US20080245324A1

US20080245324A1 - Control Valve

Info

Publication number: US20080245324A1
Application number: US11/720,465
Authority: US
Inventors: Jens Hoppe; Martin Stief; Markus Kinscher
Original assignee: Schaeffler KG
Current assignee: IHO Holding GmbH and Co KG
Priority date: 2004-12-07
Filing date: 2005-11-08
Publication date: 2008-10-09
Also published as: EP1825106B1; CN101072927A; JP4982868B2; KR101239610B1; DE102004058767A1; JP2008523294A; CN101072927B; KR20070085766A; WO2006061071A1; EP1825106A1

Abstract

A control valve (101) for the control of a hydraulic device for changing the control times of gas exchange valves of an internal combustion engine is provided, The control valve (101) is located in a valve housing (106) and an elastic seal element (124) is provided at an axial end thereof. The elastic seal element (124) secures function by prevention of leakage flow between pressure medium channels (113) and the pressure medium channels (113) and the drain connector (T). Also provided is an elastic seal ring (124) provided as a sealing ring with two conical regions (129, 131).

Description

BACKGROUND

The invention relates to a sealing element according to the preamble of Claim 1 and to a control valve for controlling the supply and discharge flow of a pressure medium to and from a device for changing the control times of an internal combustion engine according to the preamble of Claim 4.
In internal combustion engines, camshafts are used for actuating the gas-exchange valves. Camshafts are installed in the internal combustion engine, such that cams installed on these camshafts contact cam followers, for example cup tappets, rocker arms, or finger levers. If a camshaft is set in rotation, then the cams roll on the cam followers, which in turn actuate the gas-exchange valves. Thus, both the opening period and also the opening amplitude, as well as the opening and closing times of the gas-exchange valves are set through the position and the shape of the cam.
Modern engine concepts allow variable valve train designs. On one hand, the valve lift and valve opening period should be made variable up to complete shutdown of individual cylinders. For this purpose, concepts such as switchable cam followers or electrohydraulic or electrical valve actuators are provided. Furthermore, it has been shown to be advantageous to be able to influence the opening and closing times of the gas-exchange valves during the operation of the internal combustion engine. Here it is especially desirable to influence the opening or closing times of the intake or exhaust valves separately, in order, for example, to selectively set a defined valve overlap. By setting the opening or closing times of the gas-exchange valves as a function of the current engine-map range, for example, the current rotational speed or the current load, the specific fuel consumption can be lowered, which has a positive effect on the exhaust-gas behavior and increases the engine efficiency, the maximum torque, and the maximum output.
The described variability of the gas-exchange valve control times is achieved through a relative change of the phase position of the camshaft relative to the crankshaft. Here, the camshaft is usually in a driven connection with the crankshaft via a chain drive, belt drive, gearwheel drive, or equivalent drive concepts. Between the chain drive, belt drive, or gearwheel drive driven by the crankshaft and the camshaft there is a device for changing the control times of an internal combustion engine, which transmits the torque from the crankshaft to the camshaft. Here, this device is constructed such that during the operation of the internal combustion engine, the phase position between the crankshaft and camshaft is held reliably and, if desired, the camshaft can be rotated within a certain angular range relative to the crankshaft.
In internal combustion engines with a camshaft for each of the intake and exhaust valves, these can each be equipped with a camshaft adjuster. Therefore, the opening and closing times of the intake and exhaust gas-exchange valves can be shifted in time relative to each other and the valve overlaps are set selectively.
The seat of modern camshaft adjusters is usually located on the drive-side end of the camshaft. The camshaft adjuster, however, can also be arranged on an intermediate shaft, a non-rotating component, or the crankshaft. It is comprised of a drive wheel, which is driven by the crankshaft at a fixed phase relationship to the crankshaft, a driven part in drive connection with the camshaft, and an adjustment mechanism transmitting the torque from the drive wheel to the driven part. The drive wheel can be constructed in the case of a camshaft adjuster not arranged on the crankshaft as a chain, belt, or gearwheel and is driven by the crankshaft by means of a chain drive, belt drive, or gearwheel drive. The adjustment mechanism can be operated electrically, hydraulically, or pneumatically.
The so-called axial-piston adjuster and rotary-piston adjuster represent two preferred embodiments of hydraulically adjustable camshaft adjusters.
For axial piston adjusters, the drive wheel is connected to a piston and this is connected to the driven part via spiral gearing. The piston separates a hollow space formed by the driven part and the drive wheel into two pressure chambers arranged axially relative to each other. Now if one pressure chamber is charged with pressure medium, while the other pressure chamber is connected to a tank, then the piston is displaced in the axial direction. The axial displacement of the piston is converted by the spiral gearing into a relative rotation of the drive wheel relative to the driven part and thus of the camshaft relative to the crankshaft.
A second embodiment of hydraulic camshaft adjusters is the so-called rotary-piston adjuster. In these adjusters, the drive wheel is locked in rotation with a stator. The stator and a rotor are concentric to each other, wherein the rotor is connected with a non-positive, positive, or form fit, for example, by means of an interference fit, a screw or weld connection with a camshaft, an extension of the camshaft, or an intermediate shaft. In the stator there are several hollow spaces, which extend radially outwards starting from the rotor, spaced apart in the peripheral direction. The hollow spaces are pressure sealed in the axial direction by a side cover. A vane, which is connected to the rotor and which separates each hollow space into two pressure chambers, extends into each of these hollow spaces. Through selective connection of the individual pressure chambers with a pressure medium pump or with a tank, the phase of the camshaft relative to the crankshaft can be set or held.
