DE102014207337A1 - Camshaft adjustment device - Google Patents

Abstract

The present invention relates to a camshaft adjusting device with a Flügelzellenversteller and a center locking device (33) for locking the rotor (17) in a center locking position relative to the stator (16), wherein the center locking device (33) by pressing a locking link (22) is unlocked, and at least one in the rotor (17) arranged valve pin, wherein the valve pin is not used to lock the stator (16) relative to the rotor (17), and depending on the switching position of the valve pin in a rotational movement from a stop position "early" or "late" in the center locking position at least two oppositely acting working chambers (24, 25, 26, 27, 28, 32) are fluidically connectable, wherein a first pressure medium line (23) exclusively in response to the switching position of at least one first valve pin (41) with a pressure medium reservoir (T) verbin is dbar.

Description

The invention relates to a camshaft adjusting device having the features of the preamble of claim 1.

Camshaft phasers are generally used in internal combustion engine valve trains to vary the valve opening and closing times, which can improve engine fuel economy and performance generally.

A proven in practice embodiment of the camshaft adjusting device has a Flügelzellenversteller with a stator and a rotor, which define an annular space, which is divided by projections and wings in a plurality of working chambers. The working chambers are optionally acted upon by a pressure medium, which is fed in a pressure medium circuit via a pressure medium pump from a pressure medium reservoir in the working chambers on one side of the blades of the rotor and is returned from the working chambers on the other side of the wings back into the pressure medium reservoir. The working chambers, the volume of which is increased, have a direction of action, which is the direction of action of the working chambers whose volume is reduced, opposite. Accordingly, the direction of action means that pressurizing the respective group of working chambers causes rotation of the rotor either clockwise or counterclockwise relative to the stator. The control of the pressure medium flow and thus the adjustment movement of the camshaft adjusting device takes place e.g. by means of a central valve having a complex structure of flow openings and control edges and a valve body which is displaceable in the central valve and closes or releases the flow openings as a function of its position.

A problem with such a camshaft adjusting device is that it is not completely filled with pressure medium in a starting phase or may even have run empty, so that the rotor can perform uncontrolled movements relative to the stator due to the alternating moments exerted by the camshaft, which can lead to increased wear and to an undesirable noise. To avoid this problem, it is known to provide a locking device between the rotor and the stator, which locks the rotor when stopping the internal combustion engine in a favorable for the start angle of rotation position relative to the stator. In exceptional cases, such as when stalling the internal combustion engine, it is possible that the locking device does not lock the rotor as intended, and the camshaft adjuster must be operated in the subsequent starting phase with unlocked rotor. However, since some internal combustion engines have a very poor starting behavior when the rotor is not locked in the center position, the rotor must then be automatically rotated and locked in the starting phase in the center locking position.

Such automatic rotation and locking of the rotor relative to the stator is eg from the DE 10 2008 011 915 A1 and from the DE 10 2005 011 916 A1 known. Both locking devices described therein comprise a plurality of spring-loaded locking pins, which lock in a rotation of the rotor successively provided in the sealing cover or the stator locking latches and allow before reaching the center locking position each rotation of the rotor in the direction of the center locking position, but a rotation of the Block the rotor in the opposite direction. After warming up of the internal combustion engine and / or the complete filling of the camshaft adjuster with pressure medium, the locking pins are displaced pressure medium actuated from the locking cams, so that the rotor can then be rotated as intended to adjust the rotational angle position of the camshaft relative to the stator.

A disadvantage of this solution is that the locking of the rotor can be realized only with a plurality of successively locking locking pins, resulting in higher costs. Furthermore, the locking operation requires that the locking pins lock functionally in succession. If one of the locking pins is not locked, the locking process can be interrupted, since the rotor is not locked in the intermediate position on one side and can turn back.

The object of the invention is therefore to provide a camshaft adjuster with a functionally reliable and cost-effective center locking of the rotor.

