EP2492459B1 - Cam shaft phase adjuster with improved locking device - Google Patents

Description

The invention relates to a camshaft phaser for adjusting the rotational angular position of a camshaft relative to a crankshaft of an internal combustion engine, and more particularly to an improvement with respect to a locking and unlocking of the phaser.

To increase power and torque, but also to reduce fuel consumption and exhaust emissions of internal combustion engines for road vehicles, camshaft phasers have become popular for varying intake and exhaust timing. Due to the high reliability, but also in terms of a favorable cost-benefit ratio have hydraulic, operated by the lubricating oil for the internal combustion engine phaser proven by the principle of hydraulic swing motor. Stricter fuel consumption and pollutant emission requirements require high speeds. To increase the actuating speed, especially at low lubricating oil pressure and low oil temperature and correspondingly high viscosity, sees the EP 1 985 813 A2 in the lubricating oil supply to the phaser an accumulator device, which ensures a sufficiently high setting pressure for the phaser even in problematic with respect to the hydraulic supply operating conditions of the internal combustion engine.

The hydraulic phaser can run empty at standstill of the engine. When the internal combustion engine is started, the camshaft to be adjusted with the phaser can assume undefined angular positions until the phaser is completely filled again. As a result, the starting behavior and the exhaust gas pollutant emissions of the internal combustion engine deteriorate. In addition, the non-uniform torque of the camshaft with deflated phaser leads to beating noise. To avoid these effects camshaft phasers are provided with locking devices, which ensure that the camshaft occupies a defined position in relation to the crankshaft at the start of the internal combustion engine. Practically, the locking is realized by an example integrated in the rotor spring-loaded locking pin, which dips into a receptacle of the stator, so locks, and is unlocked against the spring force of a locking spring by acting on the pressurized fluid of the phaser. A release of the lock and then possible adjustment of the phase angle of the camshaft are only possible if a sufficient for the adjustment of the camshaft Built pressure in the pressure fluid system. In particular, an interpretation of the locking device for locking the camshaft in the "early" angular position is often difficult in practice, since in the unlocking the drag torque of the camshaft and the adjusting torque of the adjuster for adjusting the camshaft in the direction of "late" add and this Torque cause jamming forces on the locking pin, whereby the unlocking is difficult. In the design and vote of the locking device therefore there is a conflict of objectives with respect to a safe unlocking even at very low fluid pressures and camshaft speeds on the one hand and a secure locking even under unfavorable conditions such as the cold start of the engine with idle phaser on the other hand, especially when turning off the engine the locking position was not approached.

From the DE 196 23 818 C5 Lockable phaser are known in which the Vernegelungspin tapers conically to a free end. The cone of the locking pin is designed so that the rotor of the phaser is forced in the interaction of the locking pin with a bore in an angle of rotation end position. When unlocking there is a risk that the locking pin jammed in contact with the bore and a secure unlocking upon reaching a minimum release pressure, on which the locking device is designed, is not guaranteed.

At one of the DE 10 2004 028 015 A1 known phase adjuster, the locking pin on a ball or hemisphere surface which engages in the locking engagement without play in a conical receptacle to block the rotor relative to the stator. In order to automatically compensate for wear, the ball or hemisphere does not fully penetrate into the receptacle in locking engagement until it reaches the equator line, so that it can be pushed deeper into the receptacle by spring force when circumferential wear occurs. Whether such a locking intervention with not completely filled phaser as in the starting phase of the internal combustion engine ensures the lock is questionable. Due to the spherical shape is seen in the locking engagement in the direction of engagement also only point contact, whereby the wear to be compensated is increased. With respect to the point-like contact the same applies to one from the DE 10 2005 051 692 A1 known locking pin, which has over its entire effective engagement area an outwardly curved, for example, paraboloidal contour. In addition, this active contour on the locking and unlocking of the locking pins on such a low inclination that even with only slight penetration into the receptacle, the risk of unwanted blocking of the rotor.

The EP 1 008 729 A2 relates to a hydraulic vane cell actuator, comprising a guide device with which a holding element for fixing the rotor to an actuator housing can be guided into a holding position. In the holding position, the holding element can engage in a recess in the housing in order to lock the rotor relative to the housing in a rotationally fixed manner.

The WO 2005/049976 A1 relates to a hydraulic camshaft adjuster for the rotational adjustment of the camshaft of an internal combustion engine. The camshaft adjuster has in a side wall on a locking link, in which a locking pin is locked and unlocked. The locking link is formed as a blind hole with an outgoing from this shallow gutter.

The DE 198 25 288 A1 concerns a valve control apparatus having a closing rotation shaft, a rotation transmission member, vanes connected to the rotation shaft or the rotation transmission member, and a locking pin engageable with a fitting hole in the rotation shaft or the rotation transmission member for preventing relative rotation between the rotation shaft and the rotation transmission member.

The DE 101 50 856 A1 relates to a rotary piston adjusting device for adjusting the rotational angle of a camshaft relative to a crankshaft of an internal combustion engine. The adjusting device comprises a locking element which can mechanically couple an impeller of the adjusting device with a drive wheel by engagement in a receptacle in one of the side walls of the adjusting device.

It is an object of the invention to provide a camshaft phaser with a locking device which securely locks the phaser in start phases of an internal combustion engine, but unlocking even at low pressures of a pressure fluid acting on the phaser, such as occur during idling of the engine internal combustion engine, ensured with greater security, so that the risk is reduced that it locks at the wrong moment, if the rotor of the phaser is to be adjusted, for example, from the lockable rotational angle position.

The invention is based on a camshaft phaser for adjusting the rotational angular position of a camshaft relative to a crankshaft of an internal combustion engine comprising a rotatably driven by the crankshaft in preferably fixed speed relationship stator and a rotatably driven by the stator and rotatably driving the camshaft with this coupled rotor. When assembled, the stator is rotationally driven by the crankshaft and drives on the rotor, which in turn is coupled to the camshaft and thereby rotatably drives the camshaft. The stator may in particular be connected torque-tightly to a drive wheel of a traction drive, for example a chain drive or a toothed belt drive, or a gear drive, the drive wheel preferably being an integral part of the stator. The rotor is in the assembled state torque transmitting, preferably non-rotatably connected to the camshaft, so set up for such a mounting.

The camshaft phaser has at least one early setting chamber for generating a torque acting on the rotor in the direction of advance relative to the stator and at least one late setting chamber for generating a torque acting on the rotor in the reverse direction of rotation relative to the stator in the direction of lag. Preferably, the phaser comprises a plurality of Frühstellkammern and a plurality of Spätstellkammern to distribute the force required to generate the respective torque about the axis of rotation of the rotor uniformly and on a larger pressure surface. For the adjustment of the rotational angular position of the rotor in the direction of advance position or advance, the at least one early setting chamber or the preferably a plurality of Frühstellkammern be acted upon together with the pressurized fluid and the at least one Spätstellkammer or preferably several Spätstellkammern relieved in relation to the pressure. The reverse applies to an adjustment of the rotor in the direction of late or lag. In preferred embodiments, the early and late setting chamber (s) by means of a control device so mutually acted upon by the pressurized fluid that the rotor not only in one of the two or in the two end positions, the early position or the late position, but also in a rotational angle intermediate position, spaced from both end positions, can be adjusted regulated.

The pressurized fluid may be delivered in response to the rotational speed of the crankshaft so that its pressure increases with the speed of the crankshaft. The dependence can for example be such that the pressure of the pressure fluid quasi constantly follows the speed, in the extreme case continuously, but the dependence can also be designed so that the pressure of the pressure fluid with increasing speed of the crankshaft only in discrete steps, in stages, if necessary even in a single step rises. The pressurized fluid is conveyed in preferred embodiments by means of a positive displacement pump, which is driven by the internal combustion engine in dependence on the rotational speed of the crankshaft. The phase adjuster can be connected to a high-pressure side of a pressurized fluid system for supplying the pressurized fluid to the actuation chamber and to a low-pressure side of the pressurized fluid system for discharging the pressurized fluid from the actuation chambers.

The pressurized fluid may in particular be a lubricating oil serving to lubricate the internal combustion engine. The device may accordingly be arranged in a lubricating oil supply system of the internal combustion engine, which in this case forms the pressurized fluid system.

The phase adjuster comprises a locking device that can switch between a locking state and a release state. In the locked state, it positively locks the rotor in a specific rotational angle position relative to the stator. It is acted upon in the locking state with the pressurized fluid, such that it changes by being exposed to the pressurized fluid against a spring force in the release position permitting the adjustment of the rotational angular position of the rotor when the pressure of the pressurized fluid has reached a minimum release pressure.

The locking means comprises a reciprocally movable locking pin which is movable against a spring force from a locking engagement and correspondingly by means of the spring force in the locking engagement. The locking engagement of the pin corresponds to the locking state of the locking device. To generate the spring force, a locking spring, preferably a mechanical spring, may be provided. The locking pin may in particular be supported on the rotor and be guided to and fro by the rotor in a locking and unlocking direction between the locking engagement and a releasing position corresponding to the release state. The locking pin can be movably supported by the locking spring on the rotor in the unlocking direction. In principle, a support on the stator and guidance through the stator but instead also possible. The locking pin is movably supported in and out of the locking and unlocking engagement in the preferably over an end side of the rotor or the stator out locking direction, preferably as stated on the rotor, but in principle would also be a radial mobility of the locking pin conceivable. Particularly preferred is an axial mobility.

The locking device further comprises a receptacle for cooperation with the locking pin. With support of the pin on the rotor, the recording is rotationally fixed with the stator. When supporting the pin on the stator, the recording is rotationally fixed with the rotor. The receptacle has an opening through which the locking pin engages in existing locking engagement with an engagement portion in the receptacle. The engagement portion includes a front pin portion extended to the free end of the pin and a rear pin portion spaced from the free end by at least the front pin portion and lockingly engaged from the free end of the pin to at least the height of the rim the opening of the receptacle extends.

The receptacle has receiving portions which have in the locking and unlocking with the pin portions corresponding lengths, namely a lower receiving portion which is at least as long as the front pin portion, and an upper receiving portion extending from the edge of the receiving opening, the opening edge in Direction to the lower receiving portion, preferably extends to the lower receiving portion and as long as the rear pin portion. In the locking engagement overlap the front pin portion with the lower receiving portion and the rear pin portion with the upper receiving portion.

According to the invention acts in the locking engagement of the locking pin and recording either the rear pin portion with the upper receiving portion or the front pin portion with the lower receiving portion blocking together. In other words, in the second alternative, the locking pin is blocked with its front pin portion in the lower receiving portion, but not in the rear pin portion. In the preferred first alternative, the blocking is achieved in cooperation of the rear pin portion and upper receiving portion, while no blocking effect emanates from the front pin portion. In the first alternative, the front pin portion has at its outer periphery to the locking and unlocking a slope which is so large over the entire length of the front pin portion that the rotor is not blocked only by the engagement of the front pin portion, so the engagement the rear pin section causes the blockage. In the second alternative, instead, the upper receiving portion has an inclination at an inner periphery to the locking and unlocking direction, which is so large over the entire length of the upper receiving portion that the rotor is not blocked only by engagement of the front pin portion in the upper receiving portion However, the engagement of the front pin portion in the lower receiving portion causes the blockage. Since leaks are more difficult to prevent with increasing cross-section of the opening of the receptacle, a taper of the locking pin in the front pin portion is given preference over a widening of the receptacle towards the receiving opening.

The front pin portion is in the locking and unlocking at least 0.2 times, preferably at least half as long as the rear pin portion. On the other hand, the rear pin portion is desirably at least half as long as the front pin portion. Preferably, the ratio of the length of the front pin portion to the length of the rear pin portion is 1 ± 0.5. The front pin portion may even be longer than the rear pin portion. Preferably, however, the rear pin portion is longer than the front. Conveniently, at least that pin portion which causes the blocking in the locking engagement in cooperation with the associated receiving portion, at least 0.5 mm, preferably at least 1 mm long. In interlocking engagement, there should be line contact between those sections which interact in a blocking manner in the direction of locking and unlocking. Preferably there is a flat blocking contact.

The lower limit mentioned above for the aspect ratio, namely that the rear pin portion may be up to about five times as long as the front pin portion, is particularly true for embodiments in which both the front pin portion tapers significantly and the upper receiving portion tapers from the opening edge of the socket pronounced tapers or, in other words, widens to the opening edge with a large inclination. The lower limit mentioned for the aspect ratio of the front pin section to the rear pin section applies in particular or instead for embodiments in which the rear pin section and, correspondingly, the upper receiving section are not cylindrical or cylindrical, but also in the direction of the front pin section or lower Receptacle tapered, preferably each taper and preferably congruent in such embodiments. The locking pin in such embodiments preferably has the distinctly tapered front pin portion and the less tapered, preferably with a slight inclination of at most 20 ° tapered rear pin portion. Preferably, the rear pin portion tapers in such embodiments over its entire, in the locking state projecting into the receptacle length. In such embodiments, the receptacle preferably tapers from the opening edge to the lower receiving section or into its bottom in a lower section of the upper receiving section adjoining the lower receiving section, optionally also in the lower receiving section, with a slight inclination which is expediently equal to or less than 20 °, more preferably equal to or less than 10 °. An upper portion of the upper receiving portion, which extends to the opening edge, may have the already mentioned pronounced inclination of preferably more than 30 °. The rear pin portion or the upper receiving portion or the lower portion of the upper receiving portion is or are provided in such embodiments with such a slope, which ensures locking of the locking pin in locking engagement.

The said inclination, either of the front pin portion or the upper receiving portion or the upper portion of the upper receiving portion, is at least 45 ° to avoid self-locking of pin and receptacle. The inclination is at most 75 °. The inclination can be 60 ° ± 10 °. If the front pin portion tapers toward the free end of the locking pin, the front pin portion may be conical, ie constant pitch, or variable pitch, in at least a circumferential effective range where the front pin portion can contact the opening edge of the receptacle Embodiments preferably be concave tapered as seen from the outside. Particularly preferably, the front pin portion is frustoconical. In embodiments in which the upper receiving portion tapers in the direction of the lower receiving portion and widens in the direction of the edge of the receiving opening, the same applies mutatis mutandis.

If in locking engagement, as preferred, the rearward pin portion is in the blocking contact with the upper receiving portion, the rearward pin portion may be cylindrical over at least a portion of its length, preferably over its entire length, at least in a circumferential effective area with which it is in locking contact in locking engagement or an inclination of less than 20 °, preferably less than 10 °. Analogously, the same applies in the alternative embodiment for the front pin portion, namely, if the front pin portion is in locking engagement with the lower receiving portion in blocking contact.

The locking pin is in preferred simple embodiments about a pointing in the locking and unlocking longitudinal axis rotationally symmetric. The receptacle is rotationally symmetrical in preferred simple embodiments in relation to a longitudinal axis pointing in the direction of locking and unlocking. Rotational symmetry is particularly favorable in view of the manufacturing costs, but also in terms of Abdichtproblematik.