For controlling the camshaft adjuster, sensors detect the characteristic data of the engine, for example, the load state and the rotational speed. This data is fed to an electronic control unit, which determines a desired value of the relative phase angle between the camshaft and crankshaft after comparing the data with a characteristic data map of the internal combustion engine. By means of sensors, for example Hall sensors, the actual value of the phase angle and a deviation of the actual value from the desired value are determined. Then the control command is led to a control unit of the control valve, which controls the supply and discharge flow of pressure medium to and from the various pressure chambers and thus controls the adjustment of the phase position of the camshaft.
To adjust the phase position of the camshaft relative to the crankshaft, in hydraulic camshaft adjusters, one of the two pressure chambers acting against each other in a hollow space is connected to a pressure medium pump and the other is connected to the tank. The supply of pressure medium to one chamber in connection with the discharge of pressure medium from the other chamber displaces the piston separating the pressure chambers in the axial direction, whereby the camshaft is rotated relative to the crankshaft in axial piston adjusters via the spiral gearing. In rotary piston adjusters, the pressure loading of one chamber and the pressure relieving of the other chamber displaces the vane and thus directly rotates the camshaft relative to the crankshaft. To keep the phase position, both pressure chambers are either connected to the pressure medium pump or separated both from the pressure medium pump and also from the tank.
The control of the pressure medium flows to and from the pressure chambers is realized by means of a control valve, usually a 4/3 proportional valve. A valve housing is provided with a connection for each pressure chamber (work connection), a connection to the pressure medium pump, and at least one connection to a tank. Within the essentially hollow cylindrical valve housing there is an axially displaceable control piston. The control piston can be brought axially into any position between two defined end positions against the spring force of a spring element by means of an adjustment unit, for example, an electromagnetic or hydraulic adjustment unit. The control piston is further provided with ring grooves and control edges, whereby the individual pressure chambers can be connected selectively to the pressure medium pump or to the tank. Likewise a position of the control piston can be provided, in which the pressure medium chambers are separated both from the pressure medium pump and also from the pressure medium tank.
Such control valves can be constructed as a central valve or as an insert valve. In the case of a central valve, this is arranged within the camshaft or an extension of the camshaft in the area of the camshaft adjuster. In the case of an insert valve, a surrounding construction of the internal combustion engine is provided with a valve receptacle, in which the control valve is inserted. In the casing surface of the valve receptacle, usually constructed as a bore, there are pressure medium lines, which communicate with the pressure medium connections of the control valve. Such a surrounding construction can be, for example, a cylinder head or a cylinder head cover.
In DE 102 23 431 B4, such a device with a control valve in an insert construction is shown. The device is comprised of a camshaft-fixed driven unit, a drive unit driven by the crankshaft, and two side covers. The drive unit is arranged coaxial to the driven unit and is provided with several recesses spaced apart in the peripheral direction. The recesses are pressure sealed by the drive unit, the driven unit, and the side covers and thus form pressure spaces. A vane extends into each pressure space, wherein each vane is arranged in a vane groove formed on the driven unit. Each vane divides a pressure space into two pressure chambers acting against each other. The pressure chambers communicate via pressure medium lines formed in a camshaft by means of rotary feedthroughs with other pressure medium lines formed in a cylinder head or a cylinder head cover.
The other pressure medium lines can be connected by means of a control valve, in this case a 4/3 directional control valve, selectively to a pressure medium reservoir or to a pressure medium pump. The control valve is composed of an adjustment unit and a valve body. The valve body is surrounded by an adapter sleeve, wherein this sleeve is arranged in a bore of a cylinder head cover. In the adapter sleeve, three radial openings spaced apart axially and in the peripheral direction relative to each other are formed, which are used as pressure medium connections. A fourth pressure medium connection is formed in the axial direction on the end of the valve body facing away from the adjustment unit. Each radial opening is connected to a pressure medium line via a rising channel. Pressure medium is led via a pressure medium line to the middle radial opening in the axial direction and from there into the interior of the sleeve, wherein the pressure medium flow is guided dependent on the control position of the control valve to one of the two other radial openings. From there the pressure medium is led via another rising line to a pressure medium line, which communicates with one of the rotary feedthroughs and also with a firsts group of pressure chambers.
In an analogous way, pressure medium is led from a second group of pressure chambers via the rotary feedthrough and pressure medium lines to another rising line, which opens into the third opening. From there the pressure medium is led via the control valve to the axial discharge connection. The rising lines are constructed as grooves constructed in the bore in the cylinder head cover and open to the adapter sleeve. Furthermore, the rising lines are sealed against each other, so that the outer diameter of the adapter sleeve is adapted to the inner diameter of the bore. The pressure medium lines communicating with the rising lines are in this embodiment constructed as grooves formed in the cylinder head cover and open to the cylinder head. To allow discharge of the pressure medium forced from the pressure chambers, the cylinder head is provided with a discharge bore coaxial to the bore formed in the cylinder head cover.
To prevent leakage between the rising lines and the discharge bore, the inner diameter of the bore and the discharge bore are identical and the adapter sleeve extends at least partially into the adapter bore. The adapter sleeve now forms a sealed contact on the casing surface of the discharge bore, whereby discharge of the pressure medium from the rising lines via the discharge bore into the interior of the cylinder head is prevented. Slight offset of the bores causes damage to the adapter sleeve during assembly, which can lead to loss of the sealing effect between the components.
To guarantee the sealing function between the rising channels and the discharge bore, an exact coaxial alignment of the bore to the discharge bore and an exact adaptation of the adapter sleeve diameter to the inner diameter of the discharge bore is necessary. This is possible only with very high expense due to the tolerances inevitably appearing in the production process of the individual components.

