EP2841723B1 - Valve drive of an internal combustion engine - Google Patents
Valve drive of an internal combustion engine Download PDFInfo
- Publication number
- EP2841723B1 EP2841723B1 EP13723664.2A EP13723664A EP2841723B1 EP 2841723 B1 EP2841723 B1 EP 2841723B1 EP 13723664 A EP13723664 A EP 13723664A EP 2841723 B1 EP2841723 B1 EP 2841723B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cam
- valve
- valve actuating
- actuating cam
- toothing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 238000002485 combustion reaction Methods 0.000 title claims description 21
- 238000006073 displacement reaction Methods 0.000 description 24
- KJFBVJALEQWJBS-XUXIUFHCSA-N maribavir Chemical compound CC(C)NC1=NC2=CC(Cl)=C(Cl)C=C2N1[C@H]1O[C@@H](CO)[C@H](O)[C@@H]1O KJFBVJALEQWJBS-XUXIUFHCSA-N 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 230000001747 exhibiting effect Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/34403—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
Definitions
- the invention relates to a valve train of an internal combustion engine, with at least one base camshaft, on the rotationally fixed and axially displaceable between at least two axial positions at least one cam carrier is provided, wherein at least one valve actuating cam for actuating a gas exchange valve of the internal combustion engine is associated with the cam carrier.
- Valve trains of the type mentioned are known from the prior art. They are used for internal combustion engines, in which the cycle of gas exchange valves of individual cylinders of the internal combustion engine can be influenced to improve the thermodynamic properties.
- the at least one cam carrier which may also be referred to as a cam piece, is arranged rotationally fixed and axially displaceable on the base camshaft.
- the cam carrier is usually associated with a plurality, that is to say at least two, valve actuation cams. Each of these valve actuation cams has an eccentricity, which serves to actuate one of the gas exchange valves of the internal combustion engine at a specific angle of rotation of the basic camshaft.
- valve actuating cam run together with the base camshaft so that the respective gas exchange valve of the internal combustion engine is actuated by the associated valve actuating cam or its eccentricity at least once per revolution of the basic camshaft.
- the valve actuating cam cooperates preferably with a roller rocker arm of the gas exchange valve by coming into abutting contact with this.
- valve actuation cams are provided, which may be assigned to different cam groups.
- the valve actuation cams of a cam group now differ, for example, with regard to the angular position of their eccentricity or the extent of the same in the radial direction (height) and / or in the circumferential direction (length).
- the cam carrier By the axial displacement of the cam carrier it can be brought into at least two axial positions, for example in a first and a second axial position.
- the gas exchange valve is actuated by a first one of the valve actuation cams and in the second axial position by a second one of the valve actuation cams associated with the same cam group.
- the displacement of the cam carrier in particular the opening time, the opening duration and / or the stroke of the gas exchange valve, in particular depending on an operating state of the internal combustion engine, are selected.
- the displacement or displacement of the cam carrier in the axial direction takes place by means of an adjusting device which comprises a cam carrier associated with the cam carrier and a stationarily arranged actuator, which is usually attached to a cylinder head of the internal combustion engine.
- the actuator has, for example, an extendable driver, which can be brought into engagement with a particular helical or spiral slide track of the shift gate.
- the slide track is provided on the shift gate, which is assigned to the cam carrier.
- the shift gate is located on the cam carrier or is at least operatively connected to it for axial displacement.
- the slide track is preferably in the form of a radial groove, which passes through the circumference of the shift gate, so it is formed open-edge in this.
- the shift gate has so far at least one slide track, in which the driver of the actuator for moving the cam carrier can be introduced.
- valve train having the features of claim 1.
- the valve actuating cam is rotatably mounted and by means of an adjusting device, a rotational angular position of the valve actuating cam with respect to the cam carrier is adjustable.
- the phase angle of the valve actuating cam with respect to the base camshaft is therefore variable.
- the phase position of the valve actuating cam can be changed, in particular the time of opening of the gas exchange valve can be shifted in time forward or backward by the corresponding rotational angle position is adjusted by means of the adjusting device.
- the setting of the angular position is preferably carried out continuously or discretely in at least two stages. So there are at least two different angular positions adjustable.
- the setting of the rotational angle position and the axial position can in principle be performed in any order one behind the other or during at least partially overlapping periods. It should be emphasized in the valve drive according to the invention that, during the adjustment, the rotational angle position of the valve actuation cam does not only change with respect to the base camshaft, but also with respect to the cam carrier.
- the valve actuation cam is So rotatably mounted both with respect to the base camshaft and with respect to the cam carrier and rotatable by means of the adjusting device.
- the rotational angular position of the valve actuating cam is independent of the axial position of the cam carrier adjustable. If the valve actuating cam is displaceable together with the cam carrier in the axial direction between the at least two axial positions, it can thus be provided that the desired valve actuating cam is selected for actuating the gas exchange valve by appropriate selection of the axial position and in addition this valve actuating cam is brought into a rotational angular position, in which in the present operating state of the internal combustion engine, a particularly advantageous operation is achieved.
- the axial position and the rotational angle position are preferably adjusted such that the power of the internal combustion engine is increased and / or their consumption or their pollutant emissions are reduced.
- valve actuation cams in particular all valve actuation cams of a cam group
- each of these valve actuating cam has the eccentricity described above, which may be present for the plurality of valve actuation cams each at different angular position and / or with different extension.
- valve actuating cam is rotatably mounted on, in particular on, the cam carrier and / or the base camshaft.
- the valve actuating cam can in principle be arranged arbitrarily with respect to the cam carrier. For example, it sits in the axial direction immediately adjacent to the cam carrier on the base camshaft. Accordingly, the valve actuating cam is mounted on the cam carrier or on the base camshaft. Preferred is the former embodiment, because in this case the valve actuating cam is displaceable or displaceable together with the cam carrier in the axial direction. It can also be provided that the valve actuating cam is present on the cam carrier, thus encompassing it.
- valve actuating cam has, for example, a central recess, which extends from the cam carrier in the axial direction is penetrated.
- the valve actuating cam is therefore mounted on the cam carrier itself via a bearing, which is designed for example as a plain bearing or roller bearings.
- the valve actuating cam may of course also be present in the axial direction at a distance from the cam carrier. In this case, he is usually not together with this shiftable by means of the adjusting device.
- the adjusting device has an axially displaceable, a switching toothed exhibiting switching element, wherein the switching toothing with a valve actuating cam associated cam teeth is engaged, and both the gear teeth and the cam teeth are designed as helical teeth.
- the setting of the rotational angle position of the valve actuating cam thus takes place with the aid of the switching element, which is axially displaceable relative to the basic camshaft and / or the cam carrier. It is particularly preferably rotatably mounted with respect to the base camshaft, so it rotates with this.
- the switching element has the switching toothing, which is in engagement with the cam teeth.
- the cam teeth are associated with the valve actuating cam, so may be formed in a preferred embodiment of the valve actuating cam.
- the cam teeth can also be present on a further element, which is preferably rigidly connected to the valve actuating cam, so that a rotational movement of the further element can be transmitted to the valve actuating cam.
- the teeth are each designed as helical teeth or as a thread. Accordingly, the axial displacement of the switching element causes a rotational movement of the cam teeth and corresponding to the valve actuating cam.
- the teeth are designed such that, although by changing the axial position, a change in the angular position can be made.
- a force acting on the valve actuating cam in the circumferential direction should not lead to a rotational movement of the valve actuating cam and thus to a change in the axial position.
- the teeth are preferably carried out so self-locking.
- the adjusting device has at least one relative to the base camshaft axially displaceable and / or rotatable adjusting shaft, which is operatively connected to the valve actuating cam.
- the adjusting shaft can in principle be arranged arbitrarily.
- the adjusting shaft is axially displaceable or rotatable relative to the basic camshaft.
- the adjusting shaft for example, for the actuation or axial displacement of the switching element described above with this operatively connected.
- the operative connection of the adjusting shaft with the valve actuating cam is thus provided only indirectly via this switching element.
- the adjusting shaft is rotatable with respect to the base camshaft, it is preferably provided that it normally rotates with it and is rotated only to change the rotational angular position of the valve actuating cam relative to the base camshaft.
- a further development of the invention provides that the adjusting shaft is operatively connected to the valve actuating cam via an adjusting mechanism. This is the case, in particular, when the setting of the rotational angle position of the valve actuating cam is to take place with the aid of the adjusting shaft that is rotatable relative to the basic camshaft.
- the adjusting mechanism is provided in such a manner in the operative connection between the adjusting shaft and the valve actuating cam, that a rotation of the adjusting shaft leads to a change in the rotational angular position of the valve actuating cam.
- the adjusting mechanism can be designed such that the adjusting shaft and the valve actuating cam each have a toothing, wherein these teeth are directly in engagement with each other. Accordingly, there is a direct operative connection between the adjusting shaft and the valve actuating cam.
- the adjusting mechanism has at least one toothed wheel which is present in the operative connection between the adjusting shaft and the valve actuating cam. Accordingly, the operative connection between the adjusting and the valve actuating cam is carried out only indirectly, namely on the at least one gear. It is provided, for example, that the adjusting shaft has a toothing which is in engagement with a toothing of the gear. The latter in turn is in engagement with a toothing of the valve actuating cam.
- the axes of rotation of the adjusting shaft, gear and valve actuating cam are arranged parallel to each other. Of course, however, an angular offset may alternatively be provided, the serrations are designed accordingly in this case.
- a plurality of gears may be provided, which are arranged distributed uniformly over the circumference of the adjusting. Particularly preferably, three or four gears are provided.
- a further development of the invention provides that a shaft toothing of the adjusting shaft or the toothed wheel is in engagement with the cam toothing of the valve actuating cam.
- a shaft toothing of the adjusting shaft or the toothed wheel is in engagement with the cam toothing of the valve actuating cam.
- the adjusting shaft has the shaft toothing
- the valve actuating cam has the cam toothing.
- the teeth of the gear is now engaged with both. Accordingly, a torque between the adjusting and the valve actuating cam for adjusting the angular position can be transmitted via the gear.
- the adjusting shaft is received in the basic camshaft and / or arranged coaxially with the base camshaft.
- the adjusting shaft can be arranged arbitrarily with respect to the basic camshaft.
- the base camshaft is particularly preferably designed as a hollow shaft, wherein the adjusting shaft is arranged in the cavity present in the base camshaft. This allows a particularly space-saving design of the valve train.