According to the basic idea of the invention, it is proposed that a first pressure medium line can be connected to a pressure medium reservoir exclusively as a function of the switching position of at least one first valve pin. The function of the faster discharge of the first pressure medium line is not taken over by one of the locking pins and thus the function of the faster discharge of the first pressure medium line separated from the locking function. The particular advantage of the present invention is that a valve pin is used, which is provided anyway in the camshaft adjusting to a Freewheel to realize. In the freewheel, the rotor is rotated by utilizing the acting on the camshaft in the starting phase alternating moments (Camshaft Torque Actuated CTA) in a direction opposite to the stator, while the rotational movement in the other direction is blocked by the check valve respectively. From the already existing valve pins at least a first valve pin is adapted to establish a fluidic connection between the first pressure medium line and the pressure medium reservoir depending on its switching position. The valve pins may be provided in the rotor hub or in at least one of the blades of the rotor. The essential advantage of an additional fluidic connection of a first pressure medium line via a first valve pin to the pressure medium reservoir is that, especially at low temperatures of the pressure medium and the associated high viscosity, an increased volume flow into the pressure medium reservoir can be achieved. As a result, the locking pins can be moved faster from the first to the second switching position and thus a faster and more reliable locking in the center locking position is made possible.

It is further proposed that a receiving space for the first valve pin with a second, third and fourth pressure medium line is fluidly connected, wherein the second and the third pressure medium line are fluidly connected to the first pressure medium line, and the fourth pressure medium line is fluidly connected to the pressure medium reservoir. Depending on the switching position of the valve pin so a fluidic connection between the second pressure medium line and the pressure medium reservoir can be made, whereby the first pressure medium line is connected to the pressure medium reservoir. In a further switching position, the third pressure medium line can be connected to a receiving space of the first valve pin and thus be taken over in addition to the fluidic connection of the first pressure medium line with the pressure medium reservoir through the valve pin yet another valve function.

Further, it is advantageous if a control port is provided at the receiving space, which is fluidically connected to the first pressure medium line. The pressure level of the first pressure medium line can thus serve to control the switching position of the first valve pin. Depending on the switching position, a fluidic connection can be established between the control port and the third pressure medium line.

Preferably, the first valve pin can assume at least two switching positions, wherein in a first switching position, the second pressure medium line is fluidly connected to the fourth pressure medium line, and in a second switching position, the third pressure medium line is connected to the control port. This is particularly advantageous because in a first switching position, the first pressure medium line is fluidly connected via a receiving space of the valve pin with the pressure medium reservoir. However, since this switching position does not occur immediately after switching off due to the inertia of the system, the pressure medium from the first pressure medium line via the control port and the third pressure medium line can flow into the pressure medium reservoir until reaching the first switching position.

It is further proposed that the first valve pin is moved counter to a spring force from the first to the second switching position when a defined pressure level is exceeded at the control port. The control of the valve pin can be done in a simple manner by the pressure at any point of the printing system. Preferably, the pressure of the first pressure medium line is used as a control variable.

It is also proposed that in the first pressure medium line a check valve is arranged, which can be flowed through only in the direction of a multi-way switching valve. When the internal combustion engine is switched off, the pressure medium of a part of the line system can flow directly into the pressure medium reservoir. In a restart of the internal combustion engine direct pressurization of the conduit system is blocked by the pressure medium pump through the check valve, so that first the control port of the first valve pin is acted upon by pressure medium and so the first valve pin is moved from the first to the second switching position. By the movement from the first to the second switching position, the fluidic connection between the first pressure medium line and the pressure medium reservoir is blocked via the first valve pin. It is thus ensured that a fluidic short circuit between the pressure medium pump and the pressure medium reservoir is prevented. To ensure this functionality, the check valve is preferably arranged directly between a node and the multi-way switching valve, wherein at the node, a portion of the first pressure medium line is fluidly connected to the first valve pin.

It is further proposed that the first valve pin is provided in the rotor hub. It is particularly advantageous if the first valve pin is formed by an already existing valve function pin. The receiving space must be connected to this only with the second and third pressure medium line to a direct to allow fluidic connection to the first pressure medium line. In addition, the receiving space via the fourth pressure medium line must be connected to the pressure medium reservoir. These adjustments can be implemented with little manufacturing effort, so that a faster discharge of the first pressure medium line is inexpensive to implement.

Preferably, the control port is formed by the locking link. The locking link is directly fluidically connected to the first pressure medium line, so that in a simple manner, the pressure of the first pressure medium line can be used as a control variable.

