EP3161282A1 - Device for adjusting a camshaft of an internal combustion engine - Google Patents
Device for adjusting a camshaft of an internal combustion engineInfo
- Publication number
- EP3161282A1 EP3161282A1 EP15738599.8A EP15738599A EP3161282A1 EP 3161282 A1 EP3161282 A1 EP 3161282A1 EP 15738599 A EP15738599 A EP 15738599A EP 3161282 A1 EP3161282 A1 EP 3161282A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- individual
- groove
- control groove
- plunger
- camshaft
- 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.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 8
- 230000000694 effects Effects 0.000 claims abstract description 10
- 230000002093 peripheral effect Effects 0.000 claims abstract 3
- 238000006073 displacement reaction Methods 0.000 claims description 5
- 238000011161 development Methods 0.000 description 10
- 230000018109 developmental process Effects 0.000 description 10
- 230000004913 activation Effects 0.000 description 3
- 238000001994 activation Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 230000003993 interaction Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 230000000007 visual effect Effects 0.000 description 1
Classifications
-
- 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
- F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
-
- 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
-
- 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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
-
- 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
- F01L2013/0052—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 with cams provided on an axially slidable sleeve
-
- 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
- F01L2013/0084—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 by modification of cam contact point by radially displacing the camshaft
Definitions
- the present invention relates to a device for adjusting the camshaft of an internal combustion engine according to the preamble of the main claim.
- this known device shows how actuating means in the form of an electromagnetically driven ram unit by cooperation with a lifting profile can cause an axial, predetermined by the course of the cam groove adjustment of the camshaft, such as with the purpose of assigning a cam different cam tracks switchable.
- actuating means in the form of an electromagnetically driven ram unit by cooperation with a lifting profile can cause an axial, predetermined by the course of the cam groove adjustment of the camshaft, such as with the purpose of assigning a cam different cam tracks switchable.
- known and generic education presupposed devices typically several plungers (actuating pins) are used so that, depending on the axial displacement position of the Hubprofilbaue, each engage a suitable the control groove against standing pin and can cause the respective intended axial displacement.
- this is not problematic, but it is due to a faulty control of the actuating means (ie it is not the correct, currently the control groove opposed individual plunger driven, but an adjacent, outside of the overlap with the Hubprofilbaueria) causes a plunger feed without this Tappet (upon further rotation of the Hubprofilbaueria) can be reset.
- the generic and assumed as a superscript camshaft adjustment principle is that although electromagnetically advanced plunger engage in the control groove, a provision (ie a return) of the plunger in question, however, happens that the trained with variable groove depth control back the concerning push rod back into the starting position.
- plunger units for the actuating means which can be automatically (for example also in turn electromagnetically) transferred from the driven feed position back into the reset initial position.
- this not only causes considerable additional design effort in the realization of the actuators used for the actuating means, but in turn, in anyway limited space, such a solution again generate additional space disadvantages.
- Object of the present invention is therefore to design a device for camshaft adjustment compact according to the preamble of the main claim and to improve in terms of reliable restoring and traceability of the plunger unit so that this, even without the need for an automatic reset and only by interaction with the Hubprofilbaueria, can be returned to an initial position, even if the Hubprofilbaueria has a compact axial extent and switching states or ram positions permits, in which - along the axial direction - an individual plunger of the plunger unit can be positioned axially outside the Hubprofilbauè.
- the two individual plungers of the plunger unit adjacent to each other and preferably axially parallel enable at least one of the individual plungers to be positioned above or for cooperation with the control groove in each operating state so that the activation of the first individual plunger (FIG. more precisely: the activation of the preferably associated electromagnetic actuator to effect the plunger feed) already generates a defined axial relationship between the plunger unit and the Hubprofilbau- group.
- the second individual plunger in an - unintentionally and ineffective - extended (advanced) position would first by this constructive realization of the second single plunger in an axial Position in overlap with the Hubprofilbauè spent (and outside the control groove), wherein the additionally inventively formed on the Hubprofilbauè outside the control groove radially (or alternatively also axially) height-modified (namely increased) section or the ramp section then upon further rotation of the shaft (including ansitzender Hubprofilbau devise) on the ramp effect then causes the reminds too or take away the second single plunger.
- the realization of the first variant of the invention with two independently controllable and drivable individual tappets ensures that even an unintentionally or incorrectly pushed forward of the individual plunger outside the control groove (which causes the proper restitution for the other, cooperating of the individual plunger) can be pushed back or reset so that then a properly located in the retracted initial position ram unit for further activations and switching operations without the risk of damaging the engine is available.