- the adjusting shaft is coaxial with the base camshaft.
- the active compound is preferably produced via the gear described above in the manner of a planetary gear.
- the adjusting shaft has an axis of rotation which does not coincide with the axis of rotation of the base camshaft, but rather spaced, but parallel to this.
- the recording of the adjusting shaft in the basic camshaft can be provided completely or only partially. In the latter case, at least one region of the adjusting shaft projects beyond the circumference of the basic camshaft.
- a further development of the invention provides that the adjusting shaft is operatively connected to the valve actuating cam via a holding element that passes through the basic camshaft.
- This holding element can be present for example as a sliding block or the like.
- About the retaining element of the valve actuating cam is rotatably connected to the adjusting shaft. Accordingly, a rotation of the adjusting shaft directly causes a change in the rotational angle position of the valve actuating cam.
- the retaining element preferably passes through the base camshaft in the radial direction. This means that the adjusting shaft is at least partially received in the basic camshaft, while the valve actuating cam is present in the radial direction outside of the basic camshaft.
- the holding element may allow an axial displacement of the adjusting shaft and the valve actuating cam to each other, so that a displacement of the valve actuating cam together with the cam carrier is additionally possible.
- a further development of the invention provides that the setting of the angular position and the axial position takes place by means of a single actuator. It may in principle be provided that there are a plurality of separate actuators, at least one being used for the axial displacement of the cam carrier and at least one other for setting the rotational angle position. It is more advantageous, however, to use only a single actuator and / or a single shift gate for adjusting the rotational angular position and the axial position of the valve train. In each of the aforementioned embodiments, each actuator and / or each shift gate may serve to set at least two different angular positions and / or at least two axial positions.
- the rotational angle position and / or the axial position can be locked.
- the cam carrier is connected to the switching element and / or the adjusting shaft.
- the locking of the angular position and / or the axial position is realized, for example, by latching, so that for a change of rotational position and / or axial position, a force is applied, which exceeds a respective adjusting force.
- the adjusting force for the adjustment of the rotational angle position of the adjusting force for adjusting the axial position selected differently, so when applying a first, for example smaller force, only one size, upon application of a second, for example, greater force, only the other size will be changed.
- the locking can also switchable, so targeted, done. By loosening or making the lock can thus be influenced whether the rotational position or the axial position using the single actuator should be adjustable.
- the axial position is locked switchable, while the rotational angle position is not locked switchable. The setting of the angular position and the axial position is thus controlled when using the single actuator on the locking.
- the FIG. 1 shows a partially cut portion of a valve train 1 of an internal combustion engine, not shown.
- the valve drive 1 consists of a base camshaft 2 and an axially displaceable on this cam carrier 3, which is only hinted at here.
- the axial direction is to be understood as meaning a direction which lies parallel to a longitudinal axis 4 or axis of rotation of the basic camshaft 2.
- the cam carrier 3 has a central recess, which is penetrated by the base camshaft 2. In the region of the recess, the cam carrier 3 has, for example, an internal toothing which cooperates with external toothing of the base camshaft 2 (not visible here) in order to hold the cam carrier 3 in a rotationally fixed but axially displaceable manner on the base camshaft 2.
- the cam carrier 3 has a plurality of valve actuation cams 5 and 6, which are assigned to a cam group 7.
- the cam carrier 3 may have at least one further cam group (not shown) with further valve actuation cams.
- the cam carrier 3 has a shift gate 8.
- the cam carrier 3 can be displaced on the base camshaft 2 in the axial direction by means of an axial adjusting device.
- the Axialstell listening includes, for example, the shift gate 8. Alternatively or additionally, the AxialstellISS nerve have a further (not shown here) switching gate.
- the valve actuation cams 5 and 6 serve to actuate gas exchange valves, not shown, of the internal combustion engine.
- the valve actuating cams 5 and 6 are eccentric, wherein the eccentricities are present in different angular positions or circumferential positions with respect to the cam carrier 3 and / or have different extensions in the radial direction and / or circumferential directions can.
- the valve actuation cam 5 and 6 interact, for example, with roller cam followers of the respective gas exchange valve by contact contact contact.
- Each of the roller rocker arms are assigned the respective valve actuation cams 5 and 6 of the corresponding cam group 7. A first of the roller rocker arms is thus actuated by one of the valve actuation cams 5 and 6 of the cam group 7 and another of the roller rocker arms by one of the valve actuation cams of a further cam group.
- valve actuation cams 5 and 6 of the cam group 7 Due to the different configurations of the valve actuation cams 5 and 6 of the cam group 7 with each other thus a corresponding stroke, opening time and / or an opening duration of the gas exchange valve thus arises.
- the roller rocker arms of the valve actuating cam 5 or 6 of the respective cam group 7 can be actuated.
- the cam carrier 3 is displaced, for example, as a function of an operating state of the internal combustion engine, so that always that valve actuating cam 5 or 6 interacts with the corresponding roller cam lever for its actuation, with which, for example, an optimum efficiency or optimal performance of the internal combustion engine can be achieved.
- the displacement of the cam carrier 3 is effected by means of an actuator, not shown here, which is also part of the AxialstellISS and has a displaceable in the radial direction driver.
- the driver is displaced in the radial direction such that it engages, for example, in a slide track 9 of the shift gate 8 or in a slide track of the further shift gate.
- the slide track 9 is configured such that the switching gate 8 is urged in an insertion of the driver, while the cam carrier 3 is in a first axial position, in the direction of a second axial position and vice versa.
- a displacement of the cam carrier 3 between more than two axial positions is possible and realized by means of a correspondingly adapted shift gate 8 or AxialstellISS.
- a rotational angular position of the valve actuation cams 5 and 6 with respect to the cam carrier 3 should now additionally be adjustable.
- an adjusting device 10 is provided.
- the valve actuating cams 5 and 6 are rotatably supported. This rotatable mounting is provided in the embodiment shown here on the cam carrier 3.
- the adjusting device 10 has an axial displaceable switching element 11. This surrounds the base camshaft 2 and is therefore mounted axially displaceable on this.
- the switching element 11 is in turn partially surrounded by the valve actuating cam 5 and 6, which are made in one piece and of the same material in the embodiment shown here.
- the switching element 11 has a switching toothing 12, which is present as external toothing, while the valve actuating cam 5 and 6 have a cam toothing 13, which is present as internal toothing.
- the shift teeth 12 and the cam teeth 13 are designed as helical gears and are engaged with each other. This means that a rotational movement of the valve actuating cam 5 and 6 is achieved by a displacement of the switching element 11 in the axial direction.
- the rotational angular position of the valve actuating cam 5 and 6 can be set or selected.
- the switching element 11 is operatively connected to the shift gate 8. Using the shift gate 8 so the switching element 11 can be displaced in the axial direction, so that the rotational movement of the valve actuating cam 5 and 6 is achieved.
- FIG. 2 shows the valve train 1 in a second embodiment.
- the valve train 1 has an adjusting shaft 14 which is rotatable relative to the basic camshaft 2.
- the adjusting shaft 14 is arranged in the base camshaft 2 designed as a hollow shaft, wherein the base camshaft 2 and the adjusting shaft 14 are coaxial, ie have the same axis of rotation 4.
- the adjusting shaft 14 has a shaft toothing 15, which is present as an external toothing.
- valve actuation cams 5 and 6 again have the cam teeth 13 for producing the operative connection, which, however, is present here as a degree toothing.
- an adjusting mechanism 16 which has at least one gear 17 in the present embodiment.
- a plurality of gears 17 are provided, which are present in the radial direction between the adjusting shaft 14 and the valve actuating cam 5 and 6.
- the gear 17 and its toothing is engaged both with the shaft teeth 15 and the cam teeth 13.
- FIG. 3 shows a further embodiment of the valve train 1.
- several Verstellwellen 14 for example, two, three or four, are provided.
- the adjusting shafts 14 have axes of rotation which are different from, but parallel to, the axis of rotation 4.
- the adjusting shafts 4 are arranged symmetrically with respect to the axis of rotation 4, in particular distributed uniformly over the circumference of the basic camshaft 2.
- FIG. 4 shows the valve train 1 in a fourth embodiment.
- a single adjusting shaft 14 is provided, which is arranged such that its shaft teeth 15 can engage with the cam teeth 13.
- the valve train 1 shown is analogous to that of the FIG. 3 described executed.
- the adjusting shaft 14 is also received in the base camshaft 2 and rotatably supported in this.
- a recess 18 in the base camshaft 2 which in turn is present as a hollow shaft, the operative connection between the adjusting shaft 14 and the valve actuating cam 5 and 6 is made, for example via a holding element 19, which is present here as a sliding block.
- the retaining element 19 engages in some areas in a circumferential shape of the retaining element 19 form-fitting recess of the valve actuating cam 5 and 6 and is rotatably, but preferably axially displaceable, held on the adjusting shaft 14.
- valve train 1 From the FIG. 6 is a sixth embodiment of the valve train 1 can be seen.
- the valve actuation cams 5 and 6 are not located on the cam carrier 3, but next to it. They are either mounted on the cam carrier 3 or directly to the base camshaft 2. It can therefore be provided that by means of the cam carrier 3 only further valve actuating cam 20 and 21 a further cam group 22 are displaceable in the axial direction.
- the valve actuating cam 5 and 6 of the cam group 7 are not displaced together with the cam carrier 3. Rather, only their angular position with respect to the base camshaft 2 and the cam carrier 3 is adjustable. For this purpose is analogous to the basis of FIG.
- the recess 18 by cross-holding element is provided, via which the operative connection between the adjusting shaft 14 and the valve actuating cam 5 and 6 is made.
- a bearing of the valve actuating cam 5 and 6 may be provided on the cam carrier 3, so that both the axial displacement and the setting of the angular position for the valve actuating cam 5 and 6 can be made here.
- FIG. 7 shows a seventh embodiment of the valve train 1.
- the valve actuating cam 20 and 21 of the cam group 22 are provided.
- the basic camshaft 2 is not shown.
- the cam carrier 3 is mounted by means of a bearing 23, for example in a cylinder head housing.
- the bearing 23 holds the cam carrier 3 in the radial direction, but allows for an axial displacement along the longitudinal axis 4.