SUMMARY

The invention is based on the objective of avoiding these mentioned disadvantages and providing a sealing arrangement for a control valve, which is not susceptible to tolerances appearing in the system. Furthermore, a sealing element is provided, which is used in this sealing arrangement.
A control valve for controlling the supply and discharge flow of pressure medium to and from a device for changing the control times of an internal combustion engine comprises, among other things, an essentially cylindrical valve housing, on which pressure medium connections are formed, and an axially displaceable control piston arranged within the valve housing. Here, a connection between the different pressure medium connections can be established or separated as a function of the position of the control piston. The valve housing is arranged within a valve receptacle, wherein the insert depth of the valve housing into the valve receptacle is limited by an axial stop constructed in the valve receptacle.
The objective is met according to the invention in that the axial stop is constructed as a circular or circular ring-shaped wall, which extends radially inwards starting from an inner casing surface of the valve receptacle and that between the valve housing and the axial stop of the valve receptacle there is a sealing element.
Such a control valve comprises a cylindrical valve housing and a control piston arranged axially displaceable in the valve housing. The valve housing is provided with radial openings, which are used as pressure medium connections. By means of an adjustment unit, the control piston within the valve housing can be brought into any position between two end stops. In this way, the control piston connects or separates various pressure medium connections based on the relative position to the valve housing. The control piston can be in direct contact with the valve housing. Another possibility consists in providing, as shown in DE 102 23 431, a hollow control sleeve between the valve housing and the control piston. The inner diameter of the control sleeve is adapted to the outer diameter of the control piston and the outer diameter of the control sleeve is adapted to the inner diameter of the valve housing. Furthermore, the outer casing surface of the control sleeve is provided with several ring grooves, which communicate on one side with the pressure medium connections and on the other side via radial openings with the interior of the control sleeve. Through axial shifting of the control piston, connections between the ring grooves, and thus the pressure medium connections, and optionally with an axial pressure medium connection, can be established or separated.
Such control valves are arranged in valve receptacles, in which pressure medium channels are formed, which communicate with the pressure medium connections. The pressure chambers of the camshaft adjuster are connected selectively via the pressure medium channels with a pressure medium pump or a pressure medium reservoir. Such valve receptacles can be formed, for example, in a cylinder head or a cylinder head cover. In this case, one talks of an insert valve. Another possibility is to use the control valve as a central valve. In this case, it is arranged in a valve receptacle in the camshaft and rotates with the camshaft during the operation of the internal combustion engine.
In both cases, the valve receptacle is constructed as a cylindrical bore. The outer diameter of the valve housing is adapted to the inner diameter of the bore, whereby the pressure medium connections are sealed against each other. Within the bore there is an axial stop for the valve housing. The axial stop can be constructed as a wall limiting the bore. A diameter narrowing of the bore is also conceivable. In this case, the bore is constructed with a stepped cross section, whereby a ring section is constructed, which is used as an axial stop for the valve housing. Furthermore, between the axial stop and the valve housing there is a sealing ring, which prevents leakage currents in the axial direction.
The radial ring sealing point described in DE 102 23 431 is displaced in the axial direction by this projection, whereby the effects by tolerances in the dimensions of the control valve are not critical.
In an advantageous improvement of the invention, it is provided that the axial stop-side end of the valve housing is constructed with an area reduced in outer diameter, wherein the sealing element is arranged at least partially in the area reduced in outer diameter. The sealing element is further constructed as a sealing ring with an outer and an inner casing surface.
The area reduced in outer diameter simplifies the mounting of the sealing element and the control valve in the valve receptacle. The inner diameter of the sealing element constructed as a sealing element is adapted to the outer diameter of the area reduced in outer diameter. The sealing ring is placed in this area on the control valve and is positioned with it together in the valve receptacle. Thus, due to the guidance and centering experienced by the sealing element by means of the control valve, incorrect mounting is prevented and the sealing effect is more process reliable.
It can be further provided that the sealing element is composed of an elastomer. In the case of a valve housing with an area reduced in outer diameter on the axial stop-side end, the sealing ring contacts the outer casing surface of this area. Furthermore, it is clamped in the axial direction by the valve housing and the axial stop. During the mounting, the sealing ring is pressed by the valve housing against the axial stop. In this way, it deforms elastically, wherein deformation radially inwards is prevented by the valve housing. The elastic deformation thus obtains a “preferred direction,” namely radially outwards, against the inner casing surface of the valve receptacle. Therefore, the sealing effect is increased or reached significantly earlier. Another advantage in the use of an elastic sealing ring is to be seen in that axial tolerances can be compensated through its deformability.
The elastomer can be, for example, a fluoro-rubber or an acrylonitrile butadiene rubber. These materials are very well suited due to their high resistance relative to environmental influences in internal combustion engines, such as high temperatures and contact with motor oil.
In another realization of the invention, the valve receptacle is assembled from a first and a second bore, wherein the bores are embodied in different surrounding constructions, at least approximately coaxial and adjacent to each other. One example for such an embodiment is the valve receptacle shown in DE 102 23 431. A bore is constructed in a cylinder head and a cylinder head cover. The two bores are arranged such that they are at least approximately coaxial to each other when the cylinder head cover is mounted on the cylinder head.
In one improvement of the invention, the axial stop can be formed at the boundary of the two surrounding constructions.
In this embodiment, the inner diameter of the second bore is smaller than that of the first bore. At the boundary between the two bores there is a step. The advantage of this variant lies in the low production costs, because the step is realized by lining up two bores of different inner diameters.
Alternatively, the axial stop is formed in the second bore in the insertion direction of the control valve. The advantage is provided in that the step-like profile can be constructed such that the sealing element at the boundary of the two surrounding constructions can contact the inner casing surfaces of the bores.
In this embodiment according to the invention, because the outer casing surface of the valve housing no longer provides the sealing function at the boundary of the surrounding constructions, the inner diameter of the second bore at the boundary between the surrounding constructions can be greater than the inner diameter of the first bore and thus than the outer diameter of the valve housing. Thus, even for a slight offset of the bores relative to each other, non-destructive assembly of the control valve in the valve receptacle is guaranteed.
It is further provided that the axial stop is arranged and the sealing element is constructed so that the sealing element at the boundary of the two surrounding constructions contacts the valve receptacle. Any possible leakage paths created by edges deviating from the rectangular shape are reliably blocked by the elastic deformation of the sealing element.
In another advantageous improvement of the invention, the transition area of the valve housing to the diameter-reduced area is at least partially conical. Furthermore, the sealing element at its inner casing surface is provided with a first conical area, wherein this is adapted to the transition area of the valve housing.
The valve housing is comprised of a first and a second cylindrical area. The first cylindrical area forms a sealed contact on the inner wall of the first bore. The second area involves the area reduced in outer diameter. A conical transition area is formed at the transition from the first to second area. Here the entire diameter reduction can be bridged by means of the conical area. It is also conceivable that starting from the first area, the valve housing extends radially inwards before it transitions into the conical area, which flows into the area reduced in outer diameter. The sealing ring is arranged in this transition area, wherein its contours contacting the valve housing are adapted to the contours of the valve housing, especially the conical area. During the mounting of the control valve in the valve receptacle, the valve housing exerts a force on the sealing ring. Due to the pressure surface that is not parallel to the axial stop, a force is applied to the sealing ring both in the axial and also radial directions. Consequently, a better sealing effect is achieved in the radial direction.
In an advantageous improvement of the invention, the outer casing surface of the sealing element is provided with a second conical area at the end contacting the axial stop, so that an annular hollow space is produced between the sealing element and the axial stop. If larger axial tolerances have to be compensated, for example, and thus the valve must be positioned farther within the valve receptacle, then the sealing ring can bulge into the hollow space while maintaining its sealing function. Larger production tolerances can be compensated and thus costs can be saved.
Further proposed is a sealing element in the form of a sealing ring for sealing an axial end of a control valve of a device for changing the control times of gas-exchange valves with an inner casing surface and an outer casing surface. According to the invention, the objective is met in that the inner and the outer casing surfaces are provided with a conical area at each of its ring edges. In this way the two conical areas are formed at ring edges of the sealing ring offset relative to each other in the axial direction. One of the conical areas is provided for contacting a conical area of a component, which is to seal the sealing ring against a second component. This is meant especially for a sealing assembly of a component within a bore, wherein the sealing ring is charged with an axially directed force. The conical contact surface of the component converts the axially directed force into radial and axial force components, whereby the sealing ring deforms in the radial direction and thus increases the sealing effect. Through the conical construction of another ring edge, a ring-shaped hollow space is maintained, in which the sealing ring can bulge under the effect of forces. Due to this hollow space, large axial tolerances can be compensated without negatively affecting the sealing effect.

