respective connecting passage 45 is loaded with pressure medium. In this way, the respective locking pin 44 is forced back against the force of the spring element 46 into the borehole and thus the rotational angle limiting is cancelled.
In the shown embodiment, it is provided to supply the connecting passage 45 of the first rotational angle limiting device 42 with pressure medium via one of the first pressure chambers 35 and a connection line 47, wherein this first rotational angle limiting device prevents, in the locked state, the rotation of the internal rotor 23 relative to the external rotor 22 in the advanced direction at the locking position. The connecting passage 45 of the second rotational angle limiting device 43 can be loaded with pressure medium by the control line 48 and a channel 49. In this way it is provided that the control valve 37 regulates both the pressure medium flows to and from the first and second pressure chambers 35, 36 and also to and from the control line 48.
Such a control valve 37 is shown in
The intermediate sleeve 53 is arranged within the valve housing 52 fixed in position relative to this housing. On its outer lateral surface there is a work groove 56, a control groove 57, five work openings 56a-e, and three control openings 57a-c. The work groove 56 and the control groove 57 extend in the peripheral direction of the intermediate sleeve 53 each in a defined angle interval, wherein the two grooves 56, 57 are separated from each other hydraulically. The work ports A, B and the inflow port P are formed as radial openings in the valve housing 52, wherein the radial openings are formed exclusively in the region of the angular segment assumed by the work groove 56. Similarly, the control port S is realized by one or more radial openings that are formed exclusively in the region of the angular segment assumed by the control groove 57.
The work openings 56a-e communicate on one side with the interior of the intermediate sleeve 53 and on the other side with the first work port A (first work opening 56a), the inflow port P (second work opening 56b), the work groove 56 (third and fourth work opening 56c, d) or the radial tank port T (fifth work opening 56e). The work groove 56 also communicates with the second work port B. Furthermore, it can be provided to form additional grooves in the outer lateral surface of the intermediate sleeve 53 that connects the first, the second, or the fifth work opening 56a, b, e to the respective port A, P, T.
The control openings 57a-c communicate on one side with the interior of the intermediate sleeve 53 and on the other side with the control groove 57 that communicates, in turn, with the control port S.
The control piston 54 has an essentially hollow cylindrical construction and is arranged within the intermediate sleeve 53, wherein this piston can be moved by the actuator 50 against the force of a spring 55 in the axial direction relative to the intermediate sleeve 53 and the valve housing 52. The control piston 54 has three annular grooves 58a-c and first and second openings 59a, b.
The actuator 50 can be formed, for example, as an electrical actuator, wherein a magnetized armature is arranged within a coil. By exciting the coil, the armature can be shifted in the axial direction. This movement can be transmitted to the control piston 54 by a tappet rod 50a.
Through axial displacement of the control piston 54 within the intermediate sleeve 53, the work ports A, B and the control port S can be connected selectively to the inflow port P, the outflow port T, or none of the two.
In
In the startup position S1 (
When transitioning from the startup position S1 to an unlocked position S2 (
In the subsequent retarding position S3 (
In the first intermediate position S4 (
In the holding position S5 (
In the second intermediate position S6 (
In the subsequent advancing position S7 (
Here, the intermediate positions S4 and S6 are to be seen as optional control positions. An alternative control logic has only the control positions S1 to S3, S5, and S7.
During the startup phase of the internal combustion engine 1, the control valve 37 is located in the startup position S1. In this phase, the hydraulic clamping of the vanes 27 within the pressure spaces 33 is generally not guaranteed due to a system pressure that is too low. For this reason, the internal rotor 23 will carry out movements oscillating opposite the external rotor 22 in the peripheral direction. These oscillations are caused by the alternating moments acting on the camshafts 6, 7, wherein the oscillations themselves appear in the locked state of the device 10. In this way, their amplitude is defined by the locking play. The oscillations result in a pumping effect, whereby residual oil present in the pressure medium channels 39a, b or the pressure medium lines 38a, b can be fed into the pressure chambers 35, 36. In this way, pressure values that are sufficient to move the rotational angle limiting devices 42, 43 into the unlocked state can be achieved within the device 10.
Through the connection of the first work port A and the control port S to the tank, this is prevented. The first pressure chambers 35, the corresponding pressure medium channels 39a, the first pressure medium line 38a, and the control line 48 are emptied and thus a pressure buildup, and with it the undesired automatic unlocking during the startup phase, in the connecting passages 45 of the rotational angle limiting devices 42, 43 is prevented.
Because the second work port B is closed in the startup position S1, the second pressure chambers 36 are not charged with pressure medium. Therefore, it is prevented that the locking pin 44 of the second rotational angle limiting device 43 is forced against the end of the connecting passage 45, which could lead to jamming. On the other hand, it is prevented that the pressure medium in the second pressure medium channels 39b can flow to the tank. Thus, it is guaranteed that through the oscillations of the vanes 27, small quantities of pressure medium are fed into the second pressure chambers 36, whereby the device 10 is supplied with sufficient lubricant.