- the shift gate 8 is now formed as the only shift gate of the Nöckenarris 3. This means that by means of the shift gate 8 both the cam carrier 3 to be displaced in the axial direction, as well as the switching element 11 to be actuated.
- the cam carrier 3 is assigned a first locking device 24 and the switching element 11 has a second locking device 25.
- the first locking device 24 consists of a latching element 26, for example a ball, which is held stationary in the axial direction.
- the latching element 26 engages in one of a plurality of latching recesses 27, which are arranged on the cam carrier 3.
- the locking element 26 is in the radial direction inwardly, ie on the longitudinal axis 4, urged. Accordingly, a certain first adjusting force is necessary for displacing the cam carrier 3 in the axial direction in order to push the latching element 26 out of the instantaneous latching recess.
- the second locking device 25 is constructed, for example, analogous to the first locking device 24 and consists of a locking element 28 and a plurality of locking recesses 29.
- the locking element 28 is attached to the cam carrier 3, the locking recesses 29 on the shift gate 8, for example.
- the locking element 28 is urged in the embodiment shown here in the radial direction to the outside, so that it engages in one of the locking recesses 29. therefore can the shift gate 8 are displaced by applying a second adjusting force in the axial direction with respect to the cam carrier 3.
- the shift gate 8 is operatively connected to the switching element 11, so that such an axial displacement also causes an axial displacement of the switching element 11 and in consequence a change in the rotational angular position of the valve actuating cam 5 and 6.
- first adjusting the angular position or adjusting the axial position of the cam carrier 3 takes place. Only when reaching an end position by the element, which has the smaller adjusting force, thus, the element is set, which has the greater adjusting force.
- the locking means 24 and 25, preferably both be designed switchable.
- the latching element 26 or the latching element 28 can be specifically displaced out of the respective latching recess 27 or 29, so that the respective adjusting force can be selected.
- the latching element 26 can be displaced out of the latching recess 27 in order to effect only a displacement of the cam carrier 3 during the next actuation of the shift gate 8, but no displacement of the switching element 11.
- the latching element 26 may be urged in the direction of the latching recess 27 such that no displacement of the cam carrier 3 can take place in such an actuation of the shift gate 8, so that instead the switching element 11 is moved and thus the desired rotational angular position of the valve actuating cam 5 and 6 is set.
- the FIG. 8 shows an eighth embodiment of the valve train 1.
- the valve actuation cams 5 and 6 or 20 and 21 of the cam groups 7 and 22 respectively immediately adjacent to the shift gate 8 are arranged.
- a further shift gate 30 is provided, which is assigned to the Axialstell thanks.
- the shift gate 30 serves to adjust the rotational angle position of both the valve actuating cam 5 and 6 of the cam group 7 and the valve actuating cam 20 and 21 of the cam group 22.
- the shift gate 8 is mounted in the axial direction displaceable on the cam carrier 3 and has two switching elements eleventh one of which is associated with the valve actuation cams 5 and 6 and another with the valve actuation cams 20 and 21.
- the cam carrier 3 is supported for example by means of bearings 23.
- the cam carrier 3 may be associated with one or more cylinders of the internal combustion engine and serve to actuate the respective valve actuation cams.
- it may have further valve actuation cams 31, 32, 33 and 34 associated with cam groups 35 and 36.
- These valve actuating cams 31 to 34 are fixedly attached to the cam carrier 3. They can therefore be displaced together with this in the axial direction, but are not adjustable by means of the shift gate 8 in terms of their angular position.
- the respective switching teeth 12 and cam teeth 13 of the valve actuating cam 5 and 6 or 20 and 21 may be designed such that a shift of the shift gate 8 with respect to the cam carrier 3 in the axial direction, a change in the rotational angular position of the respective valve actuating cam 5 and 6 or 20 and 21 in the same or opposite direction causes.
- a plurality of cam groups 7 and 22 assigned to the cam carrier 3 can thus be brought into a specific rotational angle position.
- the other shift gate 30 serves for the axial displacement of the entire cam carrier 3 together with all the valve actuation cams 5, 6, 20, 21 and 31 to 34.
- any number of valve actuation cams and / or cam groups can be present.
- the shift gate 8 or 30 can be configured as desired.
- they are designed to interact with a multi-pin actuator, in particular a two-pin actuator or a three-pin actuator.
- a multi-pin actuator in particular a two-pin actuator or a three-pin actuator.
- These have, in contrast to the embodiment presented here more than one driver, namely two or three, in the form of pins.
- All embodiments have in common that the angular position is always independent of the axial position adjustable. In this way, for example, an adaptation of the cylinder charge and / or the charge movement state (which are operating parameters of the rotational angular position) in at least two, but preferably more than two, different operating conditions of the internal combustion engine, in which different axial positions are possible.
- the setting of the axial position and the angular position can of course be done in any order or simultaneously.
- the basic camshaft can be operatively connected to the crankshaft via a phase adjuster, by means of which an angular position of the basic camshaft with
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- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Description
Die Erfindung betrifft einen Ventiltrieb einer Brennkraftmaschine, mit mindestens einer Grundnockenwelle, auf der drehfest und zwischen wenigstens zwei Axialpositionen axial verschiebbar mindestens ein Nockenträger vorgesehen ist, wobei zumindest ein Ventilbetätigungsnocken zur Betätigung eines Gaswechselventils der Brennkraftmaschine dem Nockenträger zugeordnet ist.The invention relates to a valve train of an internal combustion engine, with at least one base camshaft, on the rotationally fixed and axially displaceable between at least two axial positions at least one cam carrier is provided, wherein at least one valve actuating cam for actuating a gas exchange valve of the internal combustion engine is associated with the cam carrier.
Ventiltriebe der eingangs genannten Art sind aus dem Stand der Technik bekannt. Sie werden für Brennkraftmaschinen eingesetzt, bei welchen das Arbeitsspiel von Gaswechselventilen einzelner Zylinder der Brennkraftmaschine zur Verbesserung der thermodynamischen Eigenschaften beeinflusst werden kann. Der mindestens eine Nockenträger, welcher auch als Nockenstück bezeichnet werden kann, ist drehfest und axial verschiebbar auf der Grundnockenwelle angeordnet. Dem Nockenträger sind üblicherweise mehrere, also zumindest zwei, Ventilbetätigungsnocken zugeordnet. Jeder dieser Ventilbetätigungsnocken weist eine Exzentrizität auf, welche der Betätigung eines der Gaswechselventile der Brennkraftmaschine bei einem bestimmten Drehwinkel der Grundnockenwelle dient. Die Ventilbetätigungsnocken laufen demnach gemeinsam mit der Grundnockenwelle um, sodass das jeweilige Gaswechselventil der Brennkraftmaschine zumindest einmal pro Umdrehung der Grundnockenwelle von dem zugeordneten Ventilbetätigungsnocken beziehungsweise dessen Exzentrizität betätigt wird. Der Ventilbetätigungsnocken wirkt dazu vorzugsweise mit einem Rollenschlepphebel des Gaswechselventils zusammen, indem er mit diesem in Anlagekontakt tritt.Valve trains of the type mentioned are known from the prior art. They are used for internal combustion engines, in which the cycle of gas exchange valves of individual cylinders of the internal combustion engine can be influenced to improve the thermodynamic properties. The at least one cam carrier, which may also be referred to as a cam piece, is arranged rotationally fixed and axially displaceable on the base camshaft. The cam carrier is usually associated with a plurality, that is to say at least two, valve actuation cams. Each of these valve actuation cams has an eccentricity, which serves to actuate one of the gas exchange valves of the internal combustion engine at a specific angle of rotation of the basic camshaft. Accordingly, the valve actuating cam run together with the base camshaft so that the respective gas exchange valve of the internal combustion engine is actuated by the associated valve actuating cam or its eccentricity at least once per revolution of the basic camshaft. The valve actuating cam cooperates preferably with a roller rocker arm of the gas exchange valve by coming into abutting contact with this.
Vorzugsweise sind mehrere Ventilbetätigungsnocken vorgesehen, welche unterschiedlichen Nockengruppen zugeordnet sein können. Die Ventilbetätigungsnocken einer Nockengruppe unterscheiden sich nun beispielsweise hinsichtlich der Winkellage ihrer Exzentrizität oder der Erstreckung derselben in radialer Richtung (Höhe) und/oder in Umfangsrichtung (Länge). Durch das axiale Verschieben des Nockenträgers kann dieser in wenigstens zwei Axialpositionen, beispielsweise in eine erste und eine zweite Axialposition, gebracht werden. In der ersten Axialposition wird das Gaswechselventil von einem ersten der Ventilbetätigungsnocken und in der zweiten Axialposition von einem zweiten der Ventilbetätigungsnocken betätigt, welche derselben Nockengruppe zugeordnet sind. Durch die Verlagerung des Nockenträgers können somit insbesondere der Öffnungszeitpunkt, die Öffnungsdauer und/oder der Hub des Gaswechselventils, insbesondere in Abhängigkeit von einem Betriebszustand der Brennkraftmaschine, ausgewählt werden.Preferably, a plurality of valve actuation cams are provided, which may be assigned to different cam groups. The valve actuation cams of a cam group now differ, for example, with regard to the angular position of their eccentricity or the extent of the same in the radial direction (height) and / or in the circumferential direction (length). By the axial displacement of the cam carrier it can be brought into at least two axial positions, for example in a first and a second axial position. In the first axial position, the gas exchange valve is actuated by a first one of the valve actuation cams and in the second axial position by a second one of the valve actuation cams associated with the same cam group. As a result of the displacement of the cam carrier, in particular the opening time, the opening duration and / or the stroke of the gas exchange valve, in particular depending on an operating state of the internal combustion engine, are selected.