BRIEF DESCRIPTION OF THE DRAWINGS

Additional features of the invention emerge from the following description and from the drawings, in which embodiments of the invention are shown simplified. Shown are:

FIG. 1 a longitudinal cross-sectional view through a device for changing the control times of an internal combustion engine with pressure medium circuit,

FIG. 2 a cross sectional view through the device shown in FIG. 1 along the line II-II,

FIG. 3 a longitudinal cross-sectional view through a control valve mounted in a valve receptacle according to a first sealing concept according to the invention,

FIG. 4 a cross-sectional view along the line IV-IV from FIG. 3,

FIG. 5 a longitudinal cross-sectional view through a control valve mounted in a valve receptacle according to a second sealing concept according to the invention,

FIG. 6 a cross-sectional view along the line VI-VI from FIG. 5,

FIG. 7 a longitudinal cross-sectional view through a sealing ring according to the invention, and

FIG. 8 a cross-sectional view along line VIII-VIII of FIG. 7.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIGS. 1 and 2 show a device 1 for changing the control times of an internal combustion engine. The device 1 essentially comprises a stator 2, and a rotor 3 arranged concentrically to this stator. A drive wheel 4 is locked in rotation with the stator 2 and constructed as a chain wheel in the illustrated embodiment. Embodiments of the drive wheel 4 as a belt or gearwheel are also conceivable. The stator 2 is supported rotatably on the rotor 3, wherein five recesses 5 spaced apart in the peripheral direction are provided in the illustrated embodiment on the inner casing surface of the stator 2. The recesses 5 are limited in the radial direction by the stator 2 and the rotor 3, in the peripheral direction of two side walls 6 of the stator 2, and in the axial direction by a first and a second side cover 7, 8. Each of the recesses 5 is pressure sealed in this way. The first and the second side covers 7, 8 are connected to the stator 2 by means of connection elements 9, for example, screws.
On the outer casing surface of the rotor 3 there are axial vane grooves 10, wherein a radially extending vane 11 is arranged in each vane groove 10. A vane 11 extends into each recess 5 starting from the appropriate vane groove 10, wherein the vanes 11 contact in the radial direction the stator 2 and in the axial direction the side covers 7, 8. Each vane 11 divides a recess 5 into two pressure chambers 12, 13 working against each other. To guarantee a pressure-sealed contact of the vane 11 on the stator 2, between the groove bases 14 of the vane grooves 10 and the vanes 11 there are leaf spring elements 15, which apply a force on the vanes 11 in the radial direction.
By means of first and second pressure medium lines 16, 17, the first and second pressure chambers 12, 13 are connected via a control valve 18 to a pressure medium pump 19 or a tank 20. In this way, an adjustment drive is formed, which allows a relative rotation of the stator 2 relative to the rotor 3. Here, either all of the first pressure chambers 12 are connected to the pressure medium pump 19 and all of the second pressure chambers 13 are connected to the tank 20, or there is the exact opposite configuration. If the first pressure chambers 12 are connected to the pressure medium pump 19 and the second pressure chambers 13 are connected to the tank 20, then the first pressure chambers 12 expand at the cost of the second pressure chambers 13. This produces a shift of the vanes 11 in the peripheral direction, in the direction shown by the arrow 21. By shifting the vanes 11, the rotor 3 is rotated relative to the stator 2.
The stator 2 is driven by the crankshaft in the shown embodiment by a not-shown chain drive attaching to its drive wheel 4. The drive of the stator 2, by a belt or gearwheel drive, is also conceivable. The rotor 3 is connected by a non-positive, positive, or form fit, for example, by means of an interference fit or by a screw connection by means of a central screw, to a not-shown camshaft. From the relative rotation of the rotor 3 relative to the stator 2, due to the supply or discharge of pressure medium towards or from the pressure chambers 12, 13, a phase shift results between the camshaft and crankshaft. Through targeted feeding and discharge of pressure medium into and out of the pressure chambers 12, 13, the control times of the gas-exchange valves of the internal combustion engine can be varied selectively.
The pressure medium lines 16, 17 are constructed in the shown embodiment as channels within the rotor 3, which extend from a central bore 22 of the rotor 3 to its outer casing surface. Within the central bore 22 there can be a not-shown central valve, by means of which the pressure chambers 12, 13 can be connected selectively to the pressure medium pump 19 or to the tank 20. Another possibility is provided in arranging a pressure medium distributor within the central bore 22, which connects the pressure medium lines 16, 17 via pressure medium channels and ring grooves to pressure medium connections A, B, P, T of a control valve 18 attached on the outside.
The essentially radial side walls 6 of the recesses 5 are provided with formations 23, which extend in the peripheral direction into the recesses 5. The formations 23 are used as stops for the vanes 11 and guarantee that the pressure chambers 12, 13 can be supplied with pressure medium even when the rotor 3 assumes one of its two extreme positions relative to the stator 2, in which the vanes 11 contact one of the side walls 6.
For inadequate supply of pressure medium to the device 1, for example, during the startup phase of the internal combustion engine, the rotor 3 moves uncontrollably relative to the stator 2 due to the alternating and dragging moments that the camshaft exerts on the rotor. In a first phase, the reactive torque of the camshaft forces the rotor 3 relative to the stator 2 in a peripheral direction that lies opposite the rotational direction of the stator 2 until these contact the side walls 6. Then the alternating moments exerted by the camshaft on the rotor 3 lead to back and forth oscillations of the rotor 3 and thus of the vanes 11 in the recesses 5 until at least one of the pressure chambers 12, 13 is filled completely with pressure means. This leads to higher wear and to the development of noise in the device 1. To prevent these results, a locking element 24 is provided in the device 1. For this purpose, a pot-shaped piston 26 is arranged in an axial bore 25 of the rotor 3. A first spring 27 applies a force to this piston in the axial direction. The first spring 27 is supported in the axial direction on one side on a ventilation element 28 and is arranged with its axial end facing away from this ventilation element within the pot-shaped piston 26. In the first side cover 7 there is a