- the second solution aspect of the invention enables the same advantageous effects;
- the individual tappets are mechanically coupled to each other such that driving or returning one of the individual tappets automatically causes the same movement of the other of the individual tappets, so it does not need in this pairwise solution of the radially height-changed portion or the ramp portion of the first solution variant.
- the height profile of the radially height-changed section (or of the ramp section) in such a way that it corresponds to the course of the groove depth.
- mutually parallel and aligned individual tappets so a rectified return movement is effected in corresponding return strokes.
- the height profile (in a developed projection of the circumference) is also preferable for the height profile (in a developed projection of the circumference) to be at least partially linear. designed in order to ensure so far in a uniformity in the return or driver movement.
- control groove so that it is delimited on both sides by a radially projecting wall along its course, which according to a further advantageous development has a constant wall thickness in order to simplify the geometric conditions to combine with ease of manufacture.
- the present invention is particularly suitable for (in the axial direction narrow) Hubprofilbau phenomenon having - in the settlement - an S- or Z-shaped control groove
- the present invention is nevertheless not limited to such Nutenverterrorism or contours.
- the axial extension of Hubprofilbauer limited to a maximum of three times, preferably the maximum double and more preferably at most 1, 5 times the distance of the individual plunger from each other (each measured by the distance of the respective plunger central axes) , Again, however, it is an advantageous development that does not limit the basic applicability of the invention to other geometric conditions.
- FIG. 1 (c) shows three schematics of the embodiment of a lifting profile assembly with control groove and this schematically associated plunger unit of two individual plungers according to a first embodiment, wherein the partial figure (a) is a side view with schematically drawn Nutenverlauf and positions of the first single plunger in engagement along a Rotation of Hubprofilbaueria shows, in vertically developed representation, part figure (b) is a plan view of the groove course in developed view with three possible
- FIG. 2 with associated sections corresponds to the representations of FIG. 1 and position 1 of FIG. 2 illustrates an alternative relative position of the individual plungers to the lift profile assembly;
- FIG. 3 (c) shows, analogously to the representations of FIG. 1, a second exemplary embodiment which is varied with respect to the first exemplary embodiment of FIGS. 1 and 2, in which the pair of individual tappets is coupled to one another;
- FIG. 6 (g) Schematic views of a third embodiment, which additionally varies the second embodiment of Figures 3 to 5, wherein a shown in the development of Figures 3 to 5 simple Z-curve in Fig. 6 in addition to another, axially entge - Added Z-course along the unwound circumference is added, a perspective view of actuating means with a plunger unit; and
- FIG. 1 illustrates first in the developed plan view of the part figure (b), as on a circumferential outer surface of Hubprofilbauffle 10 (shift gate) a control groove 12 is formed, which along the unwound circumference (0 ° to 360 °) has the shown S- or Z-shaped groove profile.
- This cam groove 12 has the changed groove depth profile (dashed line 14) recognizable in the subfigure (a) of FIG.
- the first exemplary embodiment of FIG. 1 shown by the shaded area 20 outside the control groove, has a ramp section which has a height profile (more precisely, a linearly rising profile) corresponding to the control groove.
- the purpose of this ramp section is the (potentially unnecessarily or erroneously extended) second single plunger P1 back to its pushed back home position to spend. This happens because from the position of FIG.
- the rising ramp region 20 then acts, so that in the lower position P1 "the ramp 20 has returned the individual plunger P1 (this has been done in parallel by the groove 14 with the same height profile for the plunger P2) without This means that at the end of the actuating movement (insofar as shown in the development by the lower portion of the sub-figures in Fig. 1) each of the individual plungers are in their retracted starting position and for renewed operations can be properly controlled.
- FIG. 1 corresponds to the representation of the position 2 in FIG. 2 corresponding to the partial representations (c) and (d) and associated groove profile curves along the sections YY and XX (FIG. 2, with respect to FIG 1, in the plane of the figure shows a direction of movement 0 ° to 360 ° in the upward direction, inversely to the representation of FIG. 1).
- the alternative orientation of the individual plungers P1, P2 relative to the assembly 10, marked as position 1 in FIG. 2 shows that here as well (usually not meaningful, but possible in an error case) actuation of the plunger P2 to no disturbance or damage In fact, if a plunger actuation of P2 positioned outside of the groove 12 in FIG.
- FIGS. 3 to 5 show the second solution aspect of the invention by means of a second embodiment of the invention.