Further preferably, the control port is fluidically decoupled from the locking link. In this case there is no direct fluidic connection between the multi-way switching valve and the locking link. About the C-port of the multi-way switching valve, the control port of the first valve pin is first pressurized with pressure medium. It is thereby the valve pin moves from the first switching position to the second switching position and thus released a fluidic connection between the control port and the third pressure medium line. In this embodiment, the second and third pressure medium line is connected fluidically exclusively with the locking link. Thus, the pressure medium loading of the locking linkage is controlled via the first valve pin; a Druckmittelbeaufschlagung the locking link is in the second switching position of the first valve pin. When the internal combustion engine is switched off, the first valve pin moves into the first switching position. Until the full reaching of the first switching position, the pressure medium flows from the locking link via the second pressure medium line and the control port back into the pressure medium reservoir. Already during the adjustment of the second to the first switching position of the first valve pin, the locking link is fluidically connected via the second pressure medium line, the receiving space and the fourth pressure medium line to the pressure medium reservoir. It can be created as a larger flow cross-section in the direction of the pressure medium reservoir, whereby the flow rate is increased. In particular, at low temperatures and the associated high viscosity of the pressure medium as a faster outflow of the pressure medium can be realized.

It is also proposed that the first valve pin is formed by at least one valve device in one of the wings. The valve device in the wing serves to fluidly connect two oppositely acting working chambers via a check valve during the freewheel.

The invention will be explained in more detail with reference to a preferred embodiment. It can be seen in the figures in detail:

1 : A schematic representation of a camshaft adjusting device according to the invention in a first embodiment with a circuit diagram of a pressure medium circuit during an adjustment movement of the rotor from the direction "late" in the center locking position.

2 a schematic representation of a camshaft adjusting device according to the invention in a first embodiment with a circuit diagram of a pressure medium circuit at an adjustment movement of the rotor from the direction "early" in the center locking position;

3 : A schematic representation of a camshaft adjusting device according to the invention in a first embodiment with a circuit diagram of a pressure medium circuit in the normal operating state;

4 : a schematic representation of a camshaft adjusting device according to the invention in a second embodiment with a circuit diagram of a pressure medium circuit in the normal operating state with a decoupled control port;

5 a schematic representation of a camshaft adjusting device according to the invention in a third embodiment with a circuit diagram of a pressure medium circuit in the normal operating state with a decoupled control port; and

6 : A schematic representation of a camshaft adjusting device according to the invention in a fourth embodiment with a circuit diagram of a pressure medium circuit in the normal operating state with a decoupled control port.

The basic operation of the camshaft adjusting device is first based on the 1 to 3 explained. In 1 is a camshaft adjusting device with a known basic structure with a schematically illustrated Flügelzellenversteller to recognize as a basic component, which is driven by a crankshaft, not shown, stator 16 and a rotatably connected to a camshaft, also not shown rotor 17 with a rotor hub 36 and a plurality of radially outwardly extending wings 11 . 12 and 13 includes. In the upper illustration, the vane pitch adjuster is in progress to recognize, while lower left schematically a section of the rotor hub 36 of the rotor 17 with a center locking device 33 and at the bottom right schematically a multi-way switching valve 21 To recognize the control of the pressure medium flow.

Furthermore, a pressure medium circuit with a plurality of pressure medium lines 1 . 2 . 3 . 4 . 5 . 6 . 7 . 8th . 23 . 34 . 35 . 37 . 38 . 39 . 40 . 42 . 43 and 44 to detect which via the multi-way switching valve 21 optionally fluidically connected to a pressure medium pump P or a pressure medium reservoir T, wherein the pressure medium pump P, the pressure medium after returning to the pressure medium reservoir T from the same again promotes the pressure fluid circuit.

The stator 16 has a plurality of stator bars, which an annular space between the stator 16 and the rotor 17 in several pressure chambers 29 . 30 and 31 divide. The pressure chambers 29 . 30 and 31 in turn are through the wings 11 . 12 and 13 of the rotor 17 in working chambers 24 . 25 . 32 . 26 . 27 and 28 divided, in which the pressure medium lines 1 . 3 . 4 . 6 . 7 and 8th lead. The center locking device 33 includes two locking pins 18 and 19 , which for locking the rotor 17 opposite the stator 16 in a stator-fixed locking link 22 lock. The locking mechanism 22 eg in one with the stator 16 be screwed sealing lid arranged.

