Central locking for a camshaft adjuster

Abstract

A hydraulic camshaft adjuster for changing the control times of gas exchange valves of an internal combustion engine, designed as a vane cell camshaft adjuster. A control device inserted in the vane selectively opens and interrupts a flow connection between the working chambers. A locking device prevents relative motion between the rotor and the stator in that the rotor is fastened to the stator at a vane position. A switching valve, which has three working ports, a P port and a T port, can be moved into different control positions by an adjusting element,wherein in the control position, the P port communicates with the working chambers via the A port, the B port is blocked at the switching valve, and the T port communicates with the control device of the vanes via the C port. In a control position provided as a starting strategy for the switching valve the A port communicates with the P port and the working chambers, the B port communicates with the T port and the working chambers, and the C port communicates with the control device of the vanes and the T port.

Claims

1. A hydraulic camshaft adjuster for changing timing of gas exchange valves of an internal combustion engine, configured as a vane camshaft adjuster, the camshaft adjuster comprising: a stator configured to be connected to a crankshaft of the internal combustion engine; a rotor rotatably fixedly supported in the stator and configured to be connected to a camshaft; a line system supplying or discharging a hydraulic medium to or from at least two pressure chambers, a hydraulic switching valve connected therebetween, as well as with aid of pressure medium lines, the at least two pressure chambers each being divided into separate, oppositely acting working chambers by a rotor-fixed vane, a phase angle of the camshaft being selectively variable relative to the crankshaft; a control device in the vane and configured to selectively unblock and interrupt a flow connection between the working chambers; a locking device preventing a relative movement between the rotor and the stator, in that the rotor is fixed on the stator in a vane position, the interacting working chambers having a corresponding volume in the vane position; the locking device including at least one locking pin locking in a central locking position of a locking gate from a direction of an ADVANCE or RETARD stop position during a rotation of the rotor; the at least one locking pin being movable from a first switching position into a second switching position against a spring force by an application of the hydraulic medium; the hydraulic switching valve including three working ports as well as a P port as an inlet and a T port as an outlet and being adjustable into different control positions via a control element; in a first control position of the control positions, the P port and an A port communicating with the working chambers, a B port connected to the working chambers and being blocked at the switching valve, and the T port communicating with the control device of the vane via a C port; in a second control position of the control positions, the P port communicating with the working chambers via the A port, the B port communicating with the working chambers, and the T port as well as the C port communicating with the control device of the vane and the T port; in a third control position of the control positions, the A port and the B port being blocked at the switching valve, and the C port communicating with the P port and the control device of the vane; and in a fourth control position, the A port communicating with the T port and the working chambers, the B port communicating with the P port and the working chambers, and the C port communicating with the P port and the control device of the vane, the switching valve being switchable into a further control position during a starting strategy, the A port communicating with the P port and the working chambers, the B port communicating with the T port and the working chambers, and the C port communicating with the control device of the vane and the P port in the further control position.

2. The camshaft adjuster as recited in claim 1 wherein the starting strategy is applicable in an event that the camshaft adjuster is not locked in a central locking position in a start phase of the internal combustion engine, and an angle position sets in between the central locking position and a RETARD end stop.

3. The camshaft adjuster as recited in claim 1 wherein the B port of the hydraulic switching valve is in a position between the A port and the C port.

4. The camshaft adjuster as recited in claim 1 wherein the at least one locking pin includes first and second locking pins, the first locking pin being provided for locking in an ADVANCE direction and the second locking pin being provided for locking in a RETARD direction.

5. The camshaft adjuster as recited in claim 4 wherein the first locking pin interrupts the hydraulic medium flowing in a hydraulic line to the working chambers in a position extended out of the rotor.

6. The camshaft adjuster as recited in claim 4 wherein the second locking pin interrupts the hydraulic medium flowing in a hydraulic line to the working chambers in a position extended out of the rotor.

7. The camshaft adjuster as recited in claim 1 further comprising a spring element displacing the at least one locking pin of the locking device out of the rotor when a counter-force acting upon the at least one locking pin is absent.

8. The camshaft adjuster as recited in claim 1 further comprising at least one further vane assigned to the at least two pressure chambers, the rotor fixed vane and the further vane each assigned to the at least two pressure chambers in a symmetrically distributed manner.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The present invention is explained in greater detail below on the basis of one preferred exemplary embodiment. Specifically:

(2) FIG. 1 shows a schematic representation of a camshaft adjuster according to the present invention;

(3) FIG. 2 shows a graph of the control characteristic and switching positions of a solenoid valve for a starting strategy of an internal combustion engine according to the present invention; and

(4) FIG. 3 shows a flow chart for the starting strategy according to the present invention.