In preferred embodiments, the rearward pin portion is cylindrical or tapered at an inclination of less than 20 °, preferably less than 10 °, and the forward pin portion is tapered with an inclination of preferably 60 ° ± 10 ° as measured against the locking and unlocking direction.

The locking pin is preferably flattened at the front end. Instead, it can also be convex at the front end and arched outwards. In preferred embodiments, the front pin portion is frusto-conical, so that at the front end of the locking pin a plane, orthogonal to the locking and unlocking direction end face is obtained.

In the lower receiving portion, a local, flat elevation is preferably formed on the locking pin in the opposite end face in a central surface area, against which the locking pin engages in locking engagement to keep the locking pin in locking engagement of the said end face of the recording and a rapid pressure build-up to promote unlocking. If the front pin section tapers to the free end of the locking pin, an exemption for rapid pressure build-up is also obtained from home.

The rotor is preferably fixed in the locking engagement of the locking pin relative to the stator in an early position. The locking device could instead by means of appropriate arrangement of locking pin and receptacle but also be adapted to fix the rotor in the retarded position in the locking engagement or in a lying between these two extreme positions intermediate position. In yet another variant, the locking device can be set up to fix the rotor in each case in a locking engagement in more than just one of the stated positions relative to the stator. For unlocking a loading of the locking device by the pressure fluid of the early adjustment chamber is advantageous. The pressurization of the early adjustment chamber relieves the locking device at least in part from the drag torque of the camshaft, so that the unlocking counteracting transverse or shear forces are reduced in comparison to an actuation of the locking device from the Spätstellkammer. There is reason to suspect that the pressure pulsations in the early-adjusting chamber resulting from drag torque fluctuations relieve the locking engagement of transverse or shear forces when the locking play exists in the locking engagement and facilitate the unlocking or even make it possible in the first place. An increase in the drag torque causes a slight reduction of the early adjustment chamber via a locking clearance, so that the pressure increases in the early adjustment chamber and relieves the locking device in the locking engagement. In preferred embodiments, the locking device for releasing the locking engagement is connected only to the early adjustment chamber.

On the other hand, it may be advantageous if the locking device for solving the locking engagement directly or indirectly with the Spätstellkammer indirectly via a supply or discharge to or from the Spätstellkammer, preferably only with the Spätstellkammer. As a result, when locking in the early position, it can be ensured with particular certainty that the locking pin moves into the locking engagement when the internal combustion engine is switched off, since the retraction movement into the receptacle can not counteract any remaining residual pressure from the early adjustment chamber. When locking in the early position, this can be particularly advantageous in designs with pressure accumulator and in embodiments, in which upstream of such a pressure accumulator or, regardless of the question of whether a pressure accumulator is provided upstream of a control valve of the phaser or optionally in the control valve of the phaser a Rücksperreinrichtung is provided.

The locking pin preferably has at least one pressure surface on which it can be acted upon by the pressure fluid to move the locking pin from the locking engagement to the release position and thereby to transfer the locking device in the release state. The locking pin can be formed as a simple piston with only a single pressure surface for the application of the pressurized fluid. In preferred first embodiments, the locking pin is designed as a stepped piston and has the engagement portion and a guide portion. The locking pin has a first pressure surface in a transition region between the engagement region and the guide portion. A second pressure surface is provided at the engagement area. The pressure surfaces are each acted upon by the pressure fluid to release the locking engagement. The first and second pressure surfaces may be fluidly separated from one another and one of the pressure surfaces connected to the early-actuator chamber and the other associated with the late-actuator chamber, as is common with phased-lock phase phasers, to unlock both upon pressurization of the advance chamber and upon application of the retarded actuation chamber to be able to. In preferred embodiments of the invention, however, the first pressure surface and the second pressure surface are connected to each other, so that the pressure fluid for releasing the locking engagement reaches one of the pressure surfaces and from there to the other of the pressure surfaces. Instead, a feeder can also branch and be led from the branching point to each of the printing surfaces. A combined application does not take place in such embodiments with fluidically connected pressure surfaces. The locking device is only connected to either the late setting chamber or only with the early adjustment chamber, however, both pressure surfaces are acted upon at the same time in accordance with the pressure in the respective adjusting chamber. This results in a large overall pressure area in comparison to the prior art and, as a result, a larger force available for unlocking, even with a small pressure, compared to the larger one. Therefore, the locking spring may have a greater spring stiffness than usual in the case of stepped piston or be installed with higher bias. Accordingly, the locking spring keeps the locking pin in locking engagement until it reaches the minimum unlocking pressure. The pressure surfaces are preferably connected to one another via a connecting channel which is internal with respect to the locking device, so that the flow resistance within the connection is low. The connecting channel is preferably a geometric inner channel of the rotor.

In advantageous embodiments, in which the rotor movably supports the locking pin, the latter has a connecting channel which is external with respect to the locking device and which is in one of the Stellkammern, preferably the Frühstellkammer, opens and connects the locking means for releasing the locking engagement with this adjusting chamber, preferably short-circuiting. Preferably, the locking device is connected only via the rotor with the respective adjusting chamber. The outer connection channel opens on an outer surface of the rotor, which limits the relevant adjusting chamber. This results in a short, structurally simple, low-loss hydraulic connection between this adjusting chamber, which is also referred to below as the unlocking adjustment chamber, and the single pressure surface or alternatively a plurality of pressure surfaces of the locking pin.

The locking pin is preferably arranged movably in a radially projecting wing of the rotor. The connecting channel between the locking device and Entriegelungsstellkammer can be guided over a short path from an inner chamber of the rotor blade, which is bounded by said pressure surface of the locking pin on one side to the mouth on the side surface of the rotor blade directly into the Entriegelungsstellkammer, preferably the Frühstellkammer as only a straight channel without change of direction. The mouth of the outer connecting channel preferably has a distance from both end sides of the rotor, so that the mouth lies completely in the rotor blade surface.

If the locking pin is not formed as a stepped piston, but as a simple piston with a simple cylindrical guide, can advantageously in embodiments in which the locking pin is movably guided in the rotor, in the guide area, i. on the guide peripheral portion of the lock pin or on the guide peripheral portion of the rotor, the inner connecting passage may be provided. It is also preferred for such embodiments, that the external connection channel directly connects the Entriegelungsstellkammer with the internal connection channel by the external connection channel of the rotor opens both directly into the Entriegelungsstellkammer and directly into the internal connection channel, wherein in the mouth region, a distribution space may be formed, for example a circumferential recess on one of the two said guide peripheral surfaces.

In the arrangement of the locking pins in a rotor blade, it is advantageous if the locking pin is arranged in an end view of the rotor seen in the circumferential direction eccentric. Relative to a radial to the axis of rotation of the rotor, which divides the rotor blade in the end view seen centrally, the locking pin is arranged at least with its center not on the radial, but in the circumferential direction next to it. Preferably, the locking pin is seen in the end view in the circumferential direction closer to the Entriegelungsstellkammer than in the located on the other side of the rotor blade actuating chamber. This is particularly advantageous if the locking device for releasing the locking engagement directly with the Entriegelungsstellkammer is connected. On the front side of the rotor blade, an advantageously long sealing web between the guide for the locking pin and the opposite adjusting chamber is obtained in the circumferential direction.

A feature that may advantageously be common with the circumferentially eccentric arrangement, but in principle also realized instead, is an arrangement of the locking pin closer to a radial end of the rotor blade than the axis of rotation. An arrangement near the radial end also contributes to reducing the already discussed shear force, which makes unlocking difficult.

To arrange the locking pin in the rotor blade is still to be noted that in the preferred mehrflügligen embodiments of the rotor that wing in which the locking pin is movably arranged, measured in the circumferential direction is preferably wider than the at least one or more other blades of the rotor. This creates space for the locking device and allows the formation of a long sealing ridge on the rotor front side on the side facing away from the Entriegelungsstellkammer with respect to the circumferential direction of the locking device. The distance between the two stator vanes, between which the wider rotor blade protrudes, is advantageously also larger, as adapted to the larger blade width, than between the other adjacent pair (s) of stator blades, preferably at least substantially the difference in rotor blade width.

In a further development, an accumulator device is arranged in the fluid supply to the phaser to ensure the pressure fluid supply and thus an operating speed of the phaser appropriate to the operation of the internal combustion engine even with short-term pressure fluctuations in the pressure fluid system. Pressure fluctuations can occur, for example, during load changes, when starting the internal combustion engine or in adjusting operations of the phaser or with the pressurized fluid to be supplied further units. If the system pressure in the pressure fluid supply upstream from the phaser and the pressure storage device at such a pressure fluctuation decreases, the pressure storage device supplies the phaser until either the system pressure upstream of phaser and pressure storage device again increased above the pressure of the pressure storage device or the pressure storage device is emptied. The storage volume of the pressure storage device is advantageously at least so great that it is ensured in the case of a pressure drop that the phase adjuster can perform at least one complete adjustment, preferably at least two complete manipulations, from one to the other end position.

The pressure storage device comprises a spring device and at least one storage chamber which can be filled with the pressure fluid against a restoring spring force of the spring device. The spring means may be formed by a single spring member or comprise a plurality of spring members in a suitable spring circuit. The spring member or the plurality of spring members may or may be gas spring (s), in particular pneumatic spring (s), or preferably one or more mechanical spring (s). Particularly suitable are pressure-tensioned coil springs.

The pressure storage device has a storage structure bounding the wall structure, which is movable for loading the pressure storage device against the spring force and for unloading by the spring force. The filled volume of the storage chamber preferably always corresponds to the balance of fluid pressure and spring force, so that the pressure storage device can fulfill its compensation function at any time during operation of the internal combustion engine without delay. The movable wall structure may be an elastically flexible, but fluid-tight wall structure, or preferably a reciprocating piston in the pressure chamber. In the first case, the wall structure may be attached to a chamber wall of the storage chamber. It can itself form the spring device. The accumulator would be in such an embodiment, a diaphragm accumulator with an elastic or possibly only flexible membrane, which is stretched in the latter case by an additional spring member. In preferred embodiments as a piston, the piston is supported on the spring device.

If the wall structure is formed as a reciprocating piston, the storage chamber may in first embodiments over the circumference of the piston alone by a correspondingly narrow gap, without sealing rings, or with a sealing ring, preferably piston ring, or possibly also several in the direction of reciprocating Agility of the piston spaced from each other sealed sealing rings. A piston ring is advantageously formed from one of the thermal expansion according to the same material as the piston. Thus, the piston may be made of aluminum or an aluminum-based alloy, in particular of aluminum or an aluminum-based alloy and a sealing ring formed as a piston ring or possibly also several such sealing rings, wherein in the case of chemically not exactly the same materials, the different materials have the same or almost equal thermal expansion coefficient , The sealing ring can at least to be coated of its gap-sealing sealing surface to reduce friction, for example a Hardcoat ^® have -Glatt sliding layer (HC-GL-slip layer). Such a sliding layer can be produced in particular by anodizing, wherein Hardcoat ^® -Glatt electrolytes can consist of a mixture of oxalic acid and additives. As a rule, sulfuric acid is used

The pressure storage device may in particular be designed so that the storage chamber begins to fill against the spring force of the spring device already at a Füllbeginndruck that is at most as large as a hot idle pressure in Zuführzweig the pressurized fluid supply. The pressure storage device is in preferred embodiments, designed so that the storage chamber fills in excess of the hot idle pressure against the spring force. In preferred embodiments, the filling start pressure is below the hot idling pressure, so that the filling process already begins below the hot idle pressure and the storage chamber is already partially filled at the hot idle pressure prevailing in Zuführzweig and can fulfill their balancing function, in this critical state of the internal combustion engine, if necessary, pressurized fluid for the phaser ready to deliver. If the pressure storage device already filled completely when the Zuführzweig is under hot idling pressure, could be achieved with an increase in the speed of the crankshaft adjusted to the increased speed adjustment speed by the phaser because the storage chamber pressure fluid supplied only with hot idle pressure. On the other hand, such an interpretation should not be ruled out. In a preferred design, however, the pressure storage device supplies the pressure fluid in such a case with a pressure lying above the hot idle pressure and therefore ensures even at higher speeds of the crankshaft sufficiently fast adjustment of the phase position of the camshaft, in which based on the number of combustion cycles per unit time absolutely only a shorter period of time is available for the adjustment. If the pressure storage device is preferably downstream of a restraint device, that is arranged between the locking device and the phaser, then it can partially charge even when the engine is idling, if its Füllbeginndruck corresponds to the hot idle pressure, especially in pressure pulsations in the or the applied control chambers. The pressure storage device can compensate for such pressure pulsations at low speed and in particular also at speeds above idle speed, so that the phase adjuster still operates at an adjusted actuating speed.

It is advantageous if the pressure storage device is designed, in particular by volume and cross-sectional area of the storage chamber and spring force, that the measured in radians per second positioning speed with which the rotational angular position of the rotor is adjusted relative to the stator, up to at least 1.5 times or preferably to at least twice, more preferably to at least three times the idling speed of the internal combustion engine at pressure drop in Zuführzweig adapted by subsequent delivery from the pressure storage device of the frequency of the combustion cycles of the internal combustion engine. The ratio of phaser actuator speed and crankshaft speed is at least substantially constant in such embodiments at least up to 1.5 times or twice, preferably up to at least three times the idle speed even under pressure fluctuations.

The hot idle pressure can be measured in the feed branch of the pressurized fluid system immediately upstream of the phaser or the pressure storage device. If the phase adjuster and the pressure storage device are preferably separated from other consumers to be supplied with the pressure fluid by means of a restraining device so that pressurized fluid can not flow back from the device comprising the pressure accumulator device and the phaser, optionally one or more further phasors in the delivery branch, this becomes the reference variable serving hot idle pressure, preferably immediately upstream of a shut-off point of the Rücksperreinrichtung measured, otherwise advantageously upstream of the memory and as close to this. Under idle running pressure is understood as usual the pressure at idle in warm operating condition of the internal combustion engine, in which the temperature of the pressurized fluid, if this is the lubricating oil, for example, in the range of about 80 ° to 120 ° C. Since higher-frequency pressure fluctuations in the Zuführzweig are unavoidable, namely pressure fluctuations with a higher frequency than by means of the pressure storage device to be compensated pressure fluctuations, is understood as the reference value of the resulting under such higher-frequency pressure fluctuations mean value of the pressure. High-frequency pressure fluctuations can occur, for example, due to delivery pulsations of a pressure fluid pump or pipeline vibrations. The frequency of these fluctuations is so high that the pressure for practical purposes, including the supply of the device according to the invention, is represented by the mean value. With regard to pressure pulsations due to drag torque fluctuations, which originate from the camshaft and act on the phaser, this may also apply to the upper speed range of the crankshaft, while in the lower and preferably also at least in the middle speed range such pressure pulsations advantageously at least partially from the pressure storage device be compensated.