connecting rod 29, such that the piston 26 can engage this connecting rod in at least one relative position of the rotor to the stator. In this position, the piston 26 is forced into the connecting rod 29 by the first spring 27 if there is inadequate supply of pressure medium to the device 1. In this state, the rotor 3 is locked in this position relative to the stator 2. The locking position primarily corresponds to the position that is to be assumed during the startup of the internal combustion engine. Furthermore, means are provided to pull the piston 26 back into the axial bore 25 for an adequate supply of pressure medium to the device 1 and thus to cancel the locking. This is typically implemented with pressure medium, which is led via not-shown pressure medium lines into a recess 30, which is formed on the cover-side end of the piston 26. To be able to discharge leakage oil from the spring space of the axial bore 25, the ventilation element 28 is provided with axial grooves, along which the pressure medium can be led to a bore in the second side cover 8.
In FIG. 1, the pressure medium circuit 31 is also shown. From a tank 20, a supply connection P of a control valve 18 is supplied with pressure medium by means of a pressure medium pump 19. Simultaneously, pressure medium is led by the control valve 18 into the tank 20 via a discharge connection T. The control valve 18 further has two work connections A, B, with the first work connection A communicating with the first pressure chambers 12 and the second work connection B communicating with the second pressure chambers 13. By means of an electromagnetic adjustment device 32, which acts against the spring force of a second spring 33, the control valve 18 can be brought into three positions. In a first position of the control valve 18, which corresponds to a non-powered state of the adjustment device 32, the first work connection A and thus the first pressure chambers 12 are connected to the discharge connection T. Simultaneously, the supply connection P communicates with the second work connection B and thus with the second pressure chambers 13. Thus, while pressure medium is discharged from the first pressure chambers 12, pressure medium are led to the second pressure chambers 13, whereby the vanes 11 are shifted in the peripheral direction. This produces a change of the phase position between the rotor 3 and the stator 2 and thus between the camshaft and crankshaft.
In a middle position, both the first work connection A and also the second work connection B are separated both from the supply connection P and also from the discharge connection T. Pressure medium can flow neither to nor from the pressure chambers 12, 13 and the phase position of the camshaft is held relative to the crankshaft. An alternative possibility is provided by connecting both work connections A, B to the supply connection P, in order to compensate for leakage appearing in the device 1.
In a third position of the control valve 18, the supply connection P is connected to the first work connection A and thus to the first pressure chamber 12, while the second pressure chamber 13 is connected to the second work connection B to the discharge connection T. Analogous to the first control position of the control valve 18, the phase position of the camshaft relative to the crankshaft is changed only in the opposite direction.
FIG. 3 shows a control valve 101 according to the invention, which has an adjustment device 102, an essentially hollow cylindrical control housing 103, a similarly essentially hollow cylindrical control piston 104, and a similarly essentially hollow cylindrical valve housing 105. The control housing 103 is arranged stationary within the valve housing 105. Here, the inner diameter of the valve housing 105 is adapted to the outer diameter of the control housing 103. Furthermore the control piston 104 is displaceable axially within the control housing 103, wherein the outer diameter of the control piston 104 is adapted to the inner diameter of the control housing 103.
The valve housing 105 is arranged within a valve receptacle 106. The valve receptacle 106 is assembled from two bores 107, 108, which are formed in two surrounding constructions 109, 110. The first surrounding construction 109 is fixed on the second surrounding construction 110 and the bores 107, 108 are constructed and arranged such that these are at least approximately coaxial to each other. The inner diameter of the second bore 108 is smaller in this embodiment than the inner diameter of the first bore 107. Therefore, at the boundary between the first surrounding construction 109 and the second surrounding construction 110 there is a circular ring-shaped axial stop 111, which limits the insertion depth of the control valve 101.
The valve housing 105 is provided on its axial stop-side end with an area 112 reduced in outer diameter, wherein the outer diameter of the area 112 reduced in outer diameter is smaller than the inner diameter of the second bore 108. Furthermore, in this embodiment the transition to the area 112 reduced in outer diameter has a stepped construction. The valve housing 105 passes through the first bore 107 and extends with its diameter-reduced area 112 at least partially into the second bore 108. Here, the outer diameter of the valve housing 105 is adapted to the inner diameter of the valve receptacle 106.
Three pressure medium channels 113 are formed at the boundary between the first and second surrounding constructions 109, 110. The pressure medium channels 113 are constructed in the form of grooves, which are formed either in the surface of the first or second surrounding constructions 109, 110. Each of the pressure medium channels 113 opens into a rising groove 114 a, 114 b, 114 p, which are formed in the casing surface of the first bore 107. The rising grooves 114 a, 114 b, 114 p are offset relative to each other in the peripheral direction of the first bore 107 and extend essentially in the axial direction of the valve housing 105. Each of the rising grooves 114 a, 114 b, 114 p communicates via corresponding radial openings 115 a, 115 b, 115 p, which are formed in the valve housing 105 and which are used as work connections A, B, and supply connection P, with the interior of the valve housing 105.
The outer casing surface of the control housing 103 is provided with three ring grooves 116 a, 116 b, 116 p offset relative to each other axially. Here, the rising grooves 114 a, 114 b, 114 p, the radial openings 115 a, 115 b, 115 p, and the ring grooves 116 a, 116 b, 116 p are arranged so that the first rising groove 114 a communicates by means of the first radial opening 115 a exclusively with the first ring groove 116 a, the second rising groove 114 b communicates by means of the second radial opening 115 b exclusively with the second ring groove 116 b, and the third rising groove 114 p communicates by means of the third radial opening 116 p exclusively with the third ring groove 116 p. Each of the ring grooves 116 a, 116 b, 116 p further communicates by means of openings 117 a, 117 b, 117 p formed in their groove bases with the interior of the control housing 103.