Basically, the angle of rotation of the camshaft is adjusted to the crankshaft in normal operation, for example in the direction of "early" characterized by the working chambers 24 . 32 and 27 be acted upon with pressure medium and thereby increase their volume, while at the same time the pressure medium from the working chambers 25 . 26 and 28 displaced and the volume is reduced. The working chambers 24 . 25 . 26 . 27 . 28 and 32 , whose volume is increased in groups in each case during this adjustment, are in the context of the invention as working chambers 24 . 25 . 26 . 27 . 28 and 32 denotes a direction of action, while the working chambers 24 . 25 . 26 . 27 . 28 and 32 whose volume is simultaneously reduced, as working chambers 24 . 25 . 26 . 27 . 28 and 32 be designated the opposite direction of action. The volume change of the working chambers 24 . 25 . 26 . 27 . 28 and 32 then causes the rotor 17 with the wings 11 . 12 and 13 opposite the stator 16 is twisted. In the upper illustration of the 3 becomes the volume of the working chambers 25 . 26 and 28 by a pressure medium via the B-port of the multi-way switching valve 21 increases while the volume of the working chambers 24 . 32 and 27 at the same time by flowing back the pressure medium via the A-port of the multi-way switching valve 21 is reduced. This change in volume then leads to a rotation of the rotor 17 opposite the stator 16 , which in the developed representation leads to a displacement of the wings 11 . 12 and 13 in the direction of the arrow leads to the left. There is also a valve operating pin 20 provided, which is also linearly displaceable and spring-loaded. The valve operating pin 20 is in the direction of the engagement position in the locking link 22 spring loaded and so on the rotor 17 arranged that he is the rotary motion of the rotor 17 opposite the stator 16 not disabled. The valve operating pin 20 is practically only moved. Thus the adjustment of the rotor 17 opposite the stator 16 is possible, the center locking device 33 first loosened by the locking link 22 over the first pressure medium line 23 from the C-port of the multi-way switching valve 21 is acted upon by the pressure medium pump P with pressure medium. By the pressure medium loading the locking link 22 become the locking pins 18 and 19 and the valve operating pin 20 from the locking frame 22 pushed out, leaving the rotor 17 then opposite the stator 16 can rotate freely.

In the wings 11 and 12 are each pressure medium lines 34 and 35 with a non-return valve disposed therein 9 and 10 provided which an overflow of the pressure medium from the working chamber 25 in the working chamber 24 and from the working chamber 32 in the working chamber 26 enable. The flow of the pressure medium through the pressure medium lines 34 and 35 may further be provided by a respective second switchable spring-loaded valve device 14 and 15 be blocked or enabled. For this purpose, the switchable valve device 14 and 15 two switch positions in which the flow is either enabled or disabled. The switchable second valve devices 14 and 15 are each via a pressure medium line 2 and 5 be acted upon with pressure medium and are transferred at a Druckmittelbeaufschlagung by a displacement of a valve body against the acting spring force of the first to the second switching position, which in the 3 can be seen. In the second switching position, the flow through the pressure medium lines 34 and 35 locked, leaving the working chambers 24 and 25 respectively. 32 and 26 are considered to be separated from each other, and the camshaft adjusting without an overflow of the pressure medium between the working chambers 24 . 25 . 32 and 26 can be operated with a correspondingly high adjustment accuracy.

The center locking device 33 includes two locking pins 18 and 19 , which together with the valve function pin 20 a switchable first valve device in the rotor hub 36 form. The locking pins 18 and 19 and the valve operating pin 20 are designed as spring-loaded valve body with corresponding grooves or holes, which by pressurizing the locking link 22 via the pressure medium line 23 against the acting spring force of a first and a second switching position are displaced. Here are the locking pins 18 and 19 and the valve operating pin 20 then in the first switching position when in the locking slot 22 engage and the springs are relaxed.

The holes or grooves in the locking pin 18 are arranged so that a flow through the pressure medium in the first switching position of the locking pin 18 with unloaded spring between the pressure medium line 1 and the pressure medium lines 37 and 4 is locked, as in the position in the 1 can be seen. This position exists when the rotor 17 when starting the internal combustion engine is not locked in the center locking position and in the direction of the stop position "late" relative to the stator 16 is twisted. The stop position "late" is marked in the illustration by an S and the stop position "early" by an F. At the same time the locking pin engages 19 not in the locking frame 22 and is thereby moved against the spring force in the second switching position. The holes or grooves in the locking pin 19 are arranged so that the locking pin 19 in the second switching position, a flow of the pressure medium between the pressure medium lines 6 and 40 releases. The pressure medium lines 6 and 40 are fluidically to the working chambers 25 . 26 and 28 connected, which are thereby short-circuited. Here, the pressure medium lines open 3 and 8th in a partial ring or annular pressure medium line 38 at the rotor hub 36 , which in turn fluidly via the pressure medium line 40 to the locking pin 19 connected. Due to the partial ring or annular pressure medium line 38 can the locking pin 19 via a single pressure medium line 40 fluidically with the pressure medium lines 3 and 8th connected, whereby the wiring and the short-circuiting of the working chambers 25 . 26 and 28 can be simplified. Furthermore, the valve operating pin is located 20 in the first switching position in which the at the valve operating pin 20 provided bore or groove a fluidic connection between the pressure medium lines 40 and 39 manufactures, so that the working chambers 32 and 26 the pressure chamber 30 and the working chambers 27 and 28 the pressure chamber 31 different directions of action are shorted. This also lead to the pressure medium lines 4 and 7 in the partial ring or annular pressure medium line 37 at the rotor hub 36 , which in turn via a pressure medium line 39 fluidically with the valve operating pin 20 is connectable. The short circuit via the valve operating pin 20 takes place in this position via the connection of the pressure medium lines 39 and 40 , So by shorting the partial ring or annular pressure medium lines 37 and 38 , A pressure medium via the multi-way switching valve 21 does not take place in this position, and the outflow of the pressure medium via the A and B ports of the multi-way valve 21 is locked.