In preferred embodiments, the locking device is designed so that the minimum unlocking pressure is at most as high as the hot idling pressure or the Füllbeginndruck. The word "or" is understood here as well as otherwise of the invention in the usual logical sense of an "inclusive or", so includes both the meaning of "either ... or" as well as the meaning of "and", as far as from the each concrete context can not exclusively give only one of these two meanings. In relation to the minimum unlocking pressure this means that in a first variant it is at most as large as the hot empty running pressure, preferably smaller than the hot empty running pressure, and in a second variant at most as large as the filling start pressure, preferably smaller than the filling start pressure. Due to the inventive design of the pressure storage device, the second variant also includes the "and" meaning of the word "or", since the minimum release pressure when implementing the second variant is at most as high as the hot idling pressure.

If the phase adjuster comprises the pressure storage device, this is preferably connected to the locking device, so that in the event of pressure fluctuations, early unlocking of the phase adjuster by means of the pressure storage device can be ensured more reliably. If the unlocking minimum pressure is less than the filling start pressure, the filling of the pressure storage device does not first begin before the unlocking of the locking device, which would lead to a delay of the unlocking. If the locking device makes the fixing of the rotor in the locking engagement preferably in a form-fitting manner, not only the pressure force of the pressure fluid leading out of the locking engagement, but also a shearing force pointing transversely to this pressure force, act in the locking engagement. The shear force depends on the drag torque of the camshaft, which is rotated by the stator, the locking engagement and the rotor in the event of a locking engagement, and also by the pressure conditions in the adjusting chambers. Accordingly, early unlocking, at low speed, is desirable, especially with regard to an advantageously low shear force, particularly in the case of a rotor locked in the early position. The explained vote of pressure accumulator and locking device ensures early, yet safe unlocking of the phaser and a sufficient actuating speed in load operation of the engine, above the hot idle speed, in combination.

In practice, the minimum release pressure, for example, 0.4-0.8 bar, the Füllbeginndruck correspondingly higher, for example, 0.5-1.0 bar, and a minimum filling pressure at which the storage chamber is completely filled, for example, 1.5-2 , 5 bar. The hot idling pressure is correspondingly between the Füllbeginndruck and required for the complete filling of the storage chamber minimum filling pressure. As already explained for hot idling pressure, the pressure average values resulting from the higher-frequency pressure fluctuations are used as representative measurement values for the different characteristic pressures. The pressures to be compared with each other are expediently measured in steady-state operating states of the internal combustion engine, in which no additional units, which may optionally be connected to the pressure fluid supply system, are switched on or off. During the measurement, the phaser expediently also does not perform a setting process.

The pressure storage device is arranged in preferred embodiments in a mounting housing which can be mounted on a machine housing of the internal combustion engine, for example a main housing or a cylinder head housing of the machine housing. In this way, the pressure storage device can be mounted by mounting the attachment housing as a unit to the internal combustion engine. If the phaser and the pressure storage device are separated by means of a Rücksperreinrichtung from the rest of the pressurized fluid system, namely with respect to a Backflow through the Zuführzweig, the Rücksperreinrichtung can be advantageously arranged in the mounting housing. Regardless of the arrangement of the pressure storage device and the Rücksperreinrichtung in a common mounting housing or separately from each other, the Rücksperreinrichtung is preferably assigned only to the phaser or optionally multiple phaser for several camshafts, so specifically secures only the phaser or possibly multiple phaser against backflow of pressurized fluid through the fluid supply from, the pressure immediately upstream of the Rücksperreinrichtung should be less than the downstream pressure. The pressure storage device is preferably arranged together with the phaser and this immediately downstream of the Rücksperreinrichtung, ie in the fluid flow between the Rücksperreinrichtung and the phaser.

In a further development, on a mounting side of the attachment housing, with which this is attached to the internal combustion engine, preferably the machine housing, a separately manufactured from the mounting housing seal arranged by means of at least one centering, which during assembly of the mounting housing for easy correct positioning of Attachment housing is used relative to the internal combustion engine, is held on the attachment housing. Preferably, the seal is held on a plurality of such centering elements of the attachment housing on this. The holder on the mounting housing may be frictionally engaged, but is preferably form-fitting or at least includes a positive connection in that the seal is in a rear grip with the at least one centering or preferably in the rear grip with one of a plurality of centering. The centering element (s) may protrude in particular on a joining surface of the attachment housing located on the mounting side. The joining surface of the attachment housing, on which the or the centering (e) protrudes or protrude or is alternatively formed as a recess (s) or is a surface with which the mounting housing is clamped against the internal combustion engine in the assembled state, preferably by means of a screw connection , In particular, it can be an end face which surrounds an axis of rotation of the stator-rotor arrangement. The holder of the seal is preferably captive, that is configured such that the seal remains in the suitable position for mounting relative to the mounting housing even if the mounting housing is held with the mounting side facing down freely. The at least one of the support of the seal serving centering or at least one of a plurality of the holder of the seal serving centering elements may have a passage, for example, be formed as a sleeve, the passage is sufficiently large to pass through such a hollow centering a screw for a screw the internal combustion engine or a bolt-shaped clamping element of another joint connection to lead. The applicant reserves the right to a housing for the phaser or the pressure storage device, in particular a mounting housing together for the pressure storage device and the Rücksperreinrichtung, optionally also the phaser, with a to hold such a seal own claim. In general, the holder of the seal but also for the connection of another purpose serving housing to the internal combustion engine or other unit of advantage.

The rotor and the stator form, as already mentioned in preferred embodiments, a hydraulic swing motor. In such an embodiment, the rotor and the stator can be arranged inside each other on the inside and each have at least one radially projecting wing. In principle, although the rotor may be a ring gear and with at least one inwardly projecting wing and the stator an internal gear with at least one radially outwardly projecting wing. Preferably, however, the stator forms the ring gear and has at least one, preferably a plurality of inwardly projecting blades, and the rotor forms the internal gear with at least one, preferably a plurality of outwardly projecting blades (n). The one or more rotor blades and the stator wing (s) limit the setting chambers in the circumferential direction. If the early-settling chamber is acted on by pressurized fluid, this produces a force acting in the circumferential direction and thus a torque which, viewed in relation to the stator, acts on the rotor in the direction of advance position or lead over. Conversely, the conditions are when the late setting chamber is acted upon by the pressure fluid and the early-acting chamber is relieved.

If the phaser operated as preferred with the lubricating oil for the internal combustion engine, the lubricating oil from the camshaft to the phaser and the optional pressure storage device or via the pressure storage device to the camshaft and from this to the phaser can be performed. In principle, however, the lubricating oil does not have to be guided via the camshaft to the phaser, but can also be supplied to it in other ways. In first embodiments, the pressurized fluid is fed to the phaser via the pressure storage device, i. the pressurized fluid flows into the storage chamber and is only supplied via this to the phaser or the control chambers. The pressure storage device is arranged in the first embodiments in the main stream. In second embodiments, the adjusting chambers and the pressure storage device are arranged in parallel with respect to the fluid flow, wherein a branch leads to the pressure storage device on the flow path of the pressurized fluid to the one or more adjusting chambers. The pressure storage device is arranged in the second embodiments in the secondary flow, based on the leading to the phaser main flow. The main flow to the device according to the invention is preferably arranged parallel to the supply current, for example to cylinders of the internal combustion engine or bearings of the camshaft and the like, so that the device flows to the pressure loss fluid with little loss.

Embodiments have been found to be particularly advantageous in which the phaser has a control valve for controlling the pressure in the control chambers, in relation to the stator-rotor assembly centrally, preferably at one end of the camshaft, and preferably also centrally with respect to its axis of rotation, for example wholly or partially in a hollow camshaft end. In such embodiments, the pressurized fluid is preferably guided via the camshaft to the control valve and supplied therefrom in accordance with the desired relative rotational angle position of the early or late setting chambers (s).

Advantageous features are also disclosed in the subclaims and their combinations.

1. A. Vorrichtung zur Verstellung der Drehwinkelposition einer Nockenwelle relativ zu einer Kurbelwelle einer Brennkraftmaschine, die Vorrichtung umfassend:
   1. (a) einen mit in fester Drehzahlbeziehung von der Kurbelwelle drehantreibbaren Stator (3),
   2. (b) einen vom Stator (3) drehantreibbaren und zum Drehantreiben der Nockenwelle (1) mit dieser koppelbaren Rotor (7),
   3. (c) eine Frühstellkammer (8) zur Erzeugung eines auf den Rotor (7) relativ zum Stator (3) in Richtung Voreilung wirkenden Drehmoments und eine Spätstellkammer (9) zur Erzeugung eines auf den Rotor (7) relativ zum Stator (3) in Richtung Nacheilung wirkenden Drehmoments, die zur Erzeugung des jeweiligen Drehmoments mit einem Druckfluid, dessen Druck bei steigender Drehzahl der Kurbelwelle ebenfalls steigt, beaufschlagbar sind, um die Drehwinkelposition des Rotors (7) relativ zum Stator (3) verstellen zu können,
   4. (d) und einen Zuführzweig (50-53) für die Zuführung und einen Abführzweig (4') für die Abführung des Druckfluids zu und aus den Stellkammern (8, 9).
2. B. Vorrichtung nach Absatz A, die ferner eine im Zuführzweig (50-53) angeordnete Druckspeichereinrichtung (40) mit einer Federeinrichtung (43) und einer Speicherkammer (41), die gegen eine rückstellende Federkraft der Federeinrichtung (43) mit dem Druckfluid befüllbar ist, umfasst.
3. C. Vorrichtung nach Absatz B, dadurch gekennzeichnet, dass die Speicherkammer (41) sich gegen die Federkraft bei einem Füllbeginndruck (P_FB) zu füllen beginnt, der höchstens so groß wie ein Heißleerlaufdruck (P_HL) ist, den das Druckfluid im betriebswarmen Zustand im Leerlauf der Brennkraftmaschine aufweist.
4. D. Vorrichtung nach Absatz C, dadurch gekennzeichnet, dass sich die Speicherkammer (41) bei Überschreiten des Heißleerlaufdrucks (P_HL) gegen die Federkraft weiter füllt.
5. E. Vorrichtung nach einem der Absätze A bis D, umfassend eine Verriegelungseinrichtung (30), die in einem Verriegelungseingriff den Rotor (7) in einer bestimmten Drehwinkelposition relativ zum Stator (3) mechanisch fixiert und durch Beaufschlagung mit dem Druckfluid in einen die Verstellung der Drehwinkelposition des Rotors (7) zulassenden Freigabezustand wechselt, wenn der Druck des Druckfluids einen Entriegelungsmindestdruck (P_E) erreicht hat, der höchstens so groß wie der Heißleerlaufdruck (P_HL) oder der Füllbeginndruck (P_FB) ist.
6. F. Vorrichtung nach einem der Absätze A bis E in Kombination mit B, dadurch gekennzeichnet, dass die Druckspeichereinrichtung (40) nach Volumen und Querschnittsfläche der Speicherkammer (41) und Federkraft so ausgelegt ist, dass die Stellgeschwindigkeit (ϕ/s), mit der die Drehwinkelposition des Rotors (7) relativ zum Stator (3) verstellt wird, bis wenigstens zur 1.5-fachen, vorzugsweise bis wenigstens zur doppelten Leerlaufdrehzahl der Brennkraftmaschine auch bei momentanem Druckabfall im stromauf der Druckspeichereinrichtung (40) gelegenen Teil des Zuführzweigs (50-53) für das Druckfluid durch Nachlieferung aus der Druckspeichereinrichtung (40) der Frequenz der Verbrennungszyklen der Brennkraßmaschine angepasst ist, derart, dass das Verhältnis von Stellgeschwindigkeit und Kurbelwellendrehzahl bis wenigstens zur 1.5-fachen, vorzugsweise bis wenigstens zur zweifachen Leerlaufdrehzahl zumindest im Wesentlichen konstant ist.
7. G. Vorrichtung nach einem der Absätze A bis F, umfassend eine Verriegelungseinrichtung (30), die in einem Verriegelungseingriff den Rotor (7) in einer bestimmten. Drehwinkelposition relativ zum Stator (3) mechanisch fixiert und durch Beaufschlagung mit dem Druckfluid in einen die Verstellung der Drehwinkelposition des Rotors (7) zulassenden Freigabezustand wechselt, wobei die Verriegelungseinrichtung (30) zum Lösen des Verriegelungseingriffs mit der Frühstellkammer (8), vorzugsweise nur mit der Frühstellkammer (8), oder der Spätstellkammer (9), vorzugsweise nur mit der Spätstellkammer (9), verbunden ist.
8. H. Vorrichtung nach einem der Absätze A bis G, umfassend eine Verriegelungseinrichtung (30) mit einer Verriegelungsfeder (32) und einem Verriegelungspin (31; 60; 70), das gegen eine rückstellende Federkraft der Verriegelungsfeder (32) aus einem Verriegelungseingriff, in der es den Rotor (7) in einer bestimmten Drehwinkelposition relativ zum Stator (3) mechanisch fixiert, durch Beaufschlagung mit dem Druckfluid in eine Freigabeposition bewegbar ist, in der es die Verstellung der relativen Drehwinkelposition des Rotors (7) zulässt.
9. I. Vorrichtung nach Absatz H, dadurch gekennzeichnet, dass der Verriegelungspin (31; 70; 80) über die Verriegelungsfeder (32) an einem aus Rotor (7) und Stator (3) abgestützt ist und von dem einen aus Rotor (7) und Stator (3) zwischen dem Verriegelungseingriff und der Freigabeposition hin und her beweglich, vorzugsweise axial beweglich geführt wird.
10. J. Vorrichtung nach Absatz H oder I, dadurch gekennzeichnet, dass der Verriegelungspin (31; 60; 70; 100) mit einem Eingriffsbereich (31b; 61, 62; 71, 72; 101, 102) im Verriegelungseingriff in eine Aufnahme (33; 80; 90; 110) eingreift, die in einem aus Stator (3) und Rotor (7) geformt ist, und eine bei bestehendem Verriegelungseingriff außerhalb der Aufnahme in dem anderen aus Stator (3) und Rotor (7) befindliche ringförmige erste Druckfläche (31c; 63; 103) und eine bei bestehendem Verriegelungseingriff in der Aufnahme befindliche zweite Druckfläche (31d; 64; 104) aufweist, die zum Lösen des Verriegelungseingriffs jeweils mit dem Druckfluid beauschlagbar sind, und die Druckflächen miteinander verbunden sind, vorzugsweise über einen in Bezug auf die Verriegelungseinrichtung (30) inneren Verbindungskanal (38), so dass das Druckfluid zum Lösen des Verriegelungseingriffs zu einer der Druckflächen und von dort auch zu der anderen der Druckflächen gelangt, vorzugsweise über den inneren Verbindungskanal (38).
11. K. Vorrichtung nach einem der Absätze H bis J, dadurch gekennzeichnet, dass der Verriegelungspin (31; 60; 70; 100) mit einem Eingriffsbereich (31b; 61, 62; 71, 72; 101, 102) im Verriegelungseingriff in einer Aufnahme (33; 80; 90; 110) eingreift, die im Stator (3) geformt ist, und im Rotor (7) ein Verbindungskanal (34) von entweder der Frühstellkammer (8) oder der Spätstellkammer (9) zu einer Umfangsfiihrungsfläche des Verriegelungspins (31; 60; 70; 100) und längs der Umfangsführungsfläche des Verriegelungspins ein weiterer Verbindungskanal (38) zur Aufnahme (33; 80; 90; 110) führt, um Druckfluid aus entweder der Frühstellkammer (8) oder der Spätstellkammer (9) in die Aufnahme zu führen und eine Druckfläche (31d; 64; 74; 104) des Verriegelungspins (31, 60; 70; 100) zum Entriegeln mit dem Druckfluid beaufschlagen zu können.
12. L. Vorrichtung nach einem der Absätze H bis K, dadurch gekennzeichnet, dass der Rotor (7) den Verriegelungspin (31; 60; 70) beweglich lagert und einen in Bezug auf die Verriegelungseinrichtung (30) äußeren Verbindungskanal (34) aufweist, der in eine der Stellkammern (8, 9), vorzugsweise in die Frühstellkammer (8), mündet und die Verriegelungseinrichtung (30) zum Lösen des Verriegelungseingriffs mit dieser Stellkammer (8) verbindet,
13. M. Vorrichtung nach einem der Absätze H bis L, dadurch gekennzeichnet, dass der Verriegelungspin (31; 60; 70) in einem Flügel (7a) des Rotors (7) beweglich und in einer Stirnansicht des Rotors (7) gesehen in Umfangsrichtung exzentrisch angeordnet ist.
14. N. Vorrichtung nach einem der Absätze H bis M, dadurch gekennzeichnet, dass der Verriegelungspin (31; 60; 70) in einem Flügel (7a) des Rotors (7) axial beweglich und einem radialen Ende des Flügels (7a) näher als der Drehachse (R) des Rotors (7) angeordnet ist.
15. O. Vorrichtung nach einem der Absätze H bis N in Kombination mit Absatz B, ferner umfassend eine Rücksperreinrichtung (51), die im Zuführzweig (50-53) stromaufwärts von der Druckspeichereinrichtung (40) angeordnet ist und die Zuführung des Druckfluids zu den Stellkammern (8, 9) und der Druckspeichereinrichtung (40) zulässt, ein Rückströmen aber verhindert, wobei zwischen der Druckspeichereinrichtung (40) und den Stellkammern (8, 9) vorzugsweise kein weiteres mit dem Druckfluid zu versorgendes Aggregat angeordnet ist.
16. P. Vorrichtung nach einem der Absätze A bis O, dadurch gekennzeichnet, dass der Phasensteller für eine Montage an einem axialen Ende der Nockenwelle (1) eingerichtet ist und ein im montierten Zustand in Bezug auf die Drehachse (R) der Nockenwelle (1) oder die Anordnung aus Stator (3) und Rotor (7) zentrales Steuerventil (10, 20) mit einem axialen Einlass (P_a, 22) für eine axiale Beaufschlagung eines hin und her beweglichen Ventilkolbens (20) des Steuerventils (10, 20) mit dem Druckfluid aufweist, dass das Druckfluid dem Steuerventil (10, 20) im montierten Zustand vorzugsweise über die Nockenwelle (1) zuführbar ist.
17. Q. Vorrichtung nach Absatz P in Kombination mit Absatz B, dadurch gekennzeichnet, dass die Druckspeichereinrichtung (40) einen an den Zuführzweig (50-53) anschließbaren Einlass (2d) für das Druckfluid und einen mit dem Steuerventil (10, 20) verbundenen oder verbindbaren, vorzugsweise an die Nockenwelle (1) anschließbaren Auslass (2e) für die Versorgung des Phasenstellers, vorzugsweise über die Nockenwelle (1) aufweist, wobei der Einlass (2d) für eine Anordnung der Druckspeichereinrichtung (40) in einem Hauptstrom (50-53) zum Steuerventil (10, 20) zusätzlich zum Auslass (2e) vorgesehen ist oder für eine vom Hauptstrom abgezweigte Anordnung der Druckspeichereinrichtung (40) in einem Nebenstrom auch den Auslass bilden kann.
18. R. Vorrichtung nach einem der Absätze A bis Q in Kombination mit Anspruch N, dadurch gekennzeichnet, dass die Druckspeichereirichtung (40) und die Rücksperreinrichtung (51) in einem an der Brennkraftmaschine montierbaren oder bereits montierten Anbaugehäuse (2a, 2b, 2c) angeordnet sind.
19. S. Vorrichtung nach Absatz R, dadurch gekennzeichnet, dass an einer Montageseite des Anbaugehäuses (2a, 2b, 2c) eine Dichtung (56), die eine Drehachse (R) des Stators (3) und des Rotors (7) umgibt, mittels wenigstens eines Zentrierelements (57), das von einer die Drehachse (R) umgebenden Fügefläche des Anbaugehäuses (2a, 2b, 2c) vorzugsweise vorragt, form- oder reibschlüssig verliersicher gehalten wird.
20. T. Vorrichtung nach einem der Absätze A bis S, dadurch gekennzeichnet, dass die Vorrichtung an der Brennkraftmaschine montiert und mit dem Zuführzweig (50-53) und dem Abführzweig (4') an ein Schmierölsystem der Brennkraftmaschine angeschlossen ist.