The control piston 104 arranged in the interior of the control housing 103 can be displaced within the control housing 103 axially by means of an adjustment device 102 via a push rod 119 against the force of a first spring element 120. The control piston 104 is provided with two control sections 121, wherein the outer periphery of the control sections 121 is adapted to the inner periphery of the control housing 103. The control sections 121 can be made as separate components and mounted on the control piston 104 or constructed in one piece with this piston as shown in FIG. 3. Outside of the control sections 121 the outer diameter of the control piston 104 has a smaller construction. The control sections 121 are constructed and arranged on the control piston 104 such that a fourth ring groove 122 is formed, which connects the first or second ring groove 116 a, 116 b to the third ring groove 116 p after the adjustment of the control piston 104 relative to the control housing 103.
The control piston 104 further has an open construction on its end attaching to the first spring element 120. Therefore, a connection between the interior of the control piston 104 and the second bore 108 is produced and thus describes a discharge connection T. Fourth openings 123 are formed on the push rod-side end of the control piston 104, whereby the interior of the control piston 104 is connected hydraulically with the outside of the control piston 104. The fourth openings 123 are located in the shown embodiment outside of the fourth ring groove 122 in the outer casing surface of the control piston 104.
By means of the adjustment device 102, the control piston 104 can be moved via the push rod 119 within the control housing 103 into any position between two maximum values. Here, the first spring element 120 exerts a restoring force on the control piston 104. As a control device 102, for example, hydraulic adjustment devices or, like in the illustrated embodiment, electromagnetic adjustment devices can be used. The electromagnetic adjustment device 102 is comprised of a coil that is arranged in a magnetic field of one or more permanent magnets. A power-supply unit is allocated to the coil, by means of which this coil can be excited with an electric current. Here, several possibilities for exciting the coil are conceivable. One possibility would be, for example, to vary the position of the coil within the magnetic field through variable current intensities, wherein high current intensities would correspond to a large deflection and low current intensities would correspond to a small deflection. Also conceivable is to excite the coil by means of pulsed currents. For example, a rectangular voltage between the values 0V and a constant voltage V₀can be applied to the electrical poles of the coil. The deflection of the coils and thus the control piston 104 is now defined by the ratio of the time intervals, in which the voltage V₀or no potential difference is applied to the electrical poles. The greater the voltage-less intervals are, the smaller the deflection of the coil. The longer the time intervals are in which the voltage V₀is applied, the greater the deflection.
In the shown embodiment in FIG. 3 and FIG. 4, a 4/3 direction control valve with four pressure medium connections A, B, P, T is shown, wherein the control piston 104 can be located essentially in three control states. However, the invention is not limited to such a four/three direction control valve, but instead embodiments, in which a 4/4 directional control valve or other valves are used, are by all means also conceivable.
Below, the function of the 4/3 directional control valve shall be described as an example. By means of one of the pressure medium channels 113, the third rising groove 114 p is charged with pressure medium. In each control position of the control valve 101, the pressure medium is led via the third radial opening 115 p, the third ring groove 116 p, and the third openings 117 p into the fourth ring groove 122.
In a first state of the control valve 101, which corresponds to a non-powered state of the adjustment device 102, the control piston 104 is shifted by means of the spring force of the first spring element 120 into a maximum deflected position in the direction of the adjustment device 102. In this control position, the fourth ring groove 122 communicates via the first openings 117 a, the first ring groove 116 a, and the first radial opening 115 a with the first rising groove 114 a, from where the pressure medium is led to the first pressure chambers 12.
In a second control position of the control valve 101, in which the adjustment device 102 receives maximum power, the control piston 104 is deflected to a maximum extent in the direction of the first spring element 120. In this case, the fourth ring groove 122 communicates both with the third openings 117 p and also with the second openings 117 b. Pressure medium is now led via the second ring groove 116 b, the second radial opening 115 b, and the second rising groove 114 b to the corresponding pressure medium channel 113 and from there to the second pressure chambers 13.
In a third state, the control piston 104 is located in a middle position, in which the fourth ring groove 122 communicates only with the third openings 117 p. In this case, the pressure medium supply to both pressure chambers 12, 13 is blocked. Alternatively, it is likewise conceivable that, in this middle position, the fourth ring groove 122 communicates with the first, the second, and the third openings 117 a, 117 b, 117 p. In this case pressure medium is led to both pressure chambers 12, 13, whereby leakage is compensated and the phase position is held functionally locked between the camshaft and crankshaft.
In the first and second control position, the control sections 121 completely open or close the appropriate openings 117 a, 117 b. Naturally the control piston 104 can also be positioned at any position between these two extreme values, whereby the openings 117 a, 117 b are only partially opened or covered. Therefore, the flow resistance and thus the extent of pressure medium supply to the pressure chambers 12, 13 can be set.