In the event that the camshaft adjusting device is not locked in the center locking position when the internal combustion engine is started, the rotor becomes 17 from the in the 1 shown position automatically from the direction of the stop position "late" (S) in the direction of the center locked position in the arrow direction by the acting on the camshaft alternating torques (CTA Camshaft Torque Actuated) are used to the pressure medium from the working chamber 25 through the pressure medium line 35 , via the check valve 9 , in the working chamber 24 can flow in. Because the other working chambers 32 . 26 . 27 and 28 are short-circuited in this position, the adjustment is not hindered by the pressure medium located therein. Furthermore, since the pressure medium is not removed from the working chamber 24 can drain and not through the check valve 9 in the working chamber 25 can flow back, the rotor can 17 at the same time, do not turn back in the direction of the stop position "late" (S). The rotor 17 is supported practically on the one in the working chamber 24 located pressure medium, wherein the volume of the working chamber 24 through the over the check valve 9 pulsating inflowing pressure medium is increased, and the rotor 17 thereby against the stator 16 is twisted. The check valve 9 forms together with the corresponding blocked or released pressure medium lines 1 . 3 . 4 . 6 . 7 and 8th a freewheel through which the rotor 17 taking advantage of the alternating moments unilaterally in the direction of the center locking position relative to the stator 16 is twisted until the locking pin 19 in the locking frame 22 engages or until the locking pin 18 laterally on a stop of the locking link 22 comes to plant. By the intervention of the locking pin 19 into the locking contour 22 this passes automatically due to the acting spring force in the first switching position in which the previously released flow connection between the pressure medium lines 6 . 3 and 8th is locked, and the short circuit created over it is canceled. This will cause a further rotational movement of the rotor 17 opposite the stator 16 prevented, and the rotor 17 is locked in the center locking position. For the functionality of the freewheel, it is of particular importance that the working chambers 32 and 26 the pressure chamber 30 and the working chambers 27 and 28 the pressure chamber 31 with the different directions of action while the groove or the bore of the valve operating pin located in the first switching position 20 are short-circuited so that the pressure medium therein can flow freely.

In the 2 is the reverse adjustment from the direction of the stop position "Early" (F) in the direction of the center locking position to recognize. The principle of the adjustment is identical. In this case, the locking pin is located 18 in the second switching position and thereby provides a flow connection between the pressure medium lines 1 . 4 and 7 come and close the working chambers 24 . 32 and 27 short by that. Furthermore, there is the locking pin 19 in the first switching position and thereby blocks a flow of the pressure medium from the working chamber 26 via the pressure medium line 6 to the pressure medium lines 3 and 8th so that the working chamber 26 is decoupled from the pressure medium circuit. In this case, the pressure medium flows out of the working chamber when alternating torques occur during the starting phase of the internal combustion engine 32 via the pressure medium line 34 and the check valve therein 10 in the working chamber 26 and thereby increases its volume, since the outflow of the pressure medium at the same time by the blocked pressure medium line 6 is prevented.

For the invention, it is of particular importance that the working chambers 24 . 25 . 26 . 27 . 28 and 32 different effective direction, which are not part of the currently acting freewheel, on the first switchable valve device formed by the valve operating pin 20 , be short-circuited, so that the automatic adjustment movement is not due to that in the working chambers 24 . 25 . 26 . 27 . 28 and 32 located pressure medium is obstructed. It is particularly advantageous that the valve function pin 20 in the rotor hub 36 is arranged, as a result of the arrangement of the valve function by the pin 20 short-circuited pressure medium lines can be considerably simplified. This is realized in the present solution by the semi-annular or annular pressure medium lines 37 and 38 are provided, in which the pressure medium lines 3 and 8th respectively. 4 and 7 lead. The short circuit via the valve operating pin 20 then takes place solely by shorting the two pressure medium lines 39 and 40 , which in each case in the partial ring or annular pressure medium lines 37 and 38 lead. The semi-annular or annular pressure medium lines 37 and 38 can be realized in the form of circumferential grooves. As a result, the design effort can be considerably simplified.