The present application is directed to the locking of the phaser. It should be noted, however, that in connection with this inventive concept described further inventive concept can be used without this basic idea with advantage. The Applicant reserves the right to apply to a device according to the features (a) to (d), optionally also the features (e) and (f), a separate application, for example, the connection of the locking device with the Entriegelungsstellkammer, namely either the Frühstellkammer, and then preferably only with the Frühstellkammer, or the Spätstellkammer, and then preferably only with the Spätstellkammer concerns. Yet another independent object, which need not necessarily be associated with the features (e) to (h) of claim 1, is the formation of the locking pin as a stepped piston and the resulting plurality of pressure surfaces, at least two pressure surfaces, with the same pressure fluid, preferably the pressurized fluid from the Entriegelungsstellkammer or for the Entriegelungsstellkammer (n) certain pressure fluid. Yet another independent object is the eccentric arrangement of the locking pin in a rotor blade relative to the circumferential direction. This concept of the invention can also be realized in principle without claim characteristics (e) to (h). However, an accumulator device is preferably also provided in such embodiments, which may be formed with respect to the pressure levels such as Füllbeginndruck, hot idling pressure, minimum filling pressure of the full filling and Entriegelungsemindestdruck advantage as under at least one of the above-explained aspects. So the following feature combinations are also beneficial:

1. A. Device for adjusting the rotational angular position of a camshaft relative to a crankshaft of an internal combustion engine, the device comprising
   1. (a) a stator (3) rotatably driven in fixed speed relation by the crankshaft,
   2. (b) a rotor (7) which can be driven in rotation by the stator (3) and rotatably drives the camshaft (1) with this rotor (7),
   3. (C) an early adjustment chamber (8) for generating a torque acting on the rotor (7) relative to the stator (3) in the direction of advance and a late adjustment chamber (9) for generating a on the rotor (7) relative to the stator (3) in Direction lag acting torque which can be acted upon to generate the respective torque with a pressurized fluid whose pressure also increases with increasing rotational speed of the crankshaft in order to be able to adjust the rotational angular position of the rotor (7) relative to the stator (3),
   4. (d) and a supply branch (50-53) for the supply and a discharge branch (4 ') for the discharge of the pressurized fluid to and from the adjusting chambers (8, 9).
2. B. Device according to paragraph A, further comprising a Zuführzweig (50-53) arranged pressure storage device (40) with a spring means (43) and a storage chamber (41) which is filled against a restoring spring force of the spring means (43) with the pressurized fluid , includes.
3. C. The device according to paragraph B, characterized in that the storage chamber (41) begins to fill against the spring force at a Füllbeginndruck (P _FB ) which is at most as high as a hot idle pressure (P _HL ), the pressurized fluid in the warm operating condition having idling of the internal combustion engine.
4. D. Device according to paragraph C, characterized in that the storage chamber (41) fills when the hot idle pressure (P _HL ) is exceeded against the spring force.
5. E. Device according to one of the paragraphs A to D, comprising a locking device (30) mechanically in a locking engagement, the rotor (7) in a certain rotational angular position relative to the stator (3) fixed and by applying the pressure fluid in a the adjustment of Rotary angular position of the rotor (7) permitting release state changes when the pressure of the pressurized fluid has reached a minimum release pressure (P _E ) which is at most as high as the hot empty pressure (P _HL ) or the Füllbeginndruck (P _FB ).
6. F. Device according to one of the paragraphs A to E in combination with B, characterized in that the pressure storage device (40) according to volume and cross-sectional area of the storage chamber (41) and spring force is designed so that the actuating speed (φ / s), with the the rotational angle position of the rotor (7) relative to the stator (3) is adjusted to at least 1.5 times, preferably up to at least twice the idle speed of the internal combustion engine even at momentary pressure drop in the upstream of the pressure storage device (40) part of the Zuführzweigs (50-53 ) is adjusted for the pressure fluid by subsequent delivery from the pressure storage device (40) the frequency of the combustion cycles of the internal combustion engine, such that the ratio of Servo speed and crankshaft speed to at least 1.5 times, preferably to at least twice the idling speed is at least substantially constant.
7. G. Device according to one of the paragraphs A to F, comprising a locking device (30) in a locking engagement, the rotor (7) in a certain. Rotary angular position relative to the stator (3) fixed mechanically and by admission to the pressure fluid in an adjustment of the rotational angular position of the rotor (7) permitting release state, wherein the locking means (30) for releasing the locking engagement with the Frühstellkammer (8), preferably only with the Frühstellkammer (8), or the Spätstellkammer (9), preferably only with the Spätstellkammer (9), is connected.
8. A device according to any one of paragraphs A to G, comprising locking means (30) having a locking spring (32) and a locking pin (31; 60; 70) against locking spring return of the locking spring (32) from a locking engagement in which it mechanically fixes the rotor (7) in a specific rotational angle position relative to the stator (3), is movable into a release position by application of pressure to the pressurized fluid, in which it permits the adjustment of the relative rotational angular position of the rotor (7).
9. I. Device according to paragraph H, characterized in that the locking pin (31; 70; 80) via the locking spring (32) on one of the rotor (7) and stator (3) is supported and of the one rotor (7) and Stator (3) between the locking engagement and the release position movable back and forth, preferably axially movable.
10. A device according to paragraph H or I, characterized in that the locking pin (31; 60; 70; 100) is engaged with an engaging portion (31b; 61,62; 71,72; 101,102) in locking engagement with a receptacle (33; 80; 90; 110) which is formed in one of stator (3) and rotor (7), and in the case of existing locking engagement outside the receptacle in the other of the stator (3) and rotor (7) located annular first pressure surface ( 31c; 63; 103) and a second pressure surface (31d; 64; 104) which is in the receptacle when there is a locking engagement, which are beauchlaglagbar respectively for releasing the locking engagement with the pressurized fluid, and the pressure surfaces are interconnected, preferably via a reference on the locking device (30) inner connecting channel (38), so that the pressure fluid for releasing the locking engagement to one of the pressure surfaces and from there to the other of the pressure surfaces passes, preferably via the inn he connecting channel (38).
11. K. Device according to one of the paragraphs H to J, characterized in that the locking pin (31; 60; 70; 100) is provided with an engagement region (31b; 61,62; 71,72; 101,102) in locking engagement in a receptacle (31; 33; 80; 90; 110) formed in the stator (3), and in the rotor (7), a communication passage (34) of either the early-stage chamber (8) or the late-stage chamber (9) to a peripheral guide surface of the lock pin (31 60; 70; 100) and along the circumferential guide surface of the locking pin, a further connecting channel (38) for receiving (33; 80; 90; 110) leads to pressurized fluid from either the Frühstellkammer (8) or the Lätstellkammer (9) in the receptacle to guide and a pressure surface (31 d, 64, 74, 104) of the locking pin (31, 60, 70, 100) to act on the pressurized fluid for unlocking.
12. Device according to one of the paragraphs H to K, characterized in that the rotor (7) movably supports the locking pin (31; 60; 70) and has an outer connecting channel (34), which is in relation to the locking device (30) one of the adjusting chambers (8, 9), preferably in the early adjustment chamber (8), opens and connects the locking device (30) for releasing the locking engagement with this adjusting chamber (8),
13. M. Device according to one of the paragraphs H to L, characterized in that the locking pin (31; 60; 70) arranged in a wing (7a) of the rotor (7) movable and seen in an end view of the rotor (7) in the circumferential direction eccentrically is.
14. Device according to one of the paragraphs H to M, characterized in that the locking pin (31; 60; 70) is axially movable in a vane (7a) of the rotor (7) and closer to the radial end of the vane (7a) than the axis of rotation (R) of the rotor (7) is arranged.
15. O. Device according to one of the paragraphs H to N in combination with paragraph B, further comprising a restraining device (51) which is arranged in the feed branch (50-53) upstream of the pressure storage device (40) and the supply of the pressurized fluid to the adjusting chambers ( 8, 9) and the pressure storage device (40) allows, but prevents backflow, wherein between the pressure storage device (40) and the adjusting chambers (8, 9) preferably no further to be supplied with the pressurized fluid unit is arranged.
16. P. Device according to one of the paragraphs A to O, characterized in that the phaser is adapted for mounting on an axial end of the camshaft (1) and in the mounted state with respect to the axis of rotation (R) of the camshaft (1) or the arrangement of stator (3) and rotor (7) central control valve (10, 20) with an axial inlet (P _a , 22) for an axial loading of a reciprocally movable valve piston (20) of the control valve (10, 20) with the pressure fluid, that the pressure fluid to the control valve (10, 20) in the assembled state, preferably via the camshaft (1) can be fed.
17. Q. Device according to paragraph P in combination with paragraph B, characterized in that the pressure storage device (40) connectable to the Zuführzweig (50-53) inlet (2d) for the pressurized fluid and one connected to the control valve (10, 20) or connectable, preferably to the camshaft (1) connectable outlet (2e) for the supply of the phaser, preferably via the camshaft (1), wherein the inlet (2d) for an arrangement of the pressure storage device (40) in a main flow (50-53 ) to the control valve (10, 20) in addition to the outlet (2e) is provided or for a branched off from the main flow arrangement of the pressure storage device (40) in a side stream can also form the outlet.
18. R. Device according to one of the paragraphs A to Q in combination with claim N, characterized in that the Druckspeichereirichtung (40) and the Rücksperreinrichtung (51) in a mounted on the internal combustion engine or already mounted mounting housing (2a, 2b, 2c) are arranged ,
19. S. Device according to paragraph R, characterized in that on a mounting side of the attachment housing (2a, 2b, 2c), a seal (56) which surrounds a rotation axis (R) of the stator (3) and the rotor (7), by means of at least a centering element (57), which protrudes from a rotational axis (R) surrounding the joining surface of the attachment housing (2a, 2b, 2c) preferably, is positively or frictionally held captive.
20. T. Device according to one of paragraphs A to S, characterized in that the device is mounted on the internal combustion engine and connected to the Zuführzweig (50-53) and the Abführzweig (4 ') to a lubricating oil system of the internal combustion engine.