To prevent pressure medium from being able to flow from the rising grooves 114 a, 114 b, 114 p directly into the second bore 108 and to prevent leakage flows between the rising grooves 114 a, 114 b, 114 p, especially at the boundary between the surrounding constructions 109, 110, a sealing element 124 is provided between the valve housing 105 and the axial stop 111. The sealing element 124 is constructed in the shown embodiment as an elastically deformable sealing ring and preferably from fluoro rubber or acrylonitrile butadiene rubber. Advantageously, the sealing element 124 is arranged on the area 112 of the valve receptacle 105 reduced in outer diameter. During the mounting of the control valve 101 in the valve receptacle 106, the sealing element 124 is positioned in the area 112 of the valve housing 105 reduced in outer diameter. Then the valve housing 105 is inserted and fixed in the valve receptacle 106. Through the arrangement on the area 112 reduced in outer diameter, the sealing element 124 is centered and guided during the mounting process, whereby incorrect mounting can be reliably prevented. Through the use of an elastically deformable sealing element 124, axial tolerances can be compensated.
The sealing element 124 is pressed 111 by the valve housing 105 in the installed state against the axial stop 111. Here, it is surrounded by a U shape by the axial stop 111 and the step of the area 112 of the valve housing 105 reduced in outer diameter. Due to the forces, the sealing element 124 deforms elastically and is thus pressed against the inner casing surface of the valve receptacle 106 due to the U-shaped clamping device. In this way, an optimal and early sealing effect is guaranteed in the axial direction.
Advantageously, the sealing element 124 is arranged such that it contacts the inner casing surface of the valve receptacle 106 at the boundary between the two surrounding constructions 109, 110. Therefore, any possible gaps at this boundary are closed and the sealing effect is guaranteed in the peripheral direction.
Through the construction of the second bore 108 with a small inner diameter in comparison with the first bore 107, an axial stop 111 is formed, which limits the insertion depth of the control valve 101 in the valve receptacle 106 and acts as a sealing surface in interaction with the sealing element 124. The control valve 101 engages only with its area 112 reduced in outer diameter into the second bore 108. Because this area 112 does not take on a sealing function in interaction with the inner casing surface of the second bore 108, its outer diameter can be smaller than the inner diameter of the second bore 108, which makes the system not susceptible to tolerances.
Furthermore, additional seals 125 are provided at the boundary between the control housing 103 and the valve housing 105 or the valve housing 105 and the first bore 107, which prevent leakage flows in the direction of the adjustment device 102 and thus into the engine space.
FIGS. 5 and 6 show a second embodiment of the invention. The second embodiment is identical to the first embodiment for the most part, which is shown in FIGS. 3 and 4. In contrast to the first embodiment, the second bore 108 has a stepped construction. Here, the inner diameter of a first area 126, which connects directly to the first bore 107, is larger than the inner diameter of the first bore 107. Furthermore, the inner diameter of a second area 127 adjacent to the first area 126 is smaller than the inner diameter of the first bore 107. At the transition from the first area 126 to the second area 127, an axial stop 111 is formed. The valve housing 105 passes through the first bore 107 of the first surrounding construction 109 and engages in the second surrounding construction 110. Due to the larger inner diameter of the first area 126 of the second bore 108, this is possible even for a slight offset of the bores 107, 108 relative to each other. The transition area 128 of the valve housing 105 to the diameter-reduced area 112 in not stepped in this embodiment as in the first embodiment, but instead at least partially conical. The sealing element 124 is constructed as a sealing ring and arranged in the transition area 128, wherein the form of the sealing element 124 is adapted to the shape of the transition area 128, especially its conicity 127. The inner casing surface 133 of the sealing element 124 thus has a first conical area 129, wherein the inner diameter continuously decreases starting from the end in the axial direction until it corresponds to the outer diameter of the area 112 reduced in outer diameter.
On an outer casing surface 134 of the sealing element 124, a second conical area 131 is formed, wherein this is formed on the ring edge 130 offset in the axial direction relative to the first conical area 129. The outer diameter of the sealing element 124 increases in the axial direction starting from the end until the maximum outer diameter of the sealing element 124 is reached.
The axial length of the first area 126, the area 112 reduced in outer diameter, and the sealing element 124 is constructed so that the sealing element 124 contacts both the first bore 107 and also the second bore 108 in the area of the boundary between the first surrounding construction 109 and the second surrounding construction 110.
The conical area formed in the outer casing surface of the valve housing 105 has the effect that the sealing element 124 forms a pressure sealed contact on the casing surface of the first bore 107 and the casing surface of the first area 126 of the second bore 108. Due to the shape of the sealing element 124, between the second bore 108 and the sealing element 124 there is a hollow space 132. This allows the compensation of any axial play during the mounting. In this case, the valve housing 105 can force material of the sealing element 124 into the hollow space 132, whereby the control valve 101 can be inserted in the axial direction farther into the valve receptacle 106. This hollow space 132 allows axial tolerances to be compensated to a greater extent than is allowed in the sealing element 124 shown in the first embodiment.
Obviously, the sealing element 124 of the second embodiment can also be inserted into the valve receptacle 106 of the first embodiment and vice versa. Furthermore, both sealing elements 124 and the control valve 101 can be used in a single stepped bore, which is used as the valve receptacle 106. Likewise, the sealing element 124 and the control valve 101 are inserted into a bore, which is limited by a circular ring-shaped wall extending in the radial direction.
FIGS. 7 and 8 show a sealing element 124 according to the invention in the shape of a sealing ring. A ring edge 130 of the inner 133 and the outer casing surface 134 of the sealing element 124 has a conical construction. The conicity is constructed such that the partial cross sectional shape of the sealing element 124 is reached through material removal of two edges of a rectangular surface. That is, the first conical area 129 on the inner casing surface 133 is funnel shaped and the second conical area 131 on the outer casing surface 134 is frustum shaped.
Furthermore, the sealing element 124 is composed of an elastomer. Here, a fluoro rubber or an acrylonitrile butadiene rubber can be used as the material, for example.