The valve operating pin 20 and the valve means 14 and 15 are essential for the operation of the freewheel, hereinafter these valve pins are called. Unlike the locking pins 18 and 19 Only use a valve function.

The solution according to the invention provides that at least one of the valve pins has a first valve pin 41 forms over which the pressure medium of a first pressure medium line 23 can drain into the pressure fluid reservoir T. In a first, second and third embodiment of the invention, the first valve pin 41 through the valve operating pin 20 formed (see 1 to 5 ). In a fourth embodiment of the invention (see 6 ) becomes the first valve pin 41 through the valve device 15 educated.

1 shows a first embodiment of the invention, in which the first valve pin 41 through the valve operating pin 20 is formed. The first valve pin 41 is in a recording room 45 mounted axially displaceable, wherein the receiving space 45 fluidically with a second, third and fourth pressure medium line 42 . 43 and 44 connected is. The control of the first valve pin 41 takes place via a control port 46 passing through the locking link 22 is formed. The multi-way switching valve 21 is switched so that with the first pressure medium line 23 Connected C-port of the multi-way switching valve 21 fluidly connected to the pressure medium reservoir T is connected.

1 shows the camshaft adjusting shortly after switching off the internal combustion engine in an adjustment movement from the direction "late" in the center locking position. The locking mechanism 22 is due to the switching position of the multi-way switching valve 21 not impacted with pressure medium, whereby the first valve pin 41 is moved by the acting spring force in the first switching position. In this switching position, the second pressure medium line 42 fluidically so with the receiving space 45 connected, that the pressure medium from the second pressure medium line 42 in the fourth pressure medium line 44 can flow. The fourth pressure medium line 44 is fluidically connected to the pressure medium reservoir T. Through the first valve pin 41 is a fluidic connection between the second pressure medium line 42 and the third pressure medium line 43 or the control port 46 prevented. The pressure medium from a section of the first pressure medium line 23 can thus on the second and fourth pressure medium line 42 and 44 drain into the pressure fluid reservoir T. A check valve 47 is between two nodes 48 and 49 arranged, the direction of action of the check valve 47 so is that the pressure medium is not from the node 49 in the direction of the junction 48 can flow.

2 shows the camshaft adjusting shortly after switching off the engine during an adjustment of the rotor 17 from the direction "early" to the center locking position. The first valve pin 41 is located, as in the movement from the direction "late" in the center locking position, in the first switching position, so that an outflow of the pressure medium from the first pressure medium line 23 also here via the second and fourth pressure medium line 42 and 44 can be done in the pressure medium reservoir T.

3 shows the camshaft adjusting device in the normal operating state. The C port and the B port of the multi-way switching valve 21 are pressurized via the pressure medium pump P with pressure medium. The locking mechanism 22 is via the first pressure medium line 23 subjected to pressure medium, so that the first valve pin 41 is moved from the first to the second switching position counter to the acting spring force. At the in the direction of the locking link 22 directed end face of the first valve pin 41 there is an annular groove 50 via which the pressure medium from the control port 46 and thus out of the locking frame 22 in the second pressure medium line 42 can flow. The fluidic connection between the third and fourth pressure medium line 43 and 44 is in the second switching position of the first valve pin 41 blocked. Through the check valve 47 between the nodes 48 and 49 Ensures that the first valve pin 41 located in the second switching position, before the valve devices 14 and 15 via the pressure medium lines 23 . 2 and 5 be acted upon with pressure medium. A fluidic short circuit between the pressure medium pump P and the pressure medium reservoir T is thus reliably prevented.

A second embodiment of the invention is the 4 refer to. The basic structure of the camshaft adjusting device agrees with that of the first embodiment. The main difference is that the tax haven 46 of the first valve pin 41 from the locking gate 22 is fluidically decoupled. The first pressure medium line 23 consists of a first subsection 23a and a second subsection 23b ,

4 shows the second embodiment of the invention in the normal operating state, in which the C-port and the B-port of the multi-way switching valve 21 are connected to the pressure medium pump P. The control port 46 is thus over the first section 23a subjected to pressure medium, so that the first valve pin 41 is moved against the spring force from the first to the second switching position. About the ring groove 50 becomes the second pressure medium line 42 release, whereby the pressure medium from the first section 23a via the control port 46 in the second pressure medium line 42 can flow. The second pressure medium line 42 is in this embodiment with the second section 23b fluidly connected, this to the locking link 22 connected. About the first and second sections 23a and 23b becomes the locking link 22 in the normal operating state pressurized with pressure medium.