Figur 1

einen Nockenwellen-Phasensteller in einem verriegelten Zustand,

Figur 2

den Nockenwellen-Phasenstellers in einem entriegelten Zustand,

Figur 3

den Phasensteller in einem Querschnitt,

Figur 4

eine Verriegelungseinrichtung des Phasenstellers im Querschnittsdetail X der Figur 3,

Figur 5

die Verriegelungseinrichtung in einem Längsschnitt,

Figur 6

den Phasensteller und eine zugeordnete Druckspeichereinrichtung in einem Schnitt,

Figur 7

ein Anbaugehäuse, in dem der Nockenwellen-Phasensteller gemeinsam mit der Druckspeiehereinrichtung angeordnet ist,

Figur 8

das Anbaugehäuse mit an einer Montageseite angeordneter Dichtung,

Figur 9

ein Detail der Dichtung,

Figur 10

die Verriegelungseinrichtung für Vergleichszwecke,

Figur 11

eine verbesserte Verriegelungseinrichtung eines ersten erfindungsgemäßen Beispiels,

Figur 12

eine verbesserte Verriegelungseinrichtung eines zweiten erfindungsgemäßen Beispiels,

Figur 13

eine verbesserte Verriegelungseinrichtung eines dritten erfindungsgemäßen Beispiels und

Figur 14

ein vergrößertes Detail der Figur 13.

Hereinafter, embodiments of the invention will be explained with reference to figures. The features disclosed in the exemplary embodiments advantageously continue to form the subject-matter of the claims individually and in any combination of features, as well as the embodiments described above. Show it:

FIG. 1

a camshaft phaser in a locked state,

FIG. 2

the camshaft phaser in an unlocked state,

FIG. 3

the phaser in a cross section,

FIG. 4

a locking device of the phaser in the cross-sectional detail X of FIG. 3 .

FIG. 5

the locking device in a longitudinal section,

FIG. 6

the phaser and an associated pressure storage device in a section,

FIG. 7

a mounting housing, in which the camshaft phaser is arranged together with the pressure-profiling device,

FIG. 8

the mounting housing with arranged on a mounting side seal,

FIG. 9

a detail of the seal,

FIG. 10

the locking device for comparison purposes,

FIG. 11

an improved locking device of a first example according to the invention,

FIG. 12

an improved locking device of a second example according to the invention,

FIG. 13

an improved locking device of a third example according to the invention and

FIG. 14

an enlarged detail of the FIG. 13 ,

FIG. 1 shows a camshaft phaser in a longitudinal section. The camshaft phaser is arranged at an end face of a camshaft 1 and serves to adjust the phase position, ie the rotational angular position of the camshaft 1 relative to a crankshaft of an internal combustion engine, for example a drive motor of a motor vehicle. The camshaft 1 is rotatably mounted about an axis of rotation R in a machine housing 2 of the internal combustion engine, for example in a cylinder head housing.

The camshaft phaser comprises a stator 3, which can be rotated by the crankshaft, and a rotor 7, which can be connected in a rotationally fixed manner to the camshaft 1. The stator 3 is composed of a drive wheel 4, for example a sprocket, a cover 6 and an impeller 5 arranged axially between the drive wheel 4 and the cover 6. The drive wheel 4, the impeller 5 and the lid 6 are rotatably connected to each other. The assembly of the stator 3 is only an example. Alternatively, the stator 3 can also be composed of more than or instead of the three parts 4, 5 and 6 also of only two parts, for example of an integral part 4, 5 and the part 6 or the part 4 and a one-piece part 5, 6. Basically, it can also be formed into a single piece. The drive wheel 4 can be formed circumferentially on the outside of the impeller 5 and the cover area of the drive wheel 4, which laterally seals the stator-rotor arrangement, forms part of the rotor 7. In addition to or instead of the cover area formed by the drive wheel 4, the cover 6 may be part of the rotor 7. The stator 3 and the rotor 7 form a hydraulic swing motor.

FIG. 3 shows the stator-rotor assembly 3, 7 in a cross section. The impeller 5 forms an outer component and the rotor 7 an inner component of the pivot motor. The hollow impeller 5 has at its inner periphery radially inwardly projecting wings 5a. The rotor 7 has radially outwardly projecting wings 7a, which form with the blades 5a of the stator 3 first control chambers 8 and second control chambers 9. The adjusting chambers 8 are arranged in the circumferential direction in each case to one side and the adjusting chambers 9 in each case to the other side of the wings 7 a of the rotor 7. If the adjusting chambers 8 are pressurized and the adjusting chambers 9 are relieved, the rotor 7 rotates relative to the stator 3 in FIG FIG. 3 clockwise to maximum in the FIG. 3 assumed end position. If the adjusting chambers 9 are pressurized and the adjusting chambers 8 relieved in pressure, the rotor 7 rotates counterclockwise. The rotational movement relative to the stator 3 in one direction of rotation corresponds to an overfeed and the relative rotational movement in the other direction to a lag of the camshaft 1 relative to the crankshaft.

In the exemplary embodiment, the adjusting chambers 8 are early adjusting chambers and the adjusting chambers 9 are late setting chambers. In FIG. 3 takes the rotor 7 relative to the stator 3, the early position in which the camshaft leads relative to 1 of the crankshaft. If, instead, the late setting chambers 9 are acted on by the pressure fluid and the early adjusting chambers 8 are relieved, the rotor 7 rotates in the direction of lag until at most a retarded position. The early position and the late position are each specified by a stop contact. In each of the two end or extreme positions, at least one of the rotor blades 7a is in a stop contact with one of the stator blades 5a. In preferred embodiments, the rotor 7 can not only be rotated back and forth relative to the stator 3 between these two rotational angle end positions, but can also be hydraulically fixed in any intermediate position by appropriate pressurization of both the early adjustment chambers 8 and the late adjustment chambers 9.

The camshaft phaser has a control valve centrally arranged with respect to the stator-rotor arrangement 3, 7, with a valve housing 10 and a valve piston 20 which is arranged axially to and fro in an adjustable way in the valve housing 10 (FIG. Fig. 1 ). The valve piston 20 is hollow with an axially extending cavity 21, a piston inlet 22 at one axial end and a piston outlet 23, which leads radially through a jacket of the valve piston 20 surrounding the cavity 21. The valve piston 20 has at its side facing away from the piston inlet 22 the other axial end of a coupling member 25 for a coupling with an actuator 15, which causes the axial displacement of the valve piston 20. The coupling member 25 acts as an actuating tappet of the valve piston 20. The coupling member 25 may be integrally formed with the piston skirt surrounding the cavity 21 in one piece or optionally be axially fixed with this. It protrudes at the front end of the valve piston 20, which faces the actuator 15 axially. The coupling member 25 extends through an end closure wall 11 of the valve housing 10. The end closure wall 11 surrounds the coupling member 25 in close fitting and thus ensures in spite of the reciprocating coupling member 25 for the fluid-tight closure of the valve housing 10th

The actuator 15 is an electromagnetic actuator, in the embodiment, a Axialhub electromagnet, with a current-carrying coil 16 and an armature 17, which surrounds the coil 16. The coil 16 is rotatably connected to the engine housing 2 of the internal combustion engine. In the exemplary embodiment, the coil 16 is rotatably connected to a cover 2b, which in turn is fixedly connected to a mounted on the machine housing 2 mounting housing part 2a. The armature 17 is axially movable relative to the coil 16. It is with the coupling member 25 directly in a coupling engagement, which is formed as an axial pressure contact. When energizing the coil 16 acts on the armature 17 an axially directed towards the coupling member 25 actuating force acting on the coupling member 25 and thus on the valve piston 20 in the coupling engagement, a pure axial pressure contact. At the point of separation between the valve piston 20 rotating with the camshaft 1 during operation and the non-rotating actuator 15, preferably only point contact prevails. The armature 17 preferably has a spherical surface at its end contacting the coupling member 25. Alternatively or additionally, the coupling member 25 may have a spherical surface at its front end. In a further development, the contact end of the armature 17 is formed as a ball sliding bearing by a ball in a pan of the armature 17 is freely rotatably mounted there.

The control valve comprises a spring member 14 whose spring force counteracts the actuating force of the actuator 15. The spring member 14 is supported directly on the valve housing 10 and in the direction of the actuator 15 on the valve piston 20. The actuator 15 is driven by a control of the internal combustion engine, namely energized. The control is preferably carried out via a stored in a memory of the engine control map, for example, depending on the speed of the crankshaft, the load or other or other relevant for the operation of the internal combustion engine parameters.

The valve piston 20 is arranged in a central axial cavity of the valve housing 10 in the manner explained back and forth movable. It has at its end facing away from the end closure wall 11 of the axial end of an axial, central leading into the housing cavity housing inlet P _a, which can be fed via the camshaft 1, namely, a pressure inlet P of the camshaft 1, fluid under pressure. The fluid may in particular be a lubricating oil serving for lubricating the internal combustion engine, which also serves for lubricating, for example, the track bearing of the camshaft 1. The pressurized fluid is supplied to the control valve by way of example as preferred by the thrust bearing of the camshaft 1, that is, the pressure port P is connected to the lubricating oil supply for the thrust bearing. This pressurized fluid flows into the camshaft 1 at P, through the axial housing inlet P _a into the valve housing 10 and through the piston inlet 22 in axial alignment with the housing inlet P _a into the cavity 21. From the cavity 21 branches off laterally, by way of example as preferred in the radial direction, a piston outlet 23 through which the pressurized fluid is supplied depending on the axial position of the valve piston 20 either the Frühstellkammern 8 or the Spätstellkammern 9 to the phase position of the rotor 7 relative to the stator. 3 and thus to adjust the phase angle of the camshaft 1 relative to the crankshaft. The piston outlet 23 is formed by radial passages distributed over the circumference of the valve piston 20 through the jacket of the valve piston 20. The piston outlet 23 is arranged in an axially central portion of the valve piston 20.

The valve housing 10 has through its jacket leading connections for the supply and discharge of the fluid to and from the adjusting chambers 8 and 9. These are a working connection A and a working connection B, a reservoir connection T _a assigned to the working connection A and a reservoir connection T _B assigned to the working connection B. The connections A to T _B are in each case straight passages through the jacket of the valve housing 10. The connections A, B and T _A extend radially over the shortest path through the jacket. The reservoir port T _B extends obliquely outward into the phaser housing 2 a. The working port B of the valve housing 10 is arranged distributed over the circumference of the valve housing 10, radially extending and therefore short passages formed by the jacket of the valve housing 10. The terminals A, T _A and T _B are also each formed by a plurality of distributed around the central axis R arranged passageways.

FIG. 1 shows the valve piston 20 in a first axial piston position in which it holds the spring member 14. In the first piston position, the piston outlet 23 is connected to the working port B. The pressure fluid supplied via the pressure port P of the camshaft 1 flows in the axial direction through the axial housing inlet P _a and the piston inlet 22 into the cavity 21 of the valve piston 20 and from there through the branching piston outlet 23 to that shown in FIG FIG. 1 The adjusting chambers 8 associated with the working connection A are connected via the working connection A and a recess 26 formed on the outer circumference of the valve piston 20 to the reservoir connection T _A and via this and a return 4 'rotating with the camshaft 1 connected to the reservoir and thus relieved in pressure. The recess 26 extends 360 ° circumferentially about the outer circumference of the valve piston 20. From the recess 26 from the rear seen in the axial direction behind the piston outlet 23, a further axially extending recess 27 is formed on the outer periphery of the valve piston 20, which also extends beyond the outer Extending circumference of the valve piston 20 circumferentially. The recess 27 is connected to the reservoir port T _B in the first piston position. The reservoir port T _B is assigned to the working port B. However, in the first piston position it is fluidically separated from the working port B by means of a sealing web of the valve piston 20 formed between the piston outlet 23 and the recess 27.

If the armature 17 is acted upon by a corresponding energization of the actuator 15 with a force exceeding the spring force of the spring member 14, the actuator 15 pushes the valve piston 20 from the illustrated first piston position axially in the direction of the housing inlet P _A and with correspondingly large actuating force to an axial second piston position, in which no longer the working port B, but the other working port A is connected to the piston outlet 23. In the second piston position, a sealing web of the valve piston 20 formed between the piston outlet 23 and the recess 26 separates the working port A from the associated reservoir port T _A , so that in the second piston position the actuating chambers 9 are acted upon by the pressure fluid. Furthermore, in the second piston position, the recess 27 connects the working port B with the reservoir port T _B , so that the fluid can flow out of the adjusting chambers 8 and these are relieved of pressure. The rotor 7 moves accordingly in the illustration of FIG. 3 counterclockwise relative to the impeller 5 and thus to the stator 3. The rotatably connected to the rotor 7 camshaft 1 is adjusted in its phase position relative to the crankshaft by the same rotational angle.

The high-pressure side fluid flowing into the control valve through the housing inlet P _a urges the valve piston 20 with a first axial force acting in the direction of the actuator 15. To compensate for this first axial force of the valve piston 20 in the direction of the actuator 15 can be flowed through, so that at its the actuator 15 facing rear between this back and the end closure wall 11, a fluid pressure builds up on the back of the valve piston 20, a counterforce, a second Exerts axial force. Since the projected by the pressurized fluid projection surface is reduced by the cross-sectional area with which the coupling member 25 protrudes through the end closure wall 11, the axial counterforce, the second axial force corresponding to the cross-sectional area of the coupling member 25 would be less than the first axial force. It would result in a resulting axial thrust, which would change according to the difference of the projection surfaces as a function of the pressure of the fluid. The characteristic of the control valve would change accordingly, which can lead to significant distortions, since the pressure of the fluid can fluctuate during operation of the internal combustion engine.

To increase the second axial force, the valve piston 20 has a radially expanded piston portion 28, in the following widening 28, and the valve housing 10 has a suitably widened housing portion 18, which surrounds the widening 28 in a tight fit. As far as the valve housing 10 and the valve piston 20 cooperate sealingly, the valve piston 20 at its outer periphery with the exception of the expansion 28, for example everywhere the same cylindrical cross-section. In order to guide the pressure fluid to the rear side of the valve piston 20, the valve piston 20 seen from the housing inlet 22 has an axial position behind the piston outlet 23 Feeder 24, which is formed by a plurality of distributed around the central axis R through channels, which are formed in a valve piston bottom. The widening 28 and corresponding to the housing section 18 are dimensioned such that the enlargement of the projection surface F ₂₈ facing the actuator 15 due to the widening 28 compensates at least a predominant part of the cross-sectional area F _{25 of} the coupling element ₂₅ "lost" for the compensation ( FIG. 2 ). The compensation surface is an outer ring surface of the projection surface F ₂₈ . Preferably, the additional, the end closure wall 11 axially facing projection surface, the compensation surface of the expansion 28, just as large as the cross-sectional area F ₂₅ , with which the coupling member 25 protrudes through the end closure wall 11. In this way it is achieved that the force acting in the direction of the actuator 15 first axial force is compensated by the opposing second axial force and resulting axial thrust can not arise. The projection surfaces which each generate an axial force when the valve piston 20 flows through are of the same size in both axial directions.