Das Verschieben beziehungsweise Verlagern des Nockenträgers in axialer Richtung erfolgt mithilfe einer Stelleinrichtung, die eine dem Nockenträger zugeordnete Schaltkulisse und einen ortsfest angeordneten Aktuator, der üblicherweise an einem Zylinderkopf der Brennkraftmaschine befestigt ist, umfasst. Der Aktuator verfügt beispielsweise über einen ausfahrbaren Mitnehmer, der sich mit einer insbesondere schrauben- oder spiralförmigen Kulissenbahn der Schaltkulisse in Eingriff bringen lässt. Die Kulissenbahn ist an der Schaltkulisse vorgesehen, welche dem Nockenträger zugeordnet ist. Zum Beispiel liegt die Schaltkulisse an dem Nockenträger vor oder ist zumindest mit diesem zum axialen Verschieben wirkverbunden. Die Kulissenbahn liegt vorzugsweise als Radialnut vor, welche den Umfang der Schaltkulisse durchgreift, also randoffen in dieser ausgebildet ist. Die Schaltkulisse weist insoweit wenigstens eine Kulissenbahn auf, in welche der Mitnehmer des Aktuators zum Verschieben des Nockenträgers einbringbar ist.The displacement or displacement of the cam carrier in the axial direction takes place by means of an adjusting device which comprises a cam carrier associated with the cam carrier and a stationarily arranged actuator, which is usually attached to a cylinder head of the internal combustion engine. The actuator has, for example, an extendable driver, which can be brought into engagement with a particular helical or spiral slide track of the shift gate. The slide track is provided on the shift gate, which is assigned to the cam carrier. For example, the shift gate is located on the cam carrier or is at least operatively connected to it for axial displacement. The slide track is preferably in the form of a radial groove, which passes through the circumference of the shift gate, so it is formed open-edge in this. The shift gate has so far at least one slide track, in which the driver of the actuator for moving the cam carrier can be introduced.
Es ist nun Aufgabe der Erfindung, einen Ventiltrieb einer Brennkraftmaschine vorzuschlagen, welcher weitergehende Einstellmöglichkeiten für das Betätigen des Gaswechselventils, insbesondere den Öffnungszeitpunkt betreffend, ermöglicht.It is an object of the invention to provide a valve train of an internal combustion engine, which further adjustment options for the actuation of the gas exchange valve, in particular the opening time point allows.
Dies wird erfindungsgemäß mit einem Ventiltrieb mit den Merkmalen des Anspruchs 1 erreicht. Dabei ist vorgesehen, dass der Ventilbetätigungsnocken drehbar gelagert ist und mittels einer Stelleinrichtung eine Drehwinkelstellung des Ventilbetätigungsnocken bezüglich des Nockenträgers einstellbar ist. Die Phasenlage des Ventilbetätigungsnockens bezüglich der Grundnockenwelle ist mithin variabel. Auf diese Weise kann die Phasenlage des Ventilbetätigungsnockens verändert, insbesondere der Öffnungszeitpunkt des Gaswechselventils zeitlich gesehen nach vorne oder nach hinten verlagert werden, indem die entsprechende Drehwinkelstellung mithilfe der Stelleinrichtung eingestellt wird. Das Einstellen der Drehwinkelstellung erfolgt bevorzugt kontinuierlich oder diskret in wenigstens zwei Stufen. Es sind also zumindest zwei voneinander verschiedene Drehwinkelstellungen einstellbar. Das Einstellen der Drehwinkelstellung und der Axialposition kann grundsätzlich in beliebiger Reihenfolge hintereinander oder während zumindest teilweise überlappenden Zeiträumen durchgeführt werden. Herauszustellen ist bei dem erfindungsgemäßen Ventiltrieb, dass sich bei dem Verstellen die Drehwinkelstellung des Ventilbetätigungsnockens nicht lediglich gegenüber der Grundnockenwelle verändert, sondern auch bezüglich des Nockenträgers. Der Ventilbetätigungsnocken ist also sowohl bezüglich der Grundnockenwelle als auch bezüglich des Nockenträgers drehbar gelagert und mittels der Stelleinrichtung drehbar.This is achieved according to the invention with a valve train having the features of
Bevorzugt ist entsprechend die Drehwinkelstellung des Ventilbetätigungsnockens unabhängig von der Axialposition des Nockenträgers einstellbar. Wenn der Ventilbetätigungsnocken gemeinsam mit dem Nockenträger in axialer Richtung zwischen den wenigstens zwei Axialpositionen verlagerbar ist, kann es also vorgesehen sein, dass durch entsprechende Auswahl der Axialposition der gewünschte Ventilbetätigungsnocken zur Betätigung des Gaswechselventils ausgewählt wird und zusätzlich dieser Ventilbetätigungsnocken in eine Drehwinkelstellung gebracht wird, in welcher in dem vorliegenden Betriebszustand der Brennkraftmaschine ein besonders vorteilhafter Betrieb erzielt wird. Die Axialposition und die Drehwinkelstellung werden bevorzugt derart eingestellt, dass die Leistung der Brennkraftmaschine erhöht und/oder ihr Verbrauch beziehungsweise ihr Schadstoffausstoß reduziert wird.Preferably, according to the rotational angular position of the valve actuating cam is independent of the axial position of the cam carrier adjustable. If the valve actuating cam is displaceable together with the cam carrier in the axial direction between the at least two axial positions, it can thus be provided that the desired valve actuating cam is selected for actuating the gas exchange valve by appropriate selection of the axial position and in addition this valve actuating cam is brought into a rotational angular position, in which in the present operating state of the internal combustion engine, a particularly advantageous operation is achieved. The axial position and the rotational angle position are preferably adjusted such that the power of the internal combustion engine is increased and / or their consumption or their pollutant emissions are reduced.
Besonders vorteilhaft ist es, wenn mehrere, also wenigstens zwei, Ventilbetätigungsnocken, insbesondere alle Ventilbetätigungsnocken einer Nockengruppe, gemeinsam mittels der Stelleinrichtung in die gewünschte Drehwinkelstellung gebracht werden können. Jeder dieser Ventilbetätigungsnocken weist dabei die eingangs beschriebene Exzentrizität auf, wobei diese für die mehreren Ventilbetätigungsnocken jeweils an unterschiedlicher Winkellage und/oder mit unterschiedlicher Erstreckung vorliegen können. Anders ausgedrückt kann auch vorgesehen sein, dass lediglich ein einziger Ventilbetätigungsnocken verlagerbar ist, welcher jedoch mehrere Nockenbahnen aufweist, wobei jede Nockenbahn mit einer Exzentrizität gemäß den vorstehenden Ausführungen versehen ist.It is particularly advantageous if several, ie at least two, valve actuation cams, in particular all valve actuation cams of a cam group, can be brought together into the desired rotational angle position by means of the actuation device. Each of these valve actuating cam in this case has the eccentricity described above, which may be present for the plurality of valve actuation cams each at different angular position and / or with different extension. In other words, it can also be provided that only a single valve actuating cam is displaceable, which, however, has a plurality of cam tracks, wherein each cam track is provided with an eccentricity according to the above statements.
Eine Weiterbildung der Erfindung sieht vor, dass der Ventilbetätigungsnocken drehbar an, insbesondere auf, dem Nockenträger und/oder der Grundnockenwelle gelagert ist. Der Ventilbetätigungsnocken kann bezüglich des Nockenträgers prinzipiell beliebig angeordnet sein. Beispielsweise sitzt er in axialer Richtung unmittelbar benachbart zu dem Nockenträger auf der Grundnockenwelle. Entsprechend ist der Ventilbetätigungsnocken an dem Nockenträger oder auf der Grundnockenwelle gelagert. Bevorzugt ist erstere Ausführungsform, weil in diesem Fall der Ventilbetätigungsnocken gemeinsam mit dem Nockenträger in axialer Richtung verlagerbar beziehungsweise verschiebbar ist. Es kann dabei auch vorgesehen sein, dass der Ventilbetätigungsnocken auf dem Nockenträger vorliegt, diesen also umgreift. Zu diesem Zweck weist der Ventilbetätigungsnocken eine beispielsweise zentrale Ausnehmung auf, welche von dem Nockenträger in axialer Richtung durchgriffen ist. Der Ventilbetätigungsnocken ist mithin über ein Lager, welches beispielsweise als Gleitlager oder Wälzlager ausgeführt ist, auf dem Nockenträger selbst gelagert. Alternativ kann der Ventilbetätigungsnocken selbstredend auch in axialer Richtung beabstandet von dem Nockenträger vorliegen. In diesem Fall ist er üblicherweise nicht gemeinsam mit diesem mithilfe der Stelleinrichtung verlagerbar.A development of the invention provides that the valve actuating cam is rotatably mounted on, in particular on, the cam carrier and / or the base camshaft. The valve actuating cam can in principle be arranged arbitrarily with respect to the cam carrier. For example, it sits in the axial direction immediately adjacent to the cam carrier on the base camshaft. Accordingly, the valve actuating cam is mounted on the cam carrier or on the base camshaft. Preferred is the former embodiment, because in this case the valve actuating cam is displaceable or displaceable together with the cam carrier in the axial direction. It can also be provided that the valve actuating cam is present on the cam carrier, thus encompassing it. For this purpose, the valve actuating cam has, for example, a central recess, which extends from the cam carrier in the axial direction is penetrated. The valve actuating cam is therefore mounted on the cam carrier itself via a bearing, which is designed for example as a plain bearing or roller bearings. Alternatively, the valve actuating cam may of course also be present in the axial direction at a distance from the cam carrier. In this case, he is usually not together with this shiftable by means of the adjusting device.
Eine Weiterbildung der Erfindung sieht vor, dass die Stelleinrichtung über ein axial verlagerbares, eine Schaltverzahnung aufweisendes Schaltelement verfügt, wobei die Schaltverzahnung mit einer dem Ventilbetätigungsnocken zugeordneten Nockenverzahnung in Eingriff steht, und sowohl die Schaltverzahnung als auch die Nockenverzahnung als Schrägverzahnung ausgeführt sind. Das Einstellen der Drehwinkelstellung des Ventilbetätigungsnockens erfolgt also mithilfe des Schaltelements, welches bezüglich der Grund-nockenwelle und/oder dem Nockenträger axial verlagerbar ist. Besonders bevorzugt ist es dabei drehfest bezüglich der Grundnockenwelle gelagert, dreht also mit dieser mit. Das Schaltelement weist die Schaltverzahnung auf, welche mit der Nockenverzahnung in Eingriff steht. Die Nockenverzahnung ist dem Ventilbetätigungsnocken zugeordnet, kann also in einer bevorzugten Ausführungsform an dem Ventilbetätigungsnocken ausgebildet sein.A further development of the invention provides that the adjusting device has an axially displaceable, a switching toothed exhibiting switching element, wherein the switching toothing with a valve actuating cam associated cam teeth is engaged, and both the gear teeth and the cam teeth are designed as helical teeth. The setting of the rotational angle position of the valve actuating cam thus takes place with the aid of the switching element, which is axially displaceable relative to the basic camshaft and / or the cam carrier. It is particularly preferably rotatably mounted with respect to the base camshaft, so it rotates with this. The switching element has the switching toothing, which is in engagement with the cam teeth. The cam teeth are associated with the valve actuating cam, so may be formed in a preferred embodiment of the valve actuating cam.