As soon as the internal combustion engine is switched off, the pressure medium flows from the control port 46 over the first section 23a and the C-port in the pressure medium reservoir T. This switching position of the multi-way switching valve 21 is in 4 not shown. By relieving the control port 46 the first valve pin moves 41 from the second to the first switching position. During the transition between the second and the first switching position, the pressure medium can still on the second pressure medium line 42 , the control port 46 and the first section 23a drain into the pressure fluid reservoir T. At the same time, the flow cross-section between the third pressure medium line increases 43 and the recording room 45 , until the fluidic connection between the third pressure medium line 43 and the fourth pressure medium line 44 over the recording room 45 is completely open in the first switching position. The pressure medium can thus from the locking link 22 over the second section 23b and on the third and fourth pressure medium line 43 and 44 flow directly into the pressure fluid reservoir T. Furthermore, the pressure medium can also be independent of the switching position of the first valve pin 41 over the second section 23b , the pressure medium line 23 , the check valve 47 and the C port of the multi-way switching valve 21 flow out. Due to the additional outflow of the pressure medium via the third and fourth pressure medium line 43 and 44 a significantly enlarged flow cross-section can be realized, whereby the volume flow of the pressure medium into the pressure medium reservoir can be improved, in particular at low temperatures.

5 shows a third embodiment of a camshaft adjusting device according to the invention. Analogous to the embodiment in FIG 4 is a decoupling of the control port 46 from the locking gate 22 to recognize. Analogous to the description of the embodiment 4 can the pressure medium in a first switching position of the first valve pin 41 from the locking gate 22 over the second section 23b and on the third and fourth pressure medium line 43 and 44 drain into the pressure fluid reservoir T. The main difference to the embodiment in 5 is the arrangement of the check valves 9 and 10 in the locking pins 18 and 19 , The operation of the additional outflow of the pressure medium via the third and fourth pressure medium line 43 and 44 in the pressure medium reservoir T is identical.

A fourth embodiment of the camshaft adjusting device according to the invention is 6 refer to. Here, the first valve pin 41 through the valve device 15 educated. Of the control port 46 is in this embodiment via the pressure medium line 5 fluidically with the first pressure medium line 23 connected. A direct pressure medium loading the locking link 22 and a control port 52 of the valve function pin 20 is through the check valve 47 between the nodes 51 and 48 prevented. Will be the C port of the multi-way switching valve 21 connected to the pressure medium pump P, then the control port 46 via the pressure medium lines 23 and 5 pressurized. The first valve pin 41 is thus moved from a first switching position to a second switching position. The control port 46 is then fluidically with the second pressure medium line 42 connected so that the locking link 22 and the control port 52 via the detour of the first valve pin 41 be acted upon with pressure medium; a fluidic short circuit between the pressure medium pump P and the pressure medium reservoir T is prevented. When switching off the internal combustion engine, the multi-way switching valve 21 switched so that the C-port is fluidically connected to the pressure medium reservoir T. The excess pressure fluid from the locking link 22 can first over the first pressure medium line 23 , via the check valve 47 and drain the C-port into the pressure medium reservoir T. At the same time the control port 46 via the pressure medium line 5 fluidly relieved, so that the first valve pin 41 is moved from a second to a first switching position. In the first switching position of the first valve pin 41 Here, too, the third pressure medium line 43 over the recording room 45 fluidically with the fourth pressure medium line 44 connected. The pressure medium from the first pressure medium line 23 Thus, even in this embodiment faster via the third and fourth pressure medium line 43 and 44 flow into the pressure medium reservoir T.