The expansion 28 is preferably formed on the actuator 15 facing the front end of the valve piston 20. The widened housing portion 18 has a sufficient axial extent to allow the adjustment movements of the valve piston 20. The widening 28 forms the end of the recess 27 facing the actuator 15. The widened housing section 18 tapers at 13 onto the narrower cross section, which is constant in the further axial course. The taper 13 is formed within the recess 27, axially by way of example in the region of the reservoir port T _B.

The phase adjuster comprises a locking device 30, which mechanically fixes the rotor 7 in a specific rotational angle position relative to the stator 3 in a locking engagement. As an example, it fixes the rotor 7 as preferred in the early position. By applying the pressure fluid, the locking device 30 can be brought out of the locking engagement in a release state. If the locking device 30 is in the release state, the rotor 7 can rotate relative to the stator 3 when pressure is applied to either the control chambers 8 or the control chambers 9 and corresponding pressure relief of the respective other control chambers 9 or 8, ie changes the rotational angular position of the rotor 7 relative to the stator 3 become. For unlocking against a spring force Entriegelungsemindestdruck P _{E is} required. The unlocking minimum pressure P _E is in preferred embodiments at most as large as the hot idle pressure P _HL in the pressure fluid supply to the phaser. The hot idling pressure P _HL can be measured, in particular, at a back-up device which is arranged in the pressure fluid supply in the vicinity of the phaser in order to prevent backflow of the pressure fluid from the phaser then, when the pressure in the pressure chambers acted upon with the pressurizing fluid 8 or 9 is higher than the supply pressure immediately upstream of the Rücksperreinrichtung. The Rücksperreinrichtung can be formed in particular by a check valve.

The locking device 30 comprises a relative to the stator 3 and rotor 7 axially reciprocable locking pin 31 and a locking spring 32 which biases with its spring force the locking pin 31 in an axial direction in the locking engagement. The locking pin 31 is supported on the rotor 7 via the locking spring 32 and guided axially reciprocally in a guide 36 in one of the rotor blades 7a. In the locking engagement, it protrudes axially beyond an end face of the respective rotor blade 7a into an axially opposite receptacle 33 of the stator 3. The receptacle 33 is formed as a recess on a rotor 7 facing end side of the stator 3, for example in the lid portion of the drive wheel 4. Die Verriegelungseinrichtung 30 is connected to either one of the adjusting chambers 8 or the adjusting chambers 9, preferably only one of the Frühstellkammern 8, so that when pressure is applied to the corresponding adjusting chambers of the locking pin 31 against the spring force of the locking spring 32 moves out of the locking engagement and the mechanical fixation of the rotor 7 solved becomes. The space in the rotor 7, in which the locking spring 32 is arranged, is connected via a discharge line 39 to the low-pressure side of the pressurized fluid system, so that the locking pin 31 of the receptacle 33 axially opposite can not build up unlocking preventing back pressure.

FIG. 2 shows the phaser in the unlocked state. The unlocking minimum pressure P _E is reached or exceeded, so that the rotor 7 can be hydraulically adjusted by means of the control valve. The rotor 7 is already no longer in the early position.

From the FIGS. 3 to 5 Details of the locking device 30 can be seen. The locking pin 31 forms a stepped piston with a guide portion 31 a, which is always guided in the rotor blade 7 a, and a contrast slimmer engagement portion 31 b, which in the in FIG. 5 shown locking engagement engages the receptacle 33 of the stator 3. Locking pin 31 has a pressure surface 31d in locking engagement with receiver 33d and a further annular pressure surface 31c remote therefrom. The pressure surfaces 31c and 31d act in the same direction. The pressure surface 31c closes an annular pressure space 37, which is formed inside the rotor 7a, at an end face. The receptacle 33, more precisely the space bounded by the pressure surface 31d within the receptacle 33, is connected to the pressure space 37 via a connecting channel 38, which is connected with respect to the locking device 30, so to speak, is short-circuited. The connecting channel 38 extends in the rotor blade 7a to the front side of the rotor 7 through a narrower guide portion of the guide 36, which engages closely the engaging portion 31b of the locking pin 31, so that the locking pin 31 not only in its wider portion 31a, but also in the engaging portion 31b is guided.

The circumferentially bounded by the guide 36 space is closed at its opposite in the locking engagement of the receptacle 33 end by means of an inserted support member 35. The locking spring 32 is supported with a spring end on the support element 35 and with its other spring end on the locking pin 31. In the support member 35, a vent passage 39a is formed, which connects the space between the support member 35 and locking pin 31 with the secondary lead 39, which is connected to the low pressure side of the pressure fluid system, so that can not build up the unlocking significantly obstructing backpressure. For recording 33 it should also be noted that their rotor blade 7a facing the opening edge 33a is circumferentially beveled to facilitate the retraction into the locking engagement, especially since the locking pin 31 is preferably cylindrical in the engagement portion 31b. Furthermore, it is preferable to provide for a certain amount of clearance, preferably in extension of the connecting channel 38, in order to create a low-loss connection between the pressure chamber 37 and the further pressure space in the receptacle 33 bounded by the pressure surface 31d. In the receptacle 33 is as preferred, but only optionally formed a flat, raised Abragung on which in locking engagement, the pressure surface 31d abutment, so that there is a certain residual volume for the pressure fluid in the locking engagement to the Abragung.

The locking device 30 is connected for unlocking with the nearest early setting chamber 8 through a connecting channel 34. The connecting channel 34 leads from the pressure chamber 37 through the rotor blade 7a directly into the early adjustment chamber 8 and closes it with the locking device 30 advantageously short. The pressure chamber 37 is therefore connected to the early setting chamber 8 in a particularly low-resistance manner, so that its pressure is virtually free from loss and distortion in the pressure chamber 37 and also via the inner connecting channel 38 in the receptacle 33 when the pressure changes. As soon as the pressure in the early adjustment chamber 8 has reached the minimum unlocking pressure P _E , this pressure is practically instantaneously applied to the pressure surfaces 31 c and 31 d so that the locking pin 31 moves out of the locking engagement and the rotor 7 increases by increasing the pressure in the retarding chambers 9 can be adjusted via the pressure in the Frühstellkammern 8 in the direction of the late position. Any pressure fluctuations in the early adjustment chamber 8 directly connected to the locking device 30 are even helpful for releasing the locking engagement, since the locking pin 31 is thereby freed, so that it briefly acts on these vibrations of the rotor 7 from the transverse locking engagement due to the drag torque of the camshaft - Is relieved or shear force. In FIG. 3 the direction of rotation of the stator 3 is shown with a direction of rotation arrow D. The rotor 7 and the torsionally stiff connected camshaft 1 are taken in tow. A portion of the torque is also transmitted in locking engagement, whereby the mentioned lateral force acts in the drawn direction of rotation on the engagement region 31b of the locking pin 31.

The inner connecting channel 38 is, as in the FIGS. 3 and 4 can be seen, advantageously groove-shaped in the guide 36 in a radial with respect to the axis of rotation R range, for example, outside arranged. As a result, the required for receiving the lateral force circumferential surface of the guide 36 is reduced as little as possible. Also advantageous is the arrangement of the locking device 30 near the radial end of the rotor blade 7a, as this contributes to the reduction of the transverse force to be absorbed. At the same drag torque would cause a more central arrangement, closer to the axis of rotation of the rotor 7, the reduction of the lever corresponding to a larger lateral force.

An advantage is an eccentric arrangement with respect to the circumferential direction of the locking device 30 in the rotor blade 7a. The locking device 30 is arranged in this eccentric arrangement in the circumferential direction closer to the side surface of the rotor blade 7a delimiting the early adjustment chamber 8 than in the side area which is opposite in the circumferential direction and delimits the late setting chamber 9. If the late setting chamber 9 is acted upon to adjust the rotor 7 in the direction of the late position, there is a comparatively long sealing web between the late setting chamber 9 and the locking device 30, in particular on the side of the stator 3 on which the receptacle 33 is arranged. The rotor blade 7a receiving the lock pin 31 is wider in the circumferential direction than the other rotor blades 7a. This creates space for the locking device 30 and in conjunction with the eccentric arrangement in the circumferential direction again extended to Spätstellkammer 9 toward sealing ridge on the rotor blade end faces. The circumferentially measured distance between the left and right adjacent stator blades 5a is also increased by the enlarged width of the wider rotor blade 5a. Finally, it should also be noted that the rotor blade 7a, in which the locking device 30 is formed, in the in FIG. 3 illustrated early position in the late setting chamber 9 has a certain distance from the nearest inwardly projecting wing of the impeller 5, so that even in the early position there remains a certain chamber volume and pressure not only significant gap resistances must be overcome.

FIG. 3 also shows the short and direct fluid connections 7b, which lead from the central control valve 10, 20 through the rotor 7 to the control chambers 8 and 9, respectively. On average, the FIG. 3 These are the fluid connections 7b to the working ports A for the late adjustment chambers 9. The fluid connections leading from the control valve to the Frühstellkammern 8 are axially and circumferentially offset from the fluid connections 7b and extends. The Fluid connections 7b and also the fluid connections for the early adjustment chambers 8 are straight, at least substantially radially extending holes which open at their radially inner ends to the valve housing 20 and at their outer ends in the root regions of the rotor blades 7a in the respective control chamber 8 and 9 respectively.

FIG. 6 shows the phaser with an associated pressure storage device 40. The pressure storage device 40 has a storage chamber 41 and a movable wall structure 42, which limits the storage chamber 41 on one side. Furthermore, it has a spring device 43 against whose restoring spring force the wall structure 42 for filling the storage chamber 41 is movable. The wall structure 42 is formed as a piston. The spring device 43 consists of a single mechanical spring, by way of example as preferred of a claimed when loading the storage chamber 41 to pressure coil spring. The wall structure 42 is freely movable back and forth, so that their chamber pressure is always distortion-free available in the at least partially filled state.

The pressure storage device 40 is arranged in the flow path of the pressurized fluid to the phaser upstream of the control valve 10, 20. The phaser is connected via a feed channel 50 to the pressurized fluid system. In the feed channel 50 is a Rücksperreinrichtung 51, for example a check valve, upstream of the phaser and the pressure storage device 40 is arranged, which prevents a backflow of pressurized fluid. In the feed channel 50, a filter element 52 is also disposed between the Rücksperreinrichtung 51 and the storage chamber 41. If, in the supply system, the fluid pressure immediately upstream of the restraint device 51 exceeds the pressure between the restraint device 51 and the phaser, in the selected arrangement the pressure in the storage chamber 41, the restraining device 51 opens in the direction of the pressure storage device 40, so that this corresponding to the pressure and can partially or completely fill the restoring spring force of the spring device 43. The maximum filling volume is reached when the wall structure 42 abuts against a stop of the pressure storage device 40. The storage chamber 41 is connected via a short path via a downstream downstream feed channel 53 with the phaser. In the exemplary embodiment, the connection is made via the camshaft 1. Via a discharge channel 46 ensures that the storage chamber 41 can fill without significant backpressure. The discharge channel 46 connects the space at the rear of the movable wall structure 42 with the low pressure side of the pressurized fluid supply system.

The storage chamber 41 is covered at an open side by a lid 2c. The lid 2c forms as preferred, but only by way of example, a stop for the piston 42 and the other as preferred, but also only by way of example, an inlet 2d leading directly into the storage chamber 41 and an outlet 2e leading directly from the storage chamber 41. The Storage chamber 41 is connected to the feed channel 50 via inlet 2d and to downstream feed line 53 leading to phaser via outlet 2e. The feed channel 53 extends as preferred, but only as an example along the storage chamber 41, in the example parallel to the direction of movement of the piston 42, and to the lid 2c, where it opens into the outlet 2c. The pressure storage device 40 is arranged in a leading to the phaser main flow of the pressurized fluid by the example by way of the machine housing 2 and the connected feed channel 50 supplied pressurized fluid only via the pressure storage device 40 while flowing through the storage chamber 41 in the advancing to the phaser feed channel 53 and this example again passes through the machine housing 2 to the pressure port P.

Instead of forming the inlet 2d or the outlet 2e on the side of the lid 2c facing the storage chamber 41, if appropriate in addition, an inlet connecting the feed channel 50 to the storage chamber 41 or an outlet connecting the storage chamber 41 to the storage chamber 41 may be provided Control valve leading supply channel 53 connects, be formed on the cover 2c facing the end face of the attachment housing 2a, for example, as one or a respective groove-shaped recess on the lid 2c facing the end of the storage chamber 41 surrounding wall. It is merely necessary to ensure that a certain space remains between the piston 42 and the cover 2c, which space is connected to the supply channel 50 or the supply channel 53 via the inlet or outlet formed in such an alternative manner. This solution offers cost advantages in the production, since the lid 2c in such embodiments on its the storage chamber 41 facing end face can be easily plan formed.

The acted upon by the pressurized fluid in the storage chamber 41 surface of the wall structure 42 and the spring stiffness and optionally an existing without pressurization spring preload of the spring means 43 are tuned to the system pressure in the pressurized fluid supply system that the storage chamber 41 begins to fill at the latest when in the pressurized fluid supply system, the hot idle pressure P _{HL is} reached. The Füllbeginndruck P _FB is the pressure at which the filling begins, ie in which the wall structure 42 is moved against the restoring spring force of the spring means 43 and an increase in the filling volume against a minimum volume of the storage chamber 41 begins. The minimum volume may be zero, but in practice the storage chamber 41 will have some residual volume in the initial state. The Füllbeginndruck P _FB is at most as large as the hot idling pressure P _HL , preferably it is smaller. The pressure storage device 40 thus becomes effective even at low system pressures.

The pressure storage device 40 is further designed so that the filling of the storage chamber 41 is not completed when the pressure in the storage chamber 41 corresponds to the hot idle pressure P _HL , ie at idle speed, but only at a higher inflation pressure. The Pressure accumulator 40 thus operates out of the hot idle, preferably even at a lower speed than the idle speed, up to a lying above the idle speed always with adjusted compensation or accumulator pressure. Preferably, the pressure storage device 40 is tuned so that the storage chamber 41 reaches its maximum fill volume at the earliest at double idle speed, more preferably at least three times idle speed. The maximum filling volume can be absolutely limited as in the embodiment by a stop contact, in principle, however, a stop limit is not required. In alternative embodiments, the pressure storage device 40 can also fill or empty corresponding to the respective system pressure over the entire speed range of the internal combustion engine. However, filling over the entire speed range is not required and not always desirable because the spring device 43 is subject to limitations in terms of its spring rigidity. Such limitations can be counteracted by a series or parallel connection of several spring members, for example, a spring member low spring stiffness and a stiffer spring member, wherein in the lower speed range primarily the softer spring member and at higher speed the stiffer spring member only to a relevant extent or at all first would tension.