- the same reference numerals clarify the same or equivalent components, wherein the embodiment of FIGS. 3 to 5 differs from the embodiment of FIGS. 1, 2 in that in FIGS. 3 to 5 the pair of individual plungers P1, P2 is mechanically coupled to one another, while in the first embodiment, these are independently driven.
- Mit Conversely 28 and permanent magnet 30 are in turn axially in response to the energization of a coil unit 32 movable anchor components which perform in an otherwise known manner an axial lifting movement; the reference numeral 34 shows a (again otherwise known) magnetically conductive bracket section for producing a magnetic flux circuit causing the drive. 7 would correspondingly and as a basis for the operating behavior of FIGS. 3 to 5 bring about a simultaneous movement of both individual plungers P1, P2.
- the second exemplary embodiment of FIGS. 3-5 differs from the first exemplary embodiment in that the lifting profile assembly (shifting gate) 10 has no ramp outside the control groove 12, which itself is profiled like the control groove 12 of the first exemplary embodiment. but has a radial (cylindrical) outer surface whose height corresponds to the deepest groove depth 16.
- the lifting profile assembly (shifting gate) 10 has no ramp outside the control groove 12, which itself is profiled like the control groove 12 of the first exemplary embodiment. but has a radial (cylindrical) outer surface whose height corresponds to the deepest groove depth 16.
- the groove 12 each laterally delimiting wall portion 22 ensures that on the leadership of the running in the groove plunger, a standing outside the groove plunger (eg P1 in Fig. 3 and P2 in FIG Fig. 4) can not inadvertently slide into the groove, if an unintentional or faulty drive this ram takes place.
- the position 1 shown therein corresponds to the representations of FIG. 4, and the position 2 shown in FIG Sub-figures (c) and (d) with section YY and XX of Figure 3.
- FIG. 6 shows a further development of the second as a third embodiment Embodiment and follows the structure of Fig. 5; in contrast to FIG. 5, however, the groove courses 12 along the circumference 0 ° to 360 ° do not contain a simple S- or Z-shaped course in the unwinding (such as in FIGS. 5 (a) to 5 (d)). rather, a double S- or Z-shape is formed along the circumference, so that the course in the embodiment of FIG. 6, the movement of the second embodiment (Fig. 3 to Fig.
- FIG. 8 shows, as an additional, generic development and further development of the first exemplary embodiment of FIGS. 1, 2, a possibility of forming the ramp 20 formed outside the control groove not as a surface increasing along the circumferential direction but as transverse to the circumferential direction (FIG. and thus in the axial direction) extending slope 21, as Fig. 8 illustrates in the sectional view AA to the middle plan view. It becomes clear that with a slide of the plunger P1 lying outside the groove along this axially beveled ramp 21, the entrainment or movement behavior equivalent to the embodiment of FIGS. 1, 2 can be achieved.
- the present invention is not limited to the embodiments shown, but is also suitable for any other variants and embodiments of the camshaft adjusting device.
- any combinations and subcombinations of the features discernible from the present disclosure should also be deemed to belong to the present invention and accordingly disclosed.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Transmission Devices (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014108927.8A DE102014108927A1 (en) | 2014-06-25 | 2014-06-25 | Device for adjusting the camshaft of an internal combustion engine |
PCT/EP2015/064427 WO2015197777A1 (en) | 2014-06-25 | 2015-06-25 | Device for adjusting a camshaft of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3161282A1 true EP3161282A1 (en) | 2017-05-03 |
EP3161282B1 EP3161282B1 (en) | 2019-05-15 |
Family
ID=53673060
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15738599.8A Active EP3161282B1 (en) | 2014-06-25 | 2015-06-25 | Cam shifting arrangement for internal combustion engine |
Country Status (5)
Country | Link |
---|---|
US (1) | US10704432B2 (en) |
EP (1) | EP3161282B1 (en) |
CN (1) | CN106460595B (en) |
DE (1) | DE102014108927A1 (en) |
WO (1) | WO2015197777A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6617737B2 (en) * | 2017-03-03 | 2019-12-11 | トヨタ自動車株式会社 | Internal combustion engine system |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19611641C1 (en) | 1996-03-25 | 1997-06-05 | Porsche Ag | Valve operating cam drive for combustion engines |
DE102007028600B4 (en) | 2007-06-19 | 2011-06-22 | ETO MAGNETIC GmbH, 78333 | Electromagnetic actuator |
DE102008060166A1 (en) * | 2008-11-27 | 2010-06-02 | Dr.Ing.H.C.F.Porsche Aktiengesellschaft | Valve train for gas