Alternativ kann die Nockenverzahnung jedoch auch an einem weiteren Element vorliegen, welches mit dem Ventilbetätigungsnocken bevorzugt starr verbunden ist, sodass eine Drehbewegung des weiteren Elements auf den Ventilbetätigungsnocken übertragbar ist. Die Verzahnungen sind jeweils als Schrägverzahnung beziehungsweise als Gewinde ausgeführt. Entsprechend bewirkt die axiale Verlagerung des Schaltelements eine Drehbewegung der Nockenverzahnung und entsprechend des Ventilbetätigungsnockens. Durch eine Wahl der Axialstellung des Schaltelements kann demnach die gewünschte Drehwinkelstellung des Ventilbetätigungsnockens eingestellt werden. Bevorzugt sind die Verzahnungen dabei derart ausgeführt, dass zwar durch die Veränderung der Axialstellung eine Veränderung der Drehwinkelstellung vorgenommen werden kann. Dagegen soll eine auf den Ventilbetätigungsnocken in Umfangsrichtung wirkende Kraft nicht zu einer Drehbewegung des Ventilbetätigungsnockens und damit zu einer Veränderung der Axialstellung führen können. Die Verzahnungen sind bevorzugt mithin selbsthemmend ausgeführt.Alternatively, however, the cam teeth can also be present on a further element, which is preferably rigidly connected to the valve actuating cam, so that a rotational movement of the further element can be transmitted to the valve actuating cam. The teeth are each designed as helical teeth or as a thread. Accordingly, the axial displacement of the switching element causes a rotational movement of the cam teeth and corresponding to the valve actuating cam. By a choice of the axial position of the switching element, therefore, the desired angular position of the valve actuating cam can be adjusted. Preferably, the teeth are designed such that, although by changing the axial position, a change in the angular position can be made. In contrast, a force acting on the valve actuating cam in the circumferential direction should not lead to a rotational movement of the valve actuating cam and thus to a change in the axial position. The teeth are preferably carried out so self-locking.
Eine Weiterbildung der Erfindung sieht vor, dass die Stelleinrichtung über wenigstens eine bezüglich der Grundnockenwelle axial verlagerbare und/oder drehbare Verstellwelle verfügt, die mit dem Ventilbetätigungsnocken wirkverbunden ist. Die Verstellwelle kann prinzipiell beliebig angeordnet sein. Die Verstellwelle ist bezüglich der Grundnockenwelle axial verlagerbar beziehungsweise drehbar. In erstem Fall kann die Verstellwelle beispielsweise zur Betätigung beziehungsweise axialen Verlagerung des vorstehend beschriebenen Schaltelements mit diesem wirkverbunden sein. Die Wirkverbindung der Verstellwelle mit dem Ventilbetätigungsnocken ist also lediglich mittelbar über dieses Schaltelement vorgesehen. Wenn die Verstellwelle bezüglich der Grundnockenwelle drehbar ist, so ist es bevorzugt vorgesehen, dass sie normalerweise mit dieser mitdreht und lediglich zur Veränderung der Drehwinkelstellung des Ventilbetätigungsnockens relativ zu der Grundnockenwelle gedreht wird.A development of the invention provides that the adjusting device has at least one relative to the base camshaft axially displaceable and / or rotatable adjusting shaft, which is operatively connected to the valve actuating cam. The adjusting shaft can in principle be arranged arbitrarily. The adjusting shaft is axially displaceable or rotatable relative to the basic camshaft. In the first case, the adjusting shaft, for example, for the actuation or axial displacement of the switching element described above with this operatively connected. The operative connection of the adjusting shaft with the valve actuating cam is thus provided only indirectly via this switching element. When the adjusting shaft is rotatable with respect to the base camshaft, it is preferably provided that it normally rotates with it and is rotated only to change the rotational angular position of the valve actuating cam relative to the base camshaft.
Eine Weiterbildung der Erfindung sieht vor, dass die Verstellwelle über ein Verstellgetriebe mit dem Ventilbetätigungsnocken wirkverbunden ist. Dies ist insbesondere dann der Fall, wenn das Einstellen der Drehwinkelstellung des Ventilbetätigungsnockens mithilfe der bezüglich der Grundnockenwelle drehbaren Verstellwelle erfolgen soll. Das Verstellgetriebe ist derart in der Wirkverbindung zwischen der Verstellwelle und dem Ventilbetätigungsnocken vorgesehen, dass ein Drehen der Verstellwelle zu einer Veränderung der Drehwinkelstellung des Ventilbetätigungsnockens führt. Das Verstellgetriebe kann derart ausgeführt sein, dass die Verstellwelle und der Ventilbetätigungsnocken jeweils über eine Verzahnung verfügen, wobei diese Verzahnungen unmittelbar miteinander in Eingriff stehen. Entsprechend liegt eine unmittelbare Wirkverbindung zwischen Verstellwelle und Ventilbetätigungsnocken vor.A further development of the invention provides that the adjusting shaft is operatively connected to the valve actuating cam via an adjusting mechanism. This is the case, in particular, when the setting of the rotational angle position of the valve actuating cam is to take place with the aid of the adjusting shaft that is rotatable relative to the basic camshaft. The adjusting mechanism is provided in such a manner in the operative connection between the adjusting shaft and the valve actuating cam, that a rotation of the adjusting shaft leads to a change in the rotational angular position of the valve actuating cam. The adjusting mechanism can be designed such that the adjusting shaft and the valve actuating cam each have a toothing, wherein these teeth are directly in engagement with each other. Accordingly, there is a direct operative connection between the adjusting shaft and the valve actuating cam.
Eine Weiterbildung der Erfindung sieht vor, dass das Verstellgetriebe wenigstens ein Zahnrad aufweist, das in der Wirkverbindung zwischen Verstellwelle und Ventilbetätigungsnocken vorliegt. Entsprechend ist die Wirkverbindung zwischen der Verstellwelle und dem Ventilbetätigungsnocken lediglich mittelbar ausgeführt, nämlich über das wenigstens eine Zahnrad. Dabei ist beispielsweise vorgesehen, dass die Verstellwelle über eine Zahnung verfügt, welche mit einer Zahnung des Zahnrads in Eingriff steht. Letztere steht wiederum mit einer Zahnung des Ventilbetätigungsnocken in Eingriff. Bevorzugt sind die Drehachsen von Verstellwelle, Zahnrad und Ventilbetätigungsnocken zueinander parallel angeordnet. Selbstverständlich kann alternativ jedoch auch ein Winkelversatz vorgesehen sein, wobei die Zahnungen in diesem Fall entsprechend ausgeführt sind. Bei paralleler Anordnung der Drehachsen liegt eine Anordnung von Verstellwelle, Zahnrad und Ventilbetätigungsnocken nach Art eines Planetengetriebes vor; das Verstellgetriebe ist also als solches ausgebildet. Entsprechend können auch mehrere Zahnräder vorgesehen sein, welche gleichmäßig über den Umfang der Verstellwelle verteilt angeordnet sind. Besonders bevorzugt sind drei oder vier Zahnräder vorgesehen.A further development of the invention provides that the adjusting mechanism has at least one toothed wheel which is present in the operative connection between the adjusting shaft and the valve actuating cam. Accordingly, the operative connection between the adjusting and the valve actuating cam is carried out only indirectly, namely on the at least one gear. It is provided, for example, that the adjusting shaft has a toothing which is in engagement with a toothing of the gear. The latter in turn is in engagement with a toothing of the valve actuating cam. Preferably, the axes of rotation of the adjusting shaft, gear and valve actuating cam are arranged parallel to each other. Of course, however, an angular offset may alternatively be provided, the serrations are designed accordingly in this case. In parallel arrangement of the axes of rotation is an arrangement of adjusting, gear and valve actuating cam in the manner of a planetary gear before; the adjusting is thus designed as such. Accordingly, a plurality of gears may be provided, which are arranged distributed uniformly over the circumference of the adjusting. Particularly preferably, three or four gears are provided.
Eine Weiterbildung der Erfindung sieht vor, dass eine Wellenverzahnung der Verstellwelle oder das Zahnrad mit der Nockenverzahnung des Ventilbetätigungsnockens in Eingriff steht. Auf eine derartige Ausführungsform wurde bereits vorstehend eingegangen. Die Verstellwelle verfügt über die Wellenverzahnung, der Ventilbetätigungsnocken über die Nockenverzahnung. Die Verzahnung des Zahnrads steht nun mit beiden in Eingriff. Entsprechend ist über das Zahnrad ein Drehmoment zwischen der Verstellwelle und dem Ventilbetätigungsnocken zum Einstellen der Drehwinkelstellung übertragbar.A further development of the invention provides that a shaft toothing of the adjusting shaft or the toothed wheel is in engagement with the cam toothing of the valve actuating cam. Such an embodiment has already been discussed above. The adjusting shaft has the shaft toothing, the valve actuating cam has the cam toothing. The teeth of the gear is now engaged with both. Accordingly, a torque between the adjusting and the valve actuating cam for adjusting the angular position can be transmitted via the gear.