DETAILED DESCRIPTION

(5) A camshaft adjuster 1, having a known basic structure, is illustrated schematically in FIG. 1, which includes a stator 2, drivable by a crankshaft of an internal combustion engine, which is not illustrated, and a rotor 3, which is rotatably fixedly connected to a camshaft (not illustrated), including a rotor hub 4, and multiple vanes 5, 6, 7 oriented radially therefrom. Pressure chambers 8, 9, 10 are divided into working chambers 11 through 16 by vanes 5, 6, 7. The top illustration in FIG. 1 shows the vane adjuster in a developed view, while a detail of rotor hub 4 of rotor 2, including a locking device 29, is shown schematically at the lower left, and a switching valve 17, designed as a multi-way switching valve for controlling the pressure or hydraulic medium of camshaft adjuster 1, is shown schematically at the lower right. Switching valve 17 according to the present invention is a proportional valve, which includes five connections or ports as well as five control or piston positions 47a through 47e. A P port 18, or inlet port, is connected to a pressure pump, and a T port 19, or outlet port, is assigned to a tank or pressure medium reservoir. An A port 20 forms a connection for working chambers 11, 13, 15, and B port 21 is in contact with working chambers 12, 14, 16. Additional C port 22 is designated for control devices 23, 24, 25 of vanes 5, 6, 7. All ports are either switched open or closed, according to the control position of switching valve 17. Pressure is applied to switching valve 17 by a spring element 26, and an integrated piston is adjustable into the particular control or piston position as needed with the aid of a control element 27 preferably designed as an electromagnet.

(6) FIG. 1 furthermore shows a hydraulic or pressure medium circuit, including a large number of pressure medium lines, which represents a hydraulic line system 28 between switching valve 17 and pressure chambers 8, 9, 10 as well as locking device 29. A hydraulic line 30 connects A port 20 directly to working chambers 13, 15. A branch of hydraulic line 30 is guided via locking device 29 to working chamber 11. Hydraulic line 31 establishes a connection between B port 21 and working chambers 12 and 16. Hydraulic line 31 runs to additional working chamber 14 via locking device 29. Hydraulic line 32 also connects C port 22 to all control devices 23 through 25 of vanes 5 through 7.

(7) The rotation angle of the camshaft with respect to the crankshaft during normal operation, e.g., in the ADVANCE direction, is adjustable by the fact that pressure medium is applied to working chambers 11, 13, 15 via hydraulic line 30, whereby their volume is increased, while the pressure medium is simultaneously forced out of working chambers 12, 14, 16 and their chamber volume is consequently reduced. In FIG. 1, the ADVANCE direction is identified by an arrow, and the RETARD direction runs counter to the arrow direction. Working chambers 11, 13, 15, whose volume is increased in groups during the adjusting movement in the ADVANCE direction, are referred to as working chambers of one operating direction. The change in volume of working chambers 11, 13, 15 results in the fact that rotor 3, including vanes 5, 6, 7, is rotated with respect to stator 2. The volume of working chambers 12, 14, 16 may be increased by an application of pressure medium via B port 21 of switching valve 17 in connection with hydraulic line 31, while the volume of working chambers 11, 13, 15 simultaneously decreases due to a back-flow of the pressure medium via A port 20. This change in volume results in a rotation of rotor 3 with respect to stator 2, against the arrow direction in the RETARD direction.

(8) Locking device 29 includes two locking pins 33, 34, which are also to be referred to as locking pinions, and which are linearly displaceable and inserted, spring loaded, into a receptacle 35 of rotor hub 4. Locking pins 33, 34 are arranged in the direction of a locking gate 36, spring-loaded by a spring element 43. Locking device 29 is released to facilitate the adjustment of rotor 3 with respect to stator 2. This takes place by applying pressure medium to locking gate 36, for which purpose pressure medium is supplied from C port 22 via hydraulic line 32 and another hydraulic line 37 in a corresponding control position of switching valve 17. Due to the application of pressure medium, locking pins 33, 34 are forced out of locking gate 36, so that rotor 3 is able to rotate freely with respect to stator 2.

(9) Flow connections 38, 39, 40 are introduced into each of vanes 5, 6, 7, flow connections 38, 39 being assigned to a check valve 41, 42, which facilitates an overflow of the pressure medium or hydraulic medium from working chamber 12 into working chamber 11 or from working chamber 13 into working chamber 14. The flow of the pressure medium through flow connections 38, 39, 40 may be unblocked or blocked by switchable, control pins 44, 45, 46, to which spring force is applied. Switchable control pins 44, 45, 46, to which spring force is applied and which are assigned to control device 23, 24, 25, are each acted upon by pressure medium via hydraulic line 32 and are adjustable from a locking position into an unlocking position. In the unlocking position, the flow-through flow connection 38, 39, 40 is blocked, so that working chambers 11, 12; 13, 14 and 15, 16 are separated from each other.

(10) According to first control position 47a of switching valve 17 illustrated in FIG. 1, locking pin 33 engages into locking gate 36, supported by spring element 43, this position corresponding to an ADVANCE stop position, in which locking pin 33 blocks a section of hydraulic line 30 and thus prevents a flow connection to working chamber 11. At the same time, engaged locking pin 34 opens a passage, so that a fluidic connection to working chamber 14 sets in via connected hydraulic line 31. Switching valve 17 according to the present invention may be adjusted in five control positions 47a through 47e by correspondingly energizing control element 27, whereby camshaft adjuster 1 is adjustable into different positions, for example in the direction of an ADVANCE adjustment or a RETARD adjustment.