The locking device 30 is tuned by appropriate design of the pressure surfaces 31c and 31d of the locking pin 31 and the spring stiffness or a spring bias of the locking spring 32 to the system pressure so that the Entriegelungsemindestdruck P _E also at most as large as the hot idling pressure P _HL , preferably smaller than this , More preferably, the unlocking minimum pressure P _{E is} at most as large as the filling start pressure P _FB , preferably smaller than this. The comparatively low unlocking minimum pressure P _E ensures early unlocking, at low speeds of the internal combustion engine, and thus already an adjustability of the rotor at a correspondingly low speed. Such a sensitive unlocking counteracts when the locking device 30 with the in the Frühstellkanimer 8 ( FIG. 3 ) prevailing pressure is unlocked, the application of both pressure surfaces 31c and 31d at the same time further favoring acts, as a result, the spring force of the locking spring 32 can be selected correspondingly high, resulting in a secure locking engagement result.

It should also be added to the pressures that are decisive for the vote that the hot idling pressure P _HL can be measured, in particular close to the restraint device 51, in particular upstream of it. The filling start pressure P _FB and the minimum filling pressure for a complete filling, if a complete filling is given by abutment contact, can be measured in the same place, assuming of course that the pressure in the storage chamber 41 at the time of measurement is not just greater than the pressure in front of the Rücksperreinrichtung 51. Finally, the minimum unlocking pressure P _E can also be measured there. The locking engagement should be released when the unlocking minimum pressure P _{E is} reached at said point. In the measurement of the pressures to be compared with one another, however, care should be taken that the pressure at the location of the measurement is at least substantially constant, that is to say that pressure fluctuations which are not exactly to be compensated by the pressure storage device 40 take place. The internal combustion engine should therefore be operated during the measurement in a stationary operating state. Unavoidable higher-frequency pressure fluctuations, as they occur by delivery pulsations of the pressure fluid pump and line vibrations in the pressurized fluid system even in steady-state operation, are not meant hereby. These higher-frequency pressure fluctuations result in a respectively representative pressure average for the purposes of comparison and do not appreciably affect the positioning speed of the phaser for practical purposes.

FIG. 7 shows the attachment housing with the attachment housing part 2a and the covers 2b and 2c, which receives the phaser, substantially the stator 3, the rotor 7 and the central control valve from which the valve housing 10 protrudes on the mounting side of the attachment housing 2a, 2b, 2c. The attachment housing, for example the attachment housing part 2a, also includes the same pressure accumulator device 40, so summarizes the phaser and the pressure storage device 40 together to form a mounting unit. This mounting unit is mounted on the engine housing of the internal combustion engine, for example on a cylinder head housing, with the cover removed 2b, which is mounted after mounting on the housing part 2a. The Rücksperreinrichtung 51 is advantageously also in the mounting housing 2a, 2b, 2c arranged.

FIG. 8 shows the attachment housing 2a, 2b, 2c in an end view of the mounting side. On the mounting side, a seal 56 is arranged, which ensures in the assembled state for the seal between the machine housing and the mounting housing 2a, 2b. On the mounting side, centering elements 57 protrude beyond the seal 56, relative to the mounted state, in the direction of the machine housing and, in the assembled state, into adapted centering counter-structures of the machine housing. The centering elements 57 are illustrative pin-shaped and can be hollow in cross section and formed in such embodiments as centering. The centering elements 57 serve not only to center and thereby facilitate assembly, but also keep the seal 56 on the mounting side of the attachment housing 2a, 2b in an immediately suitable for mounting location by the seal 56 with at least one of the centering 57, preferably with several or all centering elements 57, in a holding engagement, for example in a rear grip. In holding engagement, the seal is captively connected to the mounting housing.

FIG. 9 shows such a rear handle representative of preferably one or more others. The illustrated centering element 57 extends through an opening of the seal 56. The centering element 57 is in the attachment housing 2a, 2b inserted, is held firmly in a corresponding receptacle and protrudes as I said about the end face of the attachment housing 2a, 2b a bit far ahead. Close to the end face it is fitted in the protruding section, so that the seal 56 engages with its centering element 57 surrounding the opening edge 58 in the sidecut and so the seal 56 holding the rear handle is formed. The waist can be replaced by another retaining engagement element such as a projection such as a flange. In the embodiment, the functions of centering the attachment housing 2a, 2b and the holder of the seal 56 and the creation of the actual joint connection of mounting housing 2a, 2b and machine housing are concentrated in a confined space by a clamping element 59 of the joint connection, by the hollow centering 57, an example Screw, is guided. In the assembled state, the clamping element 59 extends through the centering element 57 and is connected in its projecting portion with the machine housing, for example in a screw engagement 2f.

FIG. 10 shows the locking device 30 again in longitudinal section. The locking pin 31 is in locking engagement and is retracted with maximum engagement length L ₃₁ in the receptacle 33. Due to the cylindrical or optionally also with a very acute angle of, for example, 2 ° or 3 ° conical circumference of the locking pin 31 acts blocking over its entire maximum engagement length L ₃₁ in Umfangsswirkbereich together with the receptacle 33.

FIG. 11 shows an improved locking device 30 of a first modified embodiment in longitudinal section. This locking device 30 differs from the locking device 30 of FIGS. 1 to 10 only with respect to the locking pin, which is therefore provided with the reference numeral 60. Although the recording is also provided with a different reference numeral, the reference numeral 80, but corresponds to the receptacle 33 of FIGS. 1 to 10 , The locking pin 60 is retracted in the locking direction L, which coincides with a central longitudinal axis of the locking pin 60, in the receptacle 80 with maximum engagement length L ₆₀ and lies in the locking direction L to stop. The stop is exemplified by a projecting at the bottom of the receptacle 80 flat elevation. In contrast to the locking pin 31, however, the locking pin 60 tapers concisely in its engagement region extending over the maximum engagement length L ₆₀ . The lock pin 60 has a front pin portion 61 and a rear pin portion 62 in its engagement portion. The front pin portion extends in the locking direction L to the front free end of the locking pin 60. The rear pin portion 62 is also dipped into the receptacle 80 in locking engagement and overlaps with the opening edge 83 of the receptacle 80. It extends in locking engagement a distance in the direction to the free end of the locking pin 60. As preferred, but by way of example only, the engagement portion of the locking pin 60 is comprised of the two pin portions 61 and 62, which together extend beyond the maximum engagement length L ₆₀ . Of the Front pin section 61 has a length L ₆₁ measured in the locking direction L, and the rear pin section 62 has a length L ₆₂ whose sum corresponds to the maximum L ₆₀ . The receptacle 80 also has an overlapping in locking engagement with the front Pinabschnitt 61 lower receiving portion 81 of the length L ₆₁ and a to the edge 83 of the receiving opening extending upper accommodating portion 82 having a length L ₆₂ corresponding length. In the locking engagement thus overlap the front pin portion 61 with the lower receiving portion 81 and the rear pin portion 62 with the upper receiving portion 82nd

The front pin portion 61 has over its entire length L ₆₁ on the outer circumference on an inclination α to the locking direction L, which is so large that the locking pin 60, should he press in the region of the front pin portion 61 against the opening edge 83, not clamp and a Self-locking of pin 60 and receptacle 80 can not take place, but the locking pin 60 is pressed in the force exerted by the rotor 7 transverse force against the spring force in the direction of the release position. By dipping only with the front pin portion 61, therefore, the rotor 7 can not be blocked relative to the stator 3. In a the relative rotational movement blocking blocking contact can reach only the rear pin portion 62, which may be tapered cylindrical or slightly conical with a very small cone angle of, for example, 3 ° or 4 ° to the free end of the locking pin 60 for this purpose. A blocking contact of the front pin portion 61 is prevented by the large inclination α, which is preferably at least 45 °. The inclination α is preferably at most 80 °. Slopes are particularly favorable by 60 °, namely from the range of 60 ° ± 10 °. The inclination values apply in each case to the entire length L _{61 of} the front pin section 61. The inclination α may be variable, but the inclination α is preferably constant over the length L ₆₁ and the pin section 61 is correspondingly conical on the outer circumference. In the embodiment, the front pin portion 61 is a truncated cone by the front end of the locking pin 60 is formed as a planar end face.

Due to the pronounced tapering of the therefore non-blocking front pin portion 61, the Umsteuerverhalten the phaser from the lockable angular position, for example, the early position in the direction of the other angular position, in the example, the late position easier. If the rotor 7 assumes the early position, the early adjustment chambers 8 are pressurized. The lock pin 60 assumes the release position in this state, assuming sufficient fluid pressure. If the rotor 7 is now to be adjusted in the direction of the retarded position, two movements can take place simultaneously when reversing: because of the pressure reduction in the early adjustment chambers 8 and the pressure build-up in the late adjustment chambers 9, the rotor 7 begins to rotate relative to the stator 3 in the direction of the retarded position , If the early-acting chambers 8 are relieved of pressure, the locking pin 60 starts driven out by the spring force, and there is the possibility that it dips into the receptacle 80. Depending on which of the two Movements is the faster, therefore finds a locking or adjustment of the rotor 7 instead. Although the locking pin 60 may initially dip easily into the receptacle 80 because of the significantly large length L ₆₁ and the large inclination α. However, as long as the locking pin 60 is immersed only with its front pin portion 61, the locking pin 60 can be urged back in the direction of the release position in cooperation of front pin portion 61 and opening edge 83 by the transverse force exerted by the rotor 7 against the locking direction 2. Since the system of locking pin 60 and locking spring 32 is subject to a certain inertia, the time required for the extension by the length L ₆₁ L is sufficient to prevent jamming of locking pin 60 and receptacle 80 safer than conventional locking pins. The pressure at which the rotor 7 can still be reliably adjusted relative to the stator 3 is reduced. It ensures a more reliable reversal in the pressure chamber connected to the control chamber at low pressure. The same advantage arises when starting the internal combustion engine. As a result of the fluid pressure that builds up in the process, the locking pin 60 only has to be pushed back by the length L _{62 of} the rear pin section 62 against the spring force. The risk of tilting due to shear forces is reduced.

Of particular advantage is also the abrupt transition in the border region of the pin sections 61 and 62. If the inclination α is applied over the locking and unlocking direction or axis L, the inclination makes a jump in the boundary region, namely from the inclination 0 ° or Due to the pitch jump, the steeply inclined circumferential effective range and the circumferential effective range of the rearward locking portion cooperating with the upper receiving portion 82 at a corresponding depth of immersion may interfere with a small degree of inclination of the outer periphery of the rear pin portion 62 Pin portion 62 relative to the maximum engagement length L _{60 of} the engagement portion of the locking pin 60 are each carried out in maximum length. This is favorable in terms of preventing unwanted Einriegelns when reversing the rotor and a secure locking in operating phases with not yet filled phaser. The tilt jump takes place advantageously within a very small length of preferably less than 10% and more preferably still less than 5% of the maximum engagement length L ₆₀ or over a correspondingly small radius. However, the production can also be set up so that the inclination jump takes place as abruptly as possible in terms of manufacturing technology. Compared to known locking pins, which have, for example, spherical or paraboloid engagement areas, the relatively sharp geometric separation into the two functionally different pin sections 61 and 62 as explained above enables unlocking when reversing the rotor 7 even at low pressures, but at the same time becomes too by the interaction of the rear pin portion 62 with the upper receiving portion 83 a secure blocking at not yet the pressure fluid filled phaser, in particular in start phases of the internal combustion engine, guaranteed. Because of the reduction of the minimum unlocking pressure required for unlocking, the unlocking can be ensured even in hot idle phases of the internal combustion engine safer than in the known locking devices. The availability of the phaser for camshaft adjusting operations is increased.

Apart from the front pin section 61, the locking pin 60 corresponds to the locking pin 31, so that reference can be made to the relevant embodiments. Merely for the purpose of formal distinction, reference numeral 63 is entered for the first printing surface. The second pressure surface 64 is formed by the inclined peripheral surface of the front pin portion 61, for the pressurization for unlocking apply the statements in connection with the locking pin 31, however, in the same way.

The lengths L ₆₁ and L ₆₂ are preferably each at least 0.5 mm, more preferably at least 1 mm. The ratio of the length L _{61 of} the non-blocking acting pin portion 61 to the length L _{62 of} the blocking acting pin portion 62 is selected in appropriate embodiments in the range of 1 ± 0.5.

FIG. 12 shows a differently modified locking device 30, a second embodiment of the invention, in which a locking pin 70 is used, which the locking pin 31 of FIGS. 1 to 10 equivalent. However, this locking device 30 has a modified receptacle 90. The receptacle 90 comprises a lower receiving portion 91, which is formed as in the receptacles 33 and 80, and an upper receiving portion 92 which extends to the opening edge 93 of the receptacle 90 and widening towards this or from the opening edge 93 to the lower receiving portion 91 continuously tapers over its entire length. The length of the lower receiving portion 91 corresponds to the length L _{71 of} the front pin portion 71, and the length of the upper receiving portion 92 corresponds to the length L _{72 of} the rear pin portion 72, but the pin portions 71 and 72 continue each other continuously without inclination changes. When locking, the front pin portion 71, in particular the front free end of the locking pin 70, and the upper receiving portion 92 cooperate in the same manner as the front pin portion 61 and the upper receiving portion 82 of the first example. The statements there also apply to the second embodiment. Only for the formal distinction of the first embodiment, the inclination of the upper receiving portion 92 is denoted by β, but for the inclination α made statements apply in the same way for the held in the locking direction L taper in the receiving portion 92. The front pin portion 71 acts in this embodiment, however with the lower receiving portion 91 in locking engagement together blocking. The Inclination at the outer periphery of the front pin portion 71 and the inclination at the inner periphery of the lower receiving portion 91 are correspondingly small. The said peripheral surfaces may in particular be cylindrical or conical with a slight inclination.

The tapering of the locking pin or the receptacle according to the invention, in each case in the locking direction L, also has advantages over the functional advantages of the locking device with respect to the development of the phaser until it is ready for series production. If, for example, the locking pin and the receptacle are formed in the early stages of development with continuous cylindrical or slightly conical circumferential effective ranges and the locking spring 32 adapted, even in later development stages, for example in the test phase on the engine test bench or even later, a locking pin conventionally shaped up to that point be replaced by a locking pin according to the invention or a conventionally shaped receptacle by a recording according to the invention. The design of the locking spring 32 and the geometry of locking pin and recording, moreover, nothing must be changed. By virtue of the possibilities opened up according to the invention, an optimum between the unlocking and the locking behavior of the respective camshaft phaser can be realized with little change effort.

FIG. 13 shows a locking device 30 of a third embodiment according to the invention with a modified locking pin 100 and a modified receptacle 110. From the longitudinal section of FIG. 13 is in FIG. 14 the area of the locking engagement is shown enlarged.