Eine Weiterbildung der Erfindung sieht vor, dass die Verstellwelle in der Grundnockenwelle aufgenommen und/oder koaxial zu der Grundnockenwelle angeordnet ist. Prinzipiell kann die Verstellwelle bezüglich der Grundnockenwelle beliebig angeordnet sein. Besonders bevorzugt ist die Grundnockenwelle jedoch als Hohlwelle ausgeführt, wobei die Verstellwelle in dem in der Grundnockenwelle vorliegenden Hohlraum angeordnet ist. Dies ermöglicht eine besonders platzsparende Ausführung des Ventiltriebs. In diesem Fall kann es vorgesehen sein, dass die Verstellwelle koaxial zu der Grundnockenwelle vorliegt. Dabei wird die Wirkverbindung bevorzugt über das vorstehend beschriebene Zahnrad nach Art eines Planetengetriebes hergestellt. Selbstverständlich kann es jedoch auch vorgesehen sein, dass die Verstellwelle eine Drehachse aufweist, welche nicht mit der Drehachse der Grundnockenwelle zusammenfällt, sondern vielmehr beabstandet, jedoch parallel zu dieser vorliegt. Das Aufnehmen der Verstellwelle in der Grundnockenwelle kann vollständig oder lediglich bereichsweise vorgesehen sein. In letzterem Fall ragt wenigstens ein Bereich der Verstellwelle über den Umfang der Grundnockenwelle heraus.A further development of the invention provides that the adjusting shaft is received in the basic camshaft and / or arranged coaxially with the base camshaft. In principle, the adjusting shaft can be arranged arbitrarily with respect to the basic camshaft. However, the base camshaft is particularly preferably designed as a hollow shaft, wherein the adjusting shaft is arranged in the cavity present in the base camshaft. This allows a particularly space-saving design of the valve train. In this case, it may be provided that the adjusting shaft is coaxial with the base camshaft. In this case, the active compound is preferably produced via the gear described above in the manner of a planetary gear. Of course, it can also be provided that the adjusting shaft has an axis of rotation which does not coincide with the axis of rotation of the base camshaft, but rather spaced, but parallel to this. The recording of the adjusting shaft in the basic camshaft can be provided completely or only partially. In the latter case, at least one region of the adjusting shaft projects beyond the circumference of the basic camshaft.
Eine Weiterbildung der Erfindung sieht vor, dass die Verstellwelle über ein die Grundnockenwelle durchgreifendes Halteelement mit dem Ventilbetätigungsnocken wirkverbunden ist. Dieses Halteelement kann beispielsweise als Nutstein oder dergleichen vorliegen. Über das Halteelement ist der Ventilbetätigungsnocken drehfest mit der Verstellwelle verbunden. Eine Drehung der Verstellwelle bewirkt demnach unmittelbar eine Veränderung der Drehwinkelstellung des Ventilbetätigungsnockens. Das Halteelement durchgreift die Grundnockenwelle vorzugsweise in radialer Richtung. Das bedeutet, dass die Verstellwelle wenigstens bereichsweise in der Grundnockenwelle aufgenommen ist, während der Ventilbetätigungsnocken in radialer Richtung außerhalb der Grundnockenwelle vorliegt. Das Halteelement kann eine axiale Verlagerung von Verstellwelle und Ventilbetätigungsnocken zueinander zulassen, sodass ein Verschieben des Ventilbetätigungsnockens zusammen mit dem Nockenträger zusätzlich möglich ist.A further development of the invention provides that the adjusting shaft is operatively connected to the valve actuating cam via a holding element that passes through the basic camshaft. This holding element can be present for example as a sliding block or the like. About the retaining element of the valve actuating cam is rotatably connected to the adjusting shaft. Accordingly, a rotation of the adjusting shaft directly causes a change in the rotational angle position of the valve actuating cam. The retaining element preferably passes through the base camshaft in the radial direction. This means that the adjusting shaft is at least partially received in the basic camshaft, while the valve actuating cam is present in the radial direction outside of the basic camshaft. The holding element may allow an axial displacement of the adjusting shaft and the valve actuating cam to each other, so that a displacement of the valve actuating cam together with the cam carrier is additionally possible.
Eine Weiterbildung der Erfindung sieht vor, dass das Einstellen der Drehwinkelstellung und der Axialposition mithilfe eines einzigen Aktuators erfolgt. Es kann grundsätzlich vorgesehen sein, dass mehrere separate Aktuatoren vorliegen, wobei wenigstens einer für das axiale Verschieben des Nockenträgers und wenigstens ein anderer für das Einstellen der Drehwinkelstellung Anwendung findet. Vorteilhafter ist es jedoch, lediglich einen einzigen Aktuator und/oder eine einzige Schaltkulisse zum Einstellen der Drehwinkelstellung und der Axialposition dem Ventiltrieb zu verwenden. Bei jeder der genannten Ausführungsformen kann jeder Aktuator und/oder jede Schaltkulisse zum Einstellen von wenigstens zwei verschiedenen Drehwinkelstellungen und/oder von wenigstens zwei Axialposition dienen. Um das Einstellen mithilfe des einzigen Aktuators beziehungsweise der einzigen Schaltkulisse zu ermöglichen, kann es vorgesehen sein, dass die Drehwinkelstellung und/oder die Axialposition arretierbar sind. Dazu ist beispielsweise der Nockenträger mit dem Schaltelement und/oder der Verstellwelle verbunden.A further development of the invention provides that the setting of the angular position and the axial position takes place by means of a single actuator. It may in principle be provided that there are a plurality of separate actuators, at least one being used for the axial displacement of the cam carrier and at least one other for setting the rotational angle position. It is more advantageous, however, to use only a single actuator and / or a single shift gate for adjusting the rotational angular position and the axial position of the valve train. In each of the aforementioned embodiments, each actuator and / or each shift gate may serve to set at least two different angular positions and / or at least two axial positions. In order to enable the setting by means of the single actuator or the single shift gate, it can be provided that the rotational angle position and / or the axial position can be locked. For this purpose, for example, the cam carrier is connected to the switching element and / or the adjusting shaft.
Das Arretieren der Drehwinkelstellung und/oder der Axialposition ist beispielsweise durch Einrasten realisiert, sodass für eine Veränderung von Drehwinkelstellung und/oder Axialposition eine Kraft aufzubringen ist, die eine jeweilige Verstellkraft überschreitet. Wird nun die Verstellkraft für das Verstellen der Drehwinkelstellung von der Verstellkraft für das Verstellen der Axialposition (oder umgekehrt) verschieden gewählt, so kann bei Aufbringen einer ersten, beispielsweise kleineren Kraft, nur die eine Größe, bei Aufbringen einer zweiten, beispielsweise größeren Kraft, nur die andere Größe verändert werden. Zusätzlich kann das Arretieren auch schaltbar, also gezielt, erfolgen. Durch Lösen oder Herstellen der Arretierung kann folglich beeinflusst werden, ob die Drehwinkelstellung oder die Axialposition mithilfe des einzigen Aktuators verstellbar sein soll. Bevorzugt ist die Axialposition schaltbar arretiert, während die Drehwinkelstellung nicht schaltbar arretiert ist. Das Einstellen der Drehwinkelstellung und der Axialposition wird bei Verwendung des einzigen Aktuators also über das Arretieren gesteuert.The locking of the angular position and / or the axial position is realized, for example, by latching, so that for a change of rotational position and / or axial position, a force is applied, which exceeds a respective adjusting force. If now the adjusting force for the adjustment of the rotational angle position of the adjusting force for adjusting the axial position (or vice versa) selected differently, so when applying a first, for example smaller force, only one size, upon application of a second, for example, greater force, only the other size will be changed. In addition, the locking can also switchable, so targeted, done. By loosening or making the lock can thus be influenced whether the rotational position or the axial position using the single actuator should be adjustable. Preferably, the axial position is locked switchable, while the rotational angle position is not locked switchable. The setting of the angular position and the axial position is thus controlled when using the single actuator on the locking.
Die Erfindung wird nachfolgend anhand der in der Zeichnung dargestellten Ausführungsbeispiele näher erläutert, ohne dass eine Beschränkung der Erfindung erfolgt. Dabei zeigt:
Figur 1- eine teilweise geschnittene Ansicht eines Bereichs eines Ventiltriebs einer Brennkraftmaschine in einer ersten Ausführungsform,
Figur 2- den Ventiltrieb in einer zweiten Ausführungsform,
Figur 3- den Ventiltrieb in einer dritten Ausführungsform,
Figur 4- eine vierte Ausführungsform des Ventiltriebs,
Figur 5- den bereits bekannten Ventiltrieb in einer fünften Ausführungsform,
Figur 6- eine sechste Ausführungsform des Ventiltriebs,
Figur 7- eine siebte Ausführungsform des Ventiltriebs, und
Figur 8- eine achte Ausführungsform des Ventiltriebs.
- FIG. 1
- 2 is a partial sectional view of a portion of a valvetrain of an internal combustion engine in a first embodiment;
- FIG. 2
- the valve train in a second embodiment,
- FIG. 3
- the valve train in a third embodiment,
- FIG. 4
- a fourth embodiment of the valve train,
- FIG. 5
- the already known valve train in a fifth embodiment,
- FIG. 6
- a sixth embodiment of the valve train,
- FIG. 7
- a seventh embodiment of the valve train, and
- FIG. 8
- an eighth embodiment of the valve train.