After a defined time span has elapsed after which the startup process has completely ended or when a sufficient pressure level is detected in the lubricant circuit of the internal combustion engine 1 and the motor controller forces a phase change, the device 10 transitions into a regulated state until the pressure in the lubricant circuit again falls below a given level. For this purpose, the actuator 50 of the control valve 37 is excited such that this valve is led via the unlocked position S2 into the control positions S3 to S7 and is regulated, according to the setting of the phase angle, by the motor controller into one of these control positions S3-S7.
While the control valve 37 assumes the unlocked position S2, in contrast to the startup position S1, the control port S is charged with pressure medium and thus the second rotational angle limiting device 43 transitions into the unlocked state. In this way, none of the pressure chambers 35, 36 are loaded with pressure, whereby jamming of the locking pin 44 of the second rotational angle limiting device 43 in its connecting passage 45 is prevented.
As a function of the current desired or actual values of the phase position, in the locked state of the device 10, the control valve 37 assumes the control positions S3-S7. If a displacement of the phase position in the direction of more retarded intake times is forced by the motor controller, then the control valve 37 is activated such that this assumes the retarding position S3. In this position, the first pressure chambers 35 are connected to the tank and the second pressure chambers 36 are connected to the pump. Simultaneously, pressure medium is led to the connecting passage 45 of the second rotational angle limiting device 43. The locking pin 44 of the second rotational angle limiting device 43 is held in the unlocked state, while, for simultaneous emptying of the first pressure chambers 35, the pressure medium loading of the second pressure chambers 36 leads to rotation of the internal rotor 23 relative to the external rotor 22 against the rotational direction of the device 10. If the motor controller forces the phase position of the internal rotor 23 relative to the external rotor 22 to be held, then this control valve 37 is moved into the holding position S5. In this position, pressure medium is not exchanged between the pressure chambers 35, 36 and the connecting passage 45 of the second rotational angle limiting device 43 to the tank or the pressure medium pump. The vanes 27 are clamped hydraulically in the pressure space 33 and the rotational angle limiting devices 42, 43 are held in the unlocked position.
If the motor controller forces more advanced control times, then the control valve 37 is brought into the advancing position S7. In this control position, pressure medium is fed to the first pressure chambers 35, while pressure medium is discharged to the tank both from the connecting passage 45 of the second rotational angle limiting device 43 and also from the second pressure chambers 36. Consequently, a relative rotation of the internal rotor 23 relative to the external rotor 22 is caused in the rotational direction of the device 10. In addition, the locking pin 44 of the second rotational angle limiting device 43 can engage in the corresponding connecting passage 45 when these stand opposite each other.
In the intermediate positions S4 and S6, one group of pressure chambers 35, 36 is loaded with pressure medium, while there is no exchange of pressure medium between the other group of pressure chambers 35, 36 and the pump and the tank. In this way it is achieved that during the assumption or exiting of the holding position S5, the hydraulic clamping of the vanes 27 within the pressure spaces 33 is maintained.
During the stop phase of the internal combustion engine 1, the control valve 37 moves into the advancing position S7 and is held in this position for a defined time span past its standstill. Therefore, pressure medium is fed to the first pressure chambers 35, while pressure medium can flow out of the second pressure chambers 36 to the tank. This causes a relative rotation of the internal rotor 23 to the external rotor 22, wherein the internal rotor 23 is led into a position between the locking position and the maximum advanced position. Simultaneously, the control port S and thus the connecting passage 45 of the second rotational angle limiting device 43 are connected to the tank, whereby the second rotational angle limiting device 43 is moved into the locked state. In this way it is guaranteed that the internal rotor 23 moves into a position between the locking position and the maximum advanced position and is then held in this position during the entire stop process and the operating pause of the internal combustion engine 1.
In the last phase of the motor stop in which the device 10 is no longer supplied with sufficient pressure medium, the internal rotor 23 is rotated relative to the external rotor 22 in the direction of the maximum retarded position due to the drag moments acting on the camshafts 6, 7. This movement is stopped by the locked second rotational angle limiting device 43 at the locking position. Due to the lack of system pressure, the first rotational angle limiting device 42 in this position is similarly moved into the locked state, whereby a mechanical fixing of the internal rotor 22 relative to the external rotor 23 is established in the locking position. Alternatively, this process can take place during the startup phase of the internal combustion engine 1 in which the control valve 37 assumes the startup position S1. In this position, the first pressure chambers 35 and the connecting passage 45 of the first rotational angle limiting device 42 connected to these chambers are connected to the tank. The internal rotor 22 is forced into the locking position due to the drag moments acting on the camshaft 6, 7 in which the first rotational angle limiting device 42 can transition into the locked state.
During the regulated operation of the device 10 (control states S3-S7), due to the control logic shown in
Through the separate control of the rotational angle limiting devices 42, 43, only a small number of switch points exists in the control logic that are stored in the motor controller or must be determined by this controller. Simultaneously, the regions of the individual control positions S1-S7 increase, whereby the regulation of the control valve 37 is simplified considerably and the error susceptibility is reduced.
| Number | Date | Country | Kind |
|---|---|---|---|
| 102006031594.4 | Jul 2006 | DE | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/EP07/56197 | 6/21/2007 | WO | 00 | 4/10/2009 |