REFERENCE SYMBOLS

1 Device
2 Stator
3 Rotor
4 Drive wheel
5 Recesses
6 Side wall
7 First side cover
8 Second side cover
9 Connection element
10 Vane groove
11 Vane
12 First pressure chamber
13 Second pressure chamber
14 Groove base
15 Leaf spring element
16 First pressure medium line
17 Second pressure medium line
18 Control valve
19 Pressure medium pump
20 Tank
21 Arrow
22 Central bore
23 Formations
24 Locking element
25 Axial bore
26 Piston
27 First spring
28 Ventilation element
29 Connecting rod
30 Recess
31 Pressure medium circuit
32 Adjustment device
33 Second spring
A First work connection
B Second work connection
P Supply connection
T Discharge connection
101 Control valve
102 Adjustment device
103 Control housing
104 Control piston
105 Valve housing
106 Valve receptacle
107 First bore
108 Second bore
109 First surrounding construction
110 Second surrounding construction
111 Axial stop
112 Area reduced in outer diameter
113 Pressure medium channel
114 a First rising groove
114 b Second rising groove
114 p Third rising groove
115 a First radial opening
115 b Second radial opening
115 p Third radial opening
116 a First ring groove
116 b Second ring groove
116 p Third ring groove
117 a First opening
117 b Second opening
117 p Third opening
119 Push rod
120 First spring element
121 Control section
122 Fourth ring groove
123 Fourth openings
124 Sealing element
125 Seal
126 First area
127 Second area
128 Transition area
129 First conical area
130 Ring edge
131 Second conical area
132 Hollow space
133 Inner casing surface
134 Outer casing surface

Claims

1. Sealing element comprising a sealing ring for sealing an axial end of a control valve of a device for changing control times of gas-exchange valves, including an inner casing surface and an outer casing surface, the inner casing surface and the outer casing surface are provided with a conical area on each of ring edges thereof.

2. Sealing element according to claim 1, wherein the two conical areas are formed on the ring edges of the sealing element offset relative to each other in an axial direction.

3. Control valve for controlling a supply and discharge of pressure medium to and from a device for changing control times of an internal combustion engine with

an essentially cylindrical valve housing, on which pressure medium connections are formed and

with an axially displaceable control piston arranged within the valve housing,

wherein a connection between the pressure medium connections can be established or separated as a function of a position of the control piston,

wherein the valve housing is arranged within a valve receptacle, and

wherein an insertion depth of the valve housing into the valve receptacle is limited by an axial stop formed in the valve receptacle,

the axial stop is formed as a circular or circular ring-shaped wall,

which extends radially inwards starting from an inner casing surface of the valve receptacle,

and a sealing element is arranged between the valve housing and the axial stop of the valve receptacle.

4. Control valve according to claim 3, wherein an axial stop-side end of the valve housing is formed with an area reduced in outer diameter, wherein the sealing element is arranged at least partially in the area reduced in outer diameter.

5. Control valve according to claim 3, wherein the sealing element is constructed as a sealing ring with an outer casing surface and an inner casing surface.

6. Control valve according to claim 3, wherein the sealing element is comprised of an elastomer.

7. Control valve according to claim 3, wherein the elastomer is a fluoro rubber or an acrylonitrile butadiene rubber.

8. Control valve according to claim 3, wherein the valve receptacle is assembled from a first and a second bore, wherein the bores are constructed in different surrounding constructions, arranged at least approximately coaxially and located adjacent to each other.

9. Control valve according to claim 8, wherein the axial stop is embodied as a boundary of the two surrounding constructions.

10. Control valve according to claim 8, wherein the axial stop is formed in the second bore in a direction of insertion of the control valve.

11. Control valve according to claim 8, wherein the axial stop is arranged and the sealing element is constructed so that the sealing element contacts the valve receptacle at a boundary of the two surrounding constructions.

12. Control valve according to claim 4, wherein a transition area of the valve housing to the diameter-reduced area has an at least partially conical construction and the sealing element is provided on an inner casing surface thereof with a first conical area that is adapted to the transition area of the valve housing.

13. Control valve according to claim 5, wherein the outer casing surface of the sealing element is provided on an end contacting the axial stop with a second conical area, so that an annular hollow space is produced between the sealing element and the axial stop.