Die
Die Ventilbetätigungsnocken 5 und 6 dienen der Betätigung von nicht dargestellten Gaswechselventilen der Brennkraftmaschine. Die Ventilbetätigungsnocken 5 und 6 sind exzentrisch, wobei die Exzentrizitäten in unterschiedlichen Winkelpositionen beziehungsweise Umfangspositionen bezüglich des Nockenträgers 3 vorliegen und/oder unterschiedliche Erstreckungen in radialer Richtung und/oder Umfangsrichtungen aufweisen können. Zur Betätigung der hier nicht dargestellten Gaswechselventile wirken die Ventilbetätigungsnocken 5 und 6 beispielsweise mit Rollenschlepphebeln des jeweiligen Gaswechselventils durch Anlagekontakt zusammen. Jedem der Rollenschlepphebel sind dabei die jeweiligen Ventilbetätigungsnocken 5 und 6 der entsprechenden Nockengruppe 7 zugeordnet. Ein erster der Rollenschlepphebel wird also von einem der Ventilbetätigungsnocken 5 und 6 der Nockengruppe 7 und ein weiterer der Rollenschlepphebel von einem der Ventilbetätigungsnocken einer weiteren Nockengruppe betätigt.The
Bedingt durch die unterschiedlichen Ausgestaltungen der Ventilbetätigungsnocken 5 und 6 der Nockengruppe 7 untereinander stellt sich somit ein entsprechender Hub, Öffnungszeitpunkt und/oder eine Öffnungsdauer des Gaswechselventils ein. Durch axiales Verschieben des Nockenträgers 3 können die Rollenschlepphebel von dem Ventilbetätigungsnocken 5 oder 6 der jeweiligen Nockengruppe 7 betätigbar sein. Der Nockenträger 3 wird beispielsweise in Abhängigkeit von einem Betriebszustand der Brennkraftmaschine verlagert, sodass stets derjenige Ventilbetätigungsnocken 5 oder 6 mit dem entsprechenden Rollenschlepphebel zu dessen Betätigung zusammenwirkt, mit welchem beispielsweise ein optimaler Wirkungsgrad beziehungsweise eine optimale Leistung der Brennkraftmaschine erzielbar ist.Due to the different configurations of the
Die Verlagerung des Nockenträgers 3 wird mithilfe eines hier nicht dargestellten Aktuators bewirkt, welcher ebenfalls Bestandteil der Axialstelleinrichtung ist und einen in radialer Richtung verlagerbaren Mitnehmer aufweist. Zur Verlagerung des Nockenträgers 3 wird der Mitnehmer in radialer Richtung derart verlagert, dass er beispielsweise in eine Kulissenbahn 9 der Schaltkulisse 8 oder in eine Kulissenbahn der weiteren Schaltkulisse eingreift. Die Kulissenbahn 9 ist derart ausgestaltet, dass die Schaltkulisse 8 bei einem Einbringen des Mitnehmers, während sich der Nockenträger 3 in einer ersten Axialposition befindet, in Richtung einer zweiten Axialposition gedrängt wird und umgekehrt. Selbstverständlich ist auch eine Verlagerung des Nockenträgers 3 zwischen mehr als zwei Axialpositionen möglich und mithilfe einer entsprechend angepassten Schaltkulisse 8 beziehungsweise Axialstelleinrichtung realisierbar.The displacement of the
Neben der Axialposition des Nockenträgers 3 und damit auch den Axialposition der Ventilbetätigungsnocken 5 und 6 soll nun zusätzlich eine Drehwinkelstellung der Ventilbetätigungsnocken 5 und 6 bezüglich des Nockenträgers 3 einstellbar sein. Zu diesem Zweck ist eine Stelleinrichtung 10 vorgesehen. Zusätzlich sind die Ventilbetätigungsnocken 5 und 6 drehbar gelagert. Diese drehbare Lagerung ist in dem hier dargestellten Ausführungsbeispiel auf dem Nockenträger 3 vorgesehen. Die Stelleinrichtung 10 weist ein axial verlagerbares Schaltelement 11 auf. Dieses umgreift die Grundnockenwelle 2 und ist mithin an dieser axial verlagerbar gelagert. Das Schaltelement 11 wird seinerseits bereichsweise von den Ventilbetätigungsnocken 5 und 6 umgriffen, welche in der hier dargestellten Ausführungsform einstückig und materialeinheitlich ausgeführt sind. Das Schaltelement 11 verfügt über eine Schaltverzahnung 12, welche als Außenverzahnung vorliegt, während die Ventilbetätigungsnocken 5 und 6 eine Nockenverzahnung 13 aufweisen, die als Innenverzahnung vorliegt. Die Schaltverzahnung 12 und die Nockenverzahnung 13 sind als Schrägverzahnungen ausgeführt und stehen miteinander in Eingriff. Das bedeutet, dass durch eine Verlagerung des Schaltelements 11 in axialer Richtung eine Drehbewegung der Ventilbetätigungsnocken 5 und 6 erzielt wird. Durch entsprechende Wahl der Axialstellung des Schaltelements 11 kann demnach die Drehwinkelstellung der Ventilbetätigungsnocken 5 und 6 eingestellt beziehungsweise ausgewählt werden. In der hier dargestellten Ausführungsform ist das Schaltelement 11 mit der Schaltkulisse 8 wirkverbunden. Mithilfe der Schaltkulisse 8 kann also das Schaltelement 11 in axialer Richtung verlagert werden, sodass die Drehbewegung der Ventilbetätigungsnocken 5 und 6 erzielt wird.In addition to the axial position of the
Die
Zwischen der Verstellwelle 14 und den Ventilbetätigungsnocken 5 und 6 ist ein Verstellgetriebe 16 vorgesehen, welches in dem vorliegenden Ausführungsbeispiel über wenigstens ein Zahnrad 17 verfügt. Bevorzugt sind mehrere Zahnräder 17 vorgesehen, welche in radialer Richtung zwischen der Verstellwelle 14 und den Ventilbetätigungsnocken 5 und 6 vorliegen. Das Zahnrad 17 beziehungsweise seine Verzahnung steht sowohl mit der Wellenverzahnung 15 als auch der Nockenverzahnung 13 in Eingriff. Durch eine Drehbewegung der Verstellwelle 14 kann demnach die Drehwinkelstellung der Ventilbetätigungsnocken 5 und 6 verändert werden.Between the adjusting
Die
Die
Anhand der
Aus der
Die
Die zweite Arretiereinrichtung 25 ist beispielsweise analog zu der ersten Arretiereinrichtung 24 aufgebaut und besteht aus einem Rastelement 28 und mehreren Rastvertiefungen 29. Auch andere Ausführungsformen sind jedoch denkbar. Das Rastelement 28 ist beispielsweise an dem Nockenträger 3, die Rastvertiefungen 29 an der Schaltkulisse 8 befestigt. Das Rastelement 28 wird in der hier gezeigten Ausführungsform in radialer Richtung nach außen gedrängt, sodass es in eine der Rastvertiefungen 29 eingreift. Mithin kann die Schaltkulisse 8 durch Aufbringen einer zweiten Verstellkraft in axialer Richtung bezüglich des Nockenträgers 3 verlagert werden. Die Schaltkulisse 8 ist mit dem Schaltelement 11 wirkverbunden, sodass eine derartige axiale Verlagerung auch eine axiale Verlagerung des Schaltelements 11 und in Folge eine Änderung der Drehwinkelstellung der Ventilbetätigungsnocken 5 und 6 bewirkt.The
Durch entsprechende Wahl der ersten Verstellkraft und der zweiten Verstellkraft kann somit erreicht werden, dass bei Aufbringen einer bestimmten Kraft auf die Schaltkulisse 8 in axialer Richtung zuerst ein Einstellen der Drehwinkelstellung oder ein Einstellen der Axialposition des Nockenträgers 3 erfolgt. Erst bei Erreichen einer Endposition durch das Element, welches die kleinere Verstellkraft aufweist, wird somit das Element eingestellt, welches die größere Verstellkraft aufweist. Selbstverständlich kann jedoch auch wenigstens eine der Arretiereinrichtungen 24 und 25, bevorzugt beide, schaltbar ausgelegt sein. In diesem Fall kann das Rastelement 26 beziehungsweise das Rastelement 28 gezielt aus der jeweiligen Rastvertiefung 27 beziehungsweise 29 herausverlagert werden, sodass die jeweilige Verstellkraft wählbar ist. So kann beispielsweise das Rastelement 26 aus der Rastvertiefung 27 herausverlagert werden, um bei dem nächsten Betätigen der Schaltkulisse 8 lediglich eine Verlagerung des Nockenträgers 3, jedoch kein Verlagern des Schaltelements 11 zu bewirken. Umgekehrt kann das Rastelement 26 derart in Richtung der Rastvertiefung 27 gedrängt sein, dass bei einer derartigen Betätigung der Schaltkulisse 8 keine Verlagerung des Nockenträgers 3 erfolgen kann, sodass stattdessen das Schaltelement 11 bewegt und mithin die gewünschte Drehwinkelstellung der Ventilbetätigungsnocken 5 und 6 eingestellt wird.By appropriate selection of the first adjusting force and the second adjusting force can thus be achieved that upon application of a certain force on the
Die
Der Nockenträger 3 ist beispielsweise mithilfe von Lagern 23 gelagert. Der Nockenträger 3 kann einem oder mehreren Zylindern der Brennkraftmaschine zugeordnet sein und der Betätigung der jeweiligen Ventilbetätigungsnocken dienen. Neben den Ventilbetätigungsnocken 5, 6, 20 und 21 kann er weitere Ventilbetätigungsnocken 31, 32, 33 und 34 aufweisen, die Nockengruppen 35 und 36 zugeordnet sind. Diese Ventilbetätigungsnocken 31 bis 34 sind fest an dem Nockenträger 3 angebracht. Sie lassen sich also gemeinsam mit diesem in axialer Richtung verlagern, sind jedoch nicht mithilfe der Schaltkulisse 8 hinsichtlich ihrer Drehwinkelstellung verstellbar. Die jeweilige Schaltverzahnung 12 und Nockenverzahnung 13 der Ventilbetätigungsnocken 5 und 6 beziehungsweise 20 und 21 können derart ausgeführt sein, dass eine Verlagerung der Schaltkulisse 8 bezüglich des Nockenträger 3 in axialer Richtung eine Veränderung der Drehwinkelstellung der jeweiligen Ventilbetätigungsnocken 5 und 6 beziehungsweise 20 und 21 in dieselbe oder gegenläufige Richtung bewirkt. Mithilfe der Stelleinrichtung 10 können also mehrere dem Nockenträger 3 zugeordnete Nockengruppen 7 und 22 in eine bestimmte Drehwinkelstellung gebracht werden. Die andere Schaltkulisse 30 dient dagegen dem axialen Verlagern des gesamten Nockenträgers 3 mitsamt aller Ventilbetätigungsnocken 5, 6, 20, 21 sowie 31 bis 34. Grundsätzlich kann eine beliebige Anzahl von Ventilbetätigungsnocken und/oder Nockengruppen vorliegen.The
Grundsätzlich kann die Schaltkulisse 8 beziehungsweise 30 beliebig ausgestaltet sein. Beispielsweise sind sie zum Zusammenspiel mit einem Mehrpin-Aktuator, insbesondere einem Zwei-Pin-Aktuator oder einem Drei-Pin-Aktuator, ausgebildet. Diese weisen im Gegensatz zu der hier vorgestellten Ausführungsform mehr als einen Mitnehmer, nämlich zwei beziehungsweise drei, in Form von Pins auf. Allen Ausführungsbeispielen ist gemeinsam, dass die Drehwinkelstellung stets unabhängig von der Axialposition einstellbar ist. Auf diese Weise ist beispielsweise eine Anpassung der Zylinderfüllung und/oder des Ladungsbewegungszustands (welche jeweils Betriebsparameter der Drehwinkelstellung sind) in mindestens zwei, vorzugweise jedoch mehr als zwei, verschiedenen Betriebszuständen der Brennkraftmaschine, in welchen verschiedene Axialpositionen vorliegen, möglich. Das Einstellen der Axialposition und der Drehwinkelstellung kann selbstverständlich in beliebiger Reihenfolge oder gleichzeitig erfolgen. Grundsätzlich kann die Grundnockenwelle über einen Phasensteller mit der Kurbelwelle wirkverbunden sein, mittels welchem eine Winkelstellung der Grundnockenwelle bezüglich der Kurbelwelle zusätzlich einstellbar ist.In principle, the
- 11
- Ventiltriebvalve train
- 22
- Grundnockenwellebase camshaft
- 33
- Nockenträgercam support
- 44
- Längsachelongitudinal axis
- 55
- VentilbetätigungsnockenValve actuating cam
- 66
- VentilbetätigungsnockenValve actuating cam
- 77
- Nockengruppecam group
- 88th
- Schaltkulisseshift gate
- 99
- Kulissenbahnlink path
- 1010
- Stelleinrichtungsetting device
- 1111
- Schaltelementswitching element
- 1212
- Schaltverzahnungshift gearing
- 1313
- Nockenverzahnungcam teeth
- 1414
- Verstellwelleadjusting
- 1515
- Wellenverzahnungshaft splines
- 1616
- Verstellgetriebevariator
- 1717
- Zahnradgear
- 1818
- Ausnehmungrecess
- 1919
- Halteelementretaining element
- 2020
- VentilbetätigungsnockenValve actuating cam
- 2121
- VentilbetätigungsnockenValve actuating cam
- 2222
- Nockengruppecam group
- 2323
- Lagercamp
- 2424
- 1. Arretiereinrichtung1st Arretiereinrichtung
- 2525
- 2. Arretiereinrichtung2nd Arretiereinrichtung
- 2626
- Rastelementlocking element
- 2727
- Rastvertiefunglatching depression
- 2828
- Rastelementlocking element
- 2929
- Rastvertiefunglatching depression
- 3030
- Schaltkulisseshift gate
- 3131
- VentilbetätigungsnockenValve actuating cam
- 3232
- VentilbetätigungsnockenValve actuating cam
- 3333
- VentilbetätigungsnockenValve actuating cam
- 3434
- VentilbetätigungsnockenValve actuating cam
- 3535
- Nockengruppecam group
- 3636
- Nockengruppecam group
Claims (10)
- Valve train (1) of an internal combustion engine, comprising at least one main camshaft (2) on which at least one cam carrier (3) is provided in a rotationally fixed manner and axially displaceably between at least two axial positions, wherein at least one valve actuating cam for actuating a gas exchange valve of the internal combustion engine is assigned to the cam carrier (3), characterised in that the valve actuating cam (5, 6) is rotatably mounted and a rotary angular position of the valve actuating cam (5, 6) relative to the cam carrier (3) is adjustable by means of a setting device (10).