The locking pin 100 has a front pin portion 101 and a rear pin portion 102 that form the engagement portion with which the locking pin 100 engages the receptacle 110 in locking engagement. In contrast to the other two embodiments of the invention, the rear pin portion 102 tapers toward the free end of the locking pin 100. As preferred, but only by way of example, the pin portion 102 tapers over its entire length, the in FIG. 14 L ₁₀₂ is tapered, conically everywhere with the same inclination. The cooperating in locking engagement with the pin portion 102 upper receiving portion 112 tapers congruent to the pin portion 102 toward the bottom of the receptacle 110, in the embodiment according to conical with anywhere the inclination of the rear pin portion 102 corresponding inclination. As preferred, but only by way of example, also the lower receiving portion 111 has the same inclination as the upper receiving portion 112 almost to the bottom of the receptacle 110. This inclination is so small that the locking pin 100 is blocked in the locking engagement in the region of the pin portion 102.

The front pin portion 101 has the pronounced strong inclination α, so that the locking pin 100 in the front pin portion 101 is not blocked. In that regard, the comments on the other embodiments apply. However, in the locking pin 100, the front pin portion 101 is shorter in relation to the rear pin portion 102 than in the two previous embodiments. The aspect ratio L ₁₀₂ : L ₁₀₁ , that is, the length of the rear pin portion 102 to the length of the front pin portion 101, is about 5.

The upper receiving portion 112 has, in an upper portion extending to the opening edge 113 and the opening edge 113, over a length L ₁₁₃ , the in FIG. 14 is registered, an inclination which is significantly greater than the inclination in the adjoining lower portion of the upper receiving portion 112. The measured in the direction of movement of the locking pin 100 length L ₁₁₃ is greater than it would be in a pure chamfering of the receptacle 114. The length L ₁₁₃ with the comparatively large, ie, flat, slope is preferably at least one fifth of the total length L _{100 of} the engagement portion of the locking pin 100. As preferred, but by way of example only, the length L _{101 of} the front pin portion 101 and the length L _{113 of} the upper one Part of the upper receiving portion 112 at least substantially equal. If the locking pin 100 protrudes into the receptacle 110 only with its front pin section 101, a comparatively large clearance is thereby obtained in the transverse direction, ie in the direction of the relative rotational movement of the stator 3 and the rotor 7.

Apart from the differences explained, the phase adjuster corresponds to the exemplary embodiments already described above.

The locking pin is formed in the illustrated embodiments as a stepped piston. In likewise preferred, simplified embodiments, the locking pin in all embodiments may instead be designed as a piston with a single-cylindrical guide, so that such a locking pin and a leading him in the locking and unlocking direction rotor 7 only have cylindrical guide circumferential surfaces. Even in such embodiments, the external connection channel 34, which in the illustrated embodiments, the Frühstellkammer 8 and in alternative embodiments, the opposite Spätstellkammer 9 connects directly to the locking device 30, open into a connecting channel 38 corresponding internal connection channel, which separates the pressurized fluid from the corresponding Entriegelungsstellkammer 8 or 9 in the respective receptacle and there against the pressure surface of the locking pin, for example, the locking pin 31, 60, 70 or 100, leads to effect the unlocking. A locking pin with only a single cylindrical guide is in terms of manufacturing and also to avoid over-determination in the guiding engagement of pin and rotor beneficial.

LIST OF REFERENCE NUMBERS

1

camshaft

1a

accommodation space

2

Thrust bearing, machine housing

2a

housing part

2 B

cover

2c

Storage chamber lid

2d

Storage chamber inlet

2e

Speicherkammerauslass

2f

threaded engagement

3

stator

4

drive wheel

4 '

return

5

impeller

5a

wing

6

cover

7

rotor

7a

wing

8th

Early setting chamber

9

Late setting chamber

10

valve housing

11

End closure wall

12

screw

14

spring member

15

actuator

16

Kitchen sink

17

anchor

18

expanded housing section

20

plunger

21

cavity

22

piston inlet

23

piston outlet

24

Compensating feed

25

coupling member

26

deepening

27

deepening

28

Expansion, flared piston section

30

locking device

31

locking pin

31a

guide section

31b

engagement area

31c

first printing surface

31d

second printing surface

32

locking spring

33

admission

33a

opening edge

34

outer connection channel

35

support element

36

guide

37

pressure chamber

38

inner connection channel

39

derivation

39a

passage

40

Pressure storage device

41

storage chamber

42

Wall structure, piston

43

spring means

44

bulkhead

45

peripheral wall

46

discharge channel

50

feed

51

Rear locking device

52

filter element

53

feed

56

poetry

57

centering

58

opening edge

59

clamping means

60

locking pin

61

front pin section

62

rear pin section

63

first printing surface

64

second printing surface

70

locking pin

71

front pin section

72

rear pin section

74

second printing surface

80

admission

81

lower receiving section

82

upper receiving section

83

opening edge

90

admission

91

lower receiving section

92

upper receiving section

93

opening edge

100

locking pin

101

front pin section

102

rear pin section

103

first printing surface

104

second printing surface

110

admission

111

lower receiving section

112

upper receiving section

113

opening edge

A

working port

B

working port

D

direction of rotation

L

Locking and unlocking direction, longitudinal axis of the locking pin

L _i

lengths

P

pressure connection

P _a

axial housing inlet

P _r

radial housing inlet

P _E

Entriegelungsmindestdruck

P _FB

Füllbeginndruck

P _HL

Hot idling pressure

R

Rotary axis, central axis

T _A

reservoir port

T _B

reservoir port

α

Tilt

β

Tilt

Claims (15)

1. A phase setter for adjusting the rotational angular position of a cam shaft relative to a crankshaft of a combustion engine, the phase setter comprising:

   (a) a stator (3) which can be rotary-driven by the crankshaft;

   (b) a rotor (7) which can be rotary-driven by the stator (3) and can be coupled to the cam shaft (1) in order to rotary-drive the cam shaft (1);

   (c) an early setting chamber (8) for generating a torque which acts on the rotor (7) relative to the stator (3) in a leading direction, and a late setting chamber (9) for generating a torque which acts on the rotor (7) relative to the stator (3) in a trailing direction, wherein in order to generate the respective torque, the early setting chamber (8) and the late setting chamber (9) can be charged with a pressure fluid in order to be able to adjust the rotational angular position of the rotor (7) relative to the stator (3);

   (d) a latching pin (60; 70; 100) which is supported on one of the stator (3) and the rotor (7) such that it can be moved back and forth in a latching and unlatching direction (± L) into and out of a latching engagement, and which can be moved out of the latching engagement, against a spring force, by being charged with the pressure fluid;

   (e) and a receptacle (80; 90; 110) which is formed by the other of the stator (3) and the rotor (7) and with which a front pin portion (61; 71; 101) of the latching pin (60; 70; 100) which extends as far as a free end of the latching pin (60; 70; 100) and a rear pin portion (62; 72; 102) of the latching pin (60; 70; 100) which is distanced from the free end engage, in the latching engagement, and thus block the rotor (7) against rotating relative to the stator (3),

   (f) wherein the rear pin portion (62; 72; 102) exhibits a length (L₆₂; L₇₂; L₁₀₂) with which it engages with the receptacle (80; 90; 110) in the latching engagement and which, as measured up to an opening edge (83; 93; 113) of the receptacle (80; 90; 110), is at most three times as large as the length (L₆₁; L₇₁; L₁₀₁) of the front pin portion (61; 71; 101), and wherein the receptacle (80; 90; 110) having a respectively corresponding length comprises a lower receptacle portion (81; 91; 111) which overlaps with the front pin portion (61; 71; 101) in the latching engagement, and an upper receptacle portion (82; 92; 112) which overlaps with the rear pin portion (62; 72; 102) in the latching engagement and comprises the opening edge (83; 93; 113), wherein

   (g) either an outer circumference of the front pin portion (61; 101) exhibits an inclination (α) to the latching and unlatching direction (± L) which is sufficiently large over the entire length (L₆₁; L₁₀₁) of the front pin portion (61; 101) that the rotor (7) cannot be blocked solely by the engagement of the front pin portion (61; 101), and the engagement of the rear pin portion (62; 102) establishes the block,

   (h) or an inner circumference of the upper receptacle portion (92) exhibits an inclination (β) to the latching and unlatching direction (± L) which is sufficiently large over the entire length (L₇₂) of the upper receptacle portion (92) that the rotor (7) cannot be blocked solely by the engagement between the front pin portion (71) and the upper receptacle portion (92), and the engagement between the front pin portion (71) and the lower receptacle portion (91) establishes the block, and wherein the inclination (α; β) is at least 45° and at most 75° over the entire length of either the front pin portion (61; 101) or the upper receptacle portion (92).
2. The phase setter according to Claim 1, characterised in that either the front pin portion (61; 101) tapers towards the free end of the latching pin (60; 100), or the upper receptacle portion (92) tapers towards the lower receptacle portion (91), at least in a circumferential acting region, either conically or in the shape of a truncated cone or concavely as viewed from without.
3. The phase setter according to any one of the preceding claims, characterised in that the front pin portion (61; 101) adjoins the rear pin portion (62; 102), and the lower receptacle portion (91) adjoins the upper receptacle portion (92), and the inclination (α; β) changes abruptly - jumping in the course of the inclination (α; β) as plotted against the latching and unlatching direction (± L) by more than at least 45° - in the respective boundary region if Feature (g) of the pin portions (61, 62; 101, 102) is realised and if Feature (h) of the receptacle portions (91, 92) is realised.
4. The phase setter according to any one of the preceding claims, characterised in that if Feature (g) is realised, the ratio of the length of the front pin portion to the length of the rear pin portion (L₆₁ : L₆₂) is chosen from the range of 0.5 to 1.5, and if Feature (h) is realised, the ratio of the length of the upper receptacle portion to the length of the lower receptacle portion (L₇₂ : L₇₁) is chosen from the range of 0.5 to 1.5.
5. The phase setter according to any one of the preceding claims, characterised in that each of the length (L₆₁) of the front pin portion (61), the length (L₆₂) of the rear pin portion (62), the length (L₇₁) of the lower receptacle portion (91) and the length (L₇₂) of the upper receptacle portion (92) is at least 1 mm.
6. The phase setter according to any one of the preceding claims, characterised in that the rear pin portion (62; 72; 102) is cylindrical or exhibits an inclination of less than 20° over at least a part of its length (L₆₂; L₇₂; L₁₀₂), at least in a circumferential acting region which co-operates with the receptacle (80; 90; 110) in the latching engagement.
7. The phase setter according to any one of the preceding claims, characterised in that

   (i) either the front pin portion (61; 101) exhibits the large inclination (α) in accordance with Feature (g), and the upper receptacle portion (82; 112) is cylindrical or exhibits an inclination of less than 20° over at least a part of its length (L₆₂; L₁₀₂) which overlaps the rear pin portion (62; 102) in the latching engagement, at least in a circumferential acting region which co-operates with the rear pin portion (62; 102) in the latching engagement

   (ii) or the upper receptacle portion (92) exhibits the large inclination (β) in accordance with Feature (h), and the front pin portion (71) is cylindrical or exhibits an inclination of less than 20° over at least a part of its length (L₇₁) which overlaps the lower receptacle portion (91) in the latching engagement, at least in a circumferential acting region which co-operates with the lower receptacle portion (91) in the latching engagement.
8. The phase setter according to any one of the preceding claims, characterised in that the front pin portion (61; 101) is shaped in accordance with Feature (g), at least in a circumferential acting region which co-operates with the receptacle (80) during latching, and the rear pin portion (62; 102) is cylindrical or exhibits an inclination of less than 20°, at least in a circumferential acting region which co-operates with the upper receptacle portion (82; 112) in the latching engagement, up to and adjoining the front pin portion (61; 101).
9. The phase setter according to any one of the preceding claims, characterised in that the front pin portion (61; 101) is shaped in accordance with Feature (g), and is preferably circumferentially conical, over its circumference, and the rear pin portion (62; 102) is cylindrical or conical at an inclination of less than 20°, circumferentially over its circumference, up to and adjoining the front pin portion (61; 101).
10. The phase setter according to any one of the preceding claims, characterised in that a pressure space (37), which accommodates the latching pin (60; 70; 100), or the receptacle (80; 90; 110) is/are connected to the early setting chamber (8) or the late setting chamber (9) in order to release the latching engagement.
11. The phase setter according to any one of the preceding claims, characterised in that the latching pin (60; 70; 100) is supported on one of the rotor (7) and the stator (3) via a latching spring (32) and is guided, such that it can be axially moved back and forth between the latching engagement and the release position, by said one of the rotor (7) and the stator (3).
12. The phase setter according to any one of the preceding claims and one of the following features:

    (i) the latching pin (60; 70; 100) comprises an annular first pressure area (63; 103) which is situated outside the receptacle (80; 90; 110) when the latching engagement is established, and a second pressure area (64; 104) which is situated in the receptacle (80; 90; 110) when the latching engagement is established, each of which can be charged with the pressure fluid in order to release the latching engagement and which are connected to each other such that the pressure fluid for releasing the latching engagement reaches one of the pressure areas, whence it also reaches the other of the pressure areas, or reaches both pressure areas via a bifurcation;

    (ii) the latching pin is guided on a simply cylindrical guide only, and a pressure area (64; 74; 104) which is situated in the receptacle (80; 90; 110) when the latching engagement is established can be charged with the pressure fluid via an internal connecting channel (38), which is formed on or in the latching pin (60; 70; 100) or in a pressure space which accommodates the latching pin (60; 70; 100), and another connecting channel (34) which leads from either the early setting chamber (8) or the late setting chamber (9) into the connecting channel (38).
13. The phase setter according to any one of the preceding claims, characterised in that the rotor (7) mounts the latching pin (60; 70; 100) such that it can be moved in a pressure space (37), and comprises a connecting channel (34) which ports into one of the setting chambers (8, 9), either into the early setting chamber (8) or into the late setting chamber (9), and connects the pressure space (37) to said setting chamber (8; 9) in order to release the latching engagement.
14. The phase setter according to any one of the preceding claims and at least one of the following features:

    (i) the latching pin (60; 70; 100) is arranged in a vane (7a) of the rotor (7), such that it can be moved and eccentrically in the circumferential direction as viewed in an axially facing view of the rotor (7);

    (ii) the latching pin (60; 70; 100) is arranged in a vane (7a) of the rotor (7), such that it can be axially moved and nearer to a radial end of the vane (7a) than to the rotational axis (R) of the rotor (7).
15. The phase setter according to any one of the preceding claims and at least one of the following features:

    (i) the latching pin (100) corresponds to Feature (g), and the rear pin portion (102) tapers at an inclination towards the front pin portion (101), and the upper receptacle portion (112) tapers at an inclination towards the lower receptacle portion (111), wherein the inclination of the rear pin portion and the inclination of the upper receptacle portion are sufficiently small that the rear pin portion (102) is blocked by the upper receptacle portion (112) in the latching engagement;

    (ii) the latching pin (100) corresponds to Feature (g), the upper receptacle portion (112) tapers from the opening edge (113) of the receptacle (110) towards the lower receptacle portion (111) at a first inclination and deeper in the receptacle (110) at a second inclination, and the first inclination is larger than the second inclination, wherein the second inclination is sufficiently small that it blocks the rear pin portion (102) in the latching engagement, and the first inclination is sufficiently large that the rotor (7) cannot be blocked solely by the engagement between the latching pin (100) and the region of the first inclination (α).

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