LIST OF REFERENCE NUMBERS

1

 Pressure medium line

2

 Pressure medium line

3

 Pressure medium line

4

 Pressure medium line

5

 Pressure medium line

6

 Pressure medium line

7

 Pressure medium line

8th

 Pressure medium line

9

 check valve

10

 check valve

11

 wing

12

 wing

13

 wing

14

 valve means

15

 valve means

16

 stator

17

 rotor

18

 locking pin

19

 locking pin

20

 Valve function pin

21

 Multi-way switch valve

22

 locking link

23

 First pressure medium line

23a

 first section

23b

second subsection

24

 working chamber

25

 working chamber

26

 working chamber

27

 working chamber

28

 working chamber

29

 pressure chamber

30

 pressure chamber

31

 pressure chamber

32

 working chamber

33

 Center locking device

34

 Pressure medium line

35

 Pressure medium line

36

 rotor hub

37

 Pressure medium line

38

 Pressure medium line

39

 Pressure medium line

40

 Pressure medium line

41

 First valve pin

42

 Second pressure medium line

43

 Third pressure medium line

44

 Fourth pressure medium line

45

 accommodation space

46

 control port

47

 check valve

48

 junction

49

 junction

50

 ring groove

51

 junction

52

 control port

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102008011915 A1 [0005]
• DE 102005011916 A1 [0005]

Claims (10)

Camshaft adjusting device with - a Flügelzellenversteller with - a connectable to a crankshaft of an internal combustion engine stator ( 16 ) and - one in the stator ( 16 ) rotatably mounted, connectable to a camshaft rotor ( 17 ), wherein - on the stator ( 16 ) a plurality of webs are provided, which an annular space between the stator ( 16 ) and the rotor ( 17 ) into a plurality of pressure chambers ( 29 . 30 . 31 ), where - the rotor ( 17 ) a rotor hub ( 36 ) and a plurality of the rotor hub ( 36 ) radially outwardly extending wings ( 11 . 12 . 13 ), which the pressure chambers ( 29 . 30 . 31 ) in two groups of each acted upon by a pressure medium in a pressure medium circuit or flowing out pressure medium working chambers ( 24 . 25 . 26 . 27 . 28 . 32 ) with a different effective direction, and - a center locking device ( 33 ) for locking the rotor ( 17 ) in a center locking position with respect to the stator ( 16 ), wherein the center locking device ( 33 ) by pressurizing a locking link ( 22 ) is unlockable, and - at least one in the rotor ( 17 ) arranged valve pin, wherein - the valve pin not for locking the stator ( 16 ) opposite the rotor ( 17 ), and - in response to the switching position of the valve pin at a rotational movement from a stop position "early" or "late" in the center locking position at least two oppositely acting working chambers ( 24 . 25 . 26 . 27 . 28 . 32 ) are fluidically connectable, characterized in that - a first pressure medium line ( 23 ) exclusively in dependence on the switching position of at least one first valve pin ( 41 ) is connectable to a pressure medium reservoir (T). Camshaft adjusting device according to claim 1, characterized in that - a receiving space ( 45 ) for the first valve pin ( 41 ) with a second, third and fourth pressure medium line ( 42 . 43 . 44 ) is fluidically connected, wherein - the second and the third pressure medium line ( 42 . 43 ) fluidically with the first pressure medium line ( 23 ), and - the fourth pressure medium line ( 44 ) is fluidically connected to the pressure medium reservoir (T). Camshaft adjusting device according to claim 2, characterized in that - at the receiving space ( 45 ) a control port ( 46 ) is provided, the fluidically with the first pressure medium line ( 23 ) connected is. Camshaft adjusting device according to one of claims 2 or 3, characterized in that - the first valve pin ( 41 ) can assume at least two switching positions, wherein - in a first switching position, the second pressure medium line ( 42 ) fluidically with the fourth pressure medium line ( 44 ), and - in a second switching position, the third pressure medium line ( 43 ) with the control port ( 46 ) connected is. Camshaft adjusting device according to one of claims 3 or 4, characterized in that - the first valve pin ( 41 ) is moved against the spring force from the first to the second switching position, when at the control port ( 46 ) a defined pressure level is exceeded. Camshaft adjusting device according to one of the preceding claims, characterized in that - in the first pressure medium line ( 23 ) a check valve ( 47 ) arranged exclusively in the direction of a multi-way switching valve ( 21 ) can be flowed through. Camshaft adjusting device according to one of the preceding claims, characterized in that - the first valve pin ( 31 ) in the rotor hub ( 36 ) is provided. Camshaft adjusting device according to one of claims 3 to 7, characterized in that - the control port ( 46 ) by the locking link ( 22 ) is formed. Camshaft adjusting device according to one of claims 3 to 7, characterized in that - the control port ( 46 ) fluidically from the locking link ( 22 ) is decoupled. Camshaft adjusting device according to one of claims 1 to 6, characterized in that - the first valve pin ( 46 ) by at least one valve device ( 14 . 15 ) in one of the wings ( 11 . 12 . 13 ) is formed.

Images