- Valve train according to claim 1, characterised in that the valve actuating cam (5, 6) is rotatably mounted at, preferably on, the cam carrier (3) and/or the main camshaft (2).
- Valve train according to one of the preceding claims, characterised in that the setting device (10) has an axially displaceable switching element (11) which has a switching toothing (12), wherein the switching toothing (12) engages with a cam toothing (13) assigned to the valve actuating cam (5, 6), and both the switching toothing (12) and also the cam toothing (13) are configured as helical toothing.
- Valve train according to one of the preceding claims, characterised in that the setting device (10) has at least one adjusting shaft (14) which is axially displaceable and/or rotatable relative to the main camshaft (2) and is operatively connected to the valve actuating cam (5, 6).
- Valve train according to one of the preceding claims, characterised in that the adjusting shaft (14) is operatively connected to the valve actuating cam (5, 6) via an adjusting gear (16).
- Valve train according to one of the preceding claims, wherein the adjusting gear (16) comprises at least one gear wheel (17) and is situated in the operative connection between the adjusting shaft (14) and the valve actuating cam (5, 6).
- Valve train according to one of the preceding claims, characterised in that a shaft toothing (15) of the adjusting shaft (14) or the gear wheel (17) engages with the cam toothing (13) of the valve actuating cam (5, 6).
- Valve train according to one of the preceding claims, characterised in that the adjusting shaft (14) is received in the main camshaft (2) and/or disposed coaxially relative to the main camshaft (2).
- Valve train according to one of the preceding claims, characterised in that the adjusting shaft (14) is operatively connected to the valve actuating cam (5, 6) via a holding element (19) which traverses the main camshaft (2).
- Valve train according to one of the preceding claims, characterised in that the adjustment of the rotary angular position and the axial position takes place by means of one single actuator.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201210008698 DE102012008698A1 (en) | 2012-04-28 | 2012-04-28 | Valve gear of an internal combustion engine |
PCT/EP2013/001259 WO2013159937A1 (en) | 2012-04-28 | 2013-04-26 | Valve drive of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2841723A1 EP2841723A1 (en) | 2015-03-04 |
EP2841723B1 true EP2841723B1 (en) | 2015-12-02 |
Family
ID=48468199
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13723664.2A Active EP2841723B1 (en) | 2012-04-28 | 2013-04-26 | Valve drive of an internal combustion engine |
Country Status (5)
Country | Link |
---|---|
US (1) | US9228456B2 (en) |
EP (1) | EP2841723B1 (en) |
CN (1) | CN104271903B (en) |
DE (1) | DE102012008698A1 (en) |
WO (1) | WO2013159937A1 (en) |
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Publication number | Priority date | Publication date | Assignee | Title |
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DE102013225865B4 (en) * | 2013-12-13 | 2022-12-15 | Volkswagen Aktiengesellschaft | camshaft |
US10072537B2 (en) | 2015-07-23 | 2018-09-11 | Husco Automotive Holdings Llc | Mechanical cam phasing system and methods |
DE102015009877A1 (en) * | 2015-07-29 | 2017-02-02 | Daimler Ag | Valve train device, internal combustion engine with a valve drive device and method for operating a valve drive device |
US10539051B2 (en) | 2015-11-06 | 2020-01-21 | Borgwarner Inc. | Valve operating system providing variable valve lift and/or variable valve timing |
DE102016125640A1 (en) | 2016-12-23 | 2018-06-28 | Karlsruher Institut Für Technologie (Kit) | Process for producing a metallic shaped body |
JP7066419B2 (en) | 2017-01-20 | 2022-05-13 | フスコ オートモーティブ ホールディングス エル・エル・シー | Cam phase adjustment system and cam phase adjustment method |
US10494961B2 (en) | 2017-06-28 | 2019-12-03 | Borgwarner Inc. | Camshaft driven pump for a hydraulic cam phaser |
USD902252S1 (en) * | 2018-06-04 | 2020-11-17 | Transportation IP Holdings, LLP | Modular cam shaft |
CN108952868B (en) * | 2018-06-19 | 2020-12-01 | 奇瑞汽车股份有限公司 | Variable camshaft and engine adopting same |
US10900387B2 (en) | 2018-12-07 | 2021-01-26 | Husco Automotive Holdings Llc | Mechanical cam phasing systems and methods |
US12098661B2 (en) | 2022-11-02 | 2024-09-24 | Husco Automotive Holdings Llc | Cam phase actuator control systems and methods |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004011586A1 (en) | 2003-03-21 | 2004-10-07 | Audi Ag | Valve gear for internal combustion engine has facility whereby in first and second axial positions of cam carrier first and second stop faces fixed on cam carrier bear against respective first and second stop faces fixed on cylinder head |
DE10349902A1 (en) * | 2003-10-25 | 2005-06-23 | Audi Ag | Valve drive for an I.C. engine comprises a camshaft with a cam piece with cams having running surfaces |
DE102005031241A1 (en) | 2005-07-01 | 2007-01-04 | Fev Motorentechnik Gmbh | Variable valve train of a piston internal combustion engine |
DE102007010151A1 (en) * | 2007-03-02 | 2008-04-24 | Audi Ag | Valve drive of internal combustion engine, has camshaft, which is supported in housing of internal combustion engine in rotating manner, and cam support in torque proof manner and axially moved on camshaft |
DE102007024600A1 (en) | 2007-05-25 | 2008-11-27 | Schaeffler Kg | Operating device for controlling stroke variable valve gear of internal combustion engine, has latching element stressing actuator pin supporting surface by force in extending direction of pin in operating position of pin |
DE102008035935A1 (en) * | 2008-07-31 | 2010-02-11 | Audi Ag | Toothed shaft connection and valve drive with toothed shaft connection between a camshaft and displaceable cam carriers |
DE102008036030A1 (en) * | 2008-08-01 | 2010-02-04 | Daimler Ag | Valve train device for use in internal-combustion engine, has set of cams arranged on set of cam elements, and bearing device rotatably mounting set of partial cams on cam elements in axial and firm manner |
DE102008060170A1 (en) * | 2008-11-27 | 2010-06-02 | Dr.Ing.H.C.F.Porsche Aktiengesellschaft | Valve gear of an internal combustion engine |
DE102009014517B4 (en) * | 2009-03-23 | 2020-01-09 | Audi Ag | Valve train for gas exchange valves of an internal combustion engine with a displaceable camshaft sensor wheel |
DE102009034990A1 (en) * | 2009-07-28 | 2011-02-03 | Daimler Ag | Valve drive device |
DE102010004591B4 (en) * | 2010-01-14 | 2021-08-19 | Audi Ag | Built cam carrier for valve train |
DE102010035186A1 (en) * | 2010-08-24 | 2012-03-01 | Schaeffler Technologies Gmbh & Co. Kg | Valve train for use in internal combustion engine, has actuator associated to sensors and arranged on axial region for detecting instantaneous axial positions, where actuator is exactly assigned to cam pieces |
-
2012
- 2012-04-28 DE DE201210008698 patent/DE102012008698A1/en not_active Withdrawn
-
2013
- 2013-04-26 US US14/397,445 patent/US9228456B2/en active Active
- 2013-04-26 EP EP13723664.2A patent/EP2841723B1/en active Active
- 2013-04-26 WO PCT/EP2013/001259 patent/WO2013159937A1/en active Application Filing
- 2013-04-26 CN CN201380022460.8A patent/CN104271903B/en active Active
Also Published As
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WO2013159937A1 (en) | 2013-10-31 |
US20150122209A1 (en) | 2015-05-07 |
DE102012008698A1 (en) | 2013-10-31 |
EP2841723A1 (en) | 2015-03-04 |
CN104271903A (en) | 2015-01-07 |
US9228456B2 (en) | 2016-01-05 |
CN104271903B (en) | 2016-04-27 |
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