(11) The application of the starting strategy according to the present invention is provided for the event that camshaft adjuster 1 does not lock in a central locking position (CLP) in a start phase of the internal combustion engine. In the start phase, the controller of the internal combustion engine briefly detects the angle position of the camshaft, no later than after one revolution of the camshaft. If camshaft adjuster 1 is not locked in the central locking position (CLP) but rather, for example, in an angle position between a RETARD stop position and the central locking position, the starting strategy according to the present invention is automatically initiated. Switching valve 17 is energized in such a way that its piston approaches control position 47b, the second position. After a brief engine standstill, an oil pressure builds up relatively quickly in the internal combustion engine, so that oil as the hydraulic medium is applied to working chambers 13, 15 from P port 18 to A port 20 and via hydraulic line 30. At the same time, working chambers 14, 16 are connected to the tank or the pressure medium reservoir via hydraulic line 31, B port 21 and T port 19. Similar to control position 47c, the third piston position, camshaft adjuster 1 is adjusted into control position 47c in the direction of the arrow, i.e., in the ADVANCE direction.

(12) In contrast to control position 47c but corresponding to control position 47a, C port 22 is connected to T port 19 in control position 47b, resulting in an unpressurized hydraulic line 32 and unpressurized locking gate 36, whereby locking pin 33 remains engaged in locking gate 36. Deviating from control position 47a, the first piston position, which provides a closed B port 21, B port 21 is also connected to the tank via T port 19 in control position 47b. In first control position 47a, B port 21 is closed, so that the oil does not flow out of camshaft adjuster 1 back into the tank in the start phase of the internal combustion engine when camshaft adjuster 1 is being filled. This results in increased pressure medium or oil leaks, which prevent a necessary, short-term pressure buildup within the internal combustion engine. Compared to previous approaches, A port 20 and the B port are reversed for the starting strategy according to the present invention, so that camshaft adjuster 2 adjusts to ADVANCE in second control position 47b of switching valve 17. In the previous circuit, camshaft adjuster 1 would have adjusted to RETARD and thus not in the direction of the central locking position (CLP).

(13) Based on the new starting strategy, camshaft adjuster 1 is able to adjust only to up the central locking position, where it locks due to the engagement of locking pin 34. The internal combustion engine may subsequently be started up. After a long standstill time, the oil pressure buildup within the internal combustion engine may be prolonged, whereby the adjusting operation is slightly delayed. The starting strategy according to the present invention may, however, also be applied here, since a delayed oil pressure buildup does not have a negative impact on the start operation.

(14) FIG. 2 shows a valve characteristic of switching valve 17 according to the present invention. In the graphical illustration, the magnetic flux (A) of the control element 27 used to adjust switching valve 17 is plotted on the abscissa, and the volume flow (1/min.) of the oil, which is referred to as hydraulic or pressure medium, is plotted on the ordinate. Based on additional control position 47b, a modified volume flow characteristic of the hydraulic medium sets in. In control position 47b, no oil yet flows into C port 22 and into hydraulic line 32 connected thereto. At the same time, B port 21 is connected to T port 19 and enables oil to be forced out of working chambers 12, 16 into the reservoir or into the tank via hydraulic line 31. As a result, the existing pressure present at A port 20 may be transferred to working chambers 13, 15 via hydraulic line 30 for the purpose of triggering an adjustment of camshaft adjuster 1 and consequently the timing of the gas exchange valves in the ADVANCE direction.

(15) A flowchart for the starting strategy of an internal combustion engine according to the present invention is illustrated graphically in FIG. 3. Three different line diagrams are combined vertically one above the other in such a way that the abscissa forms a time axis for all diagrams. The bottom line diagram shows a pulse duty factor (%) related to the different control positions 47a through 47e of switching valve 17. The course of the curve of the middle diagram relates to the angle position of the adjusting system of the camshaft ( CS). The top diagram shows the rotational speed curve (rpm) of the internal combustion engine.

LIST OF REFERENCE NUMERALS

(16) 1 camshaft adjuster 2 stator 3 rotor 4 rotor hub 5 vane 6 vane 7 vane 8 pressure chamber 9 pressure chamber 10 pressure chamber 11 working chamber 12 working chamber 13 working chamber 14 working chamber 15 working chamber 16 working chamber 17 switching valve 18 P port 19 T port 20 A port 21 B port 22 C port 23 control device 24 control device 25 control device 26 spring element 27 control element 28 line system 29 locking device 30 hydraulic line 31 hydraulic line 32 hydraulic line 33 locking pin 34 locking pin 35 receptacle 36 locking gate 37 hydraulic line 38 flow connection 39 flow connection 40 flow connection 41 check valve 42 check valve 43 spring element 44 control pin 45 control pin 46 control pin 47a control position 47b control position 47c control position 47d control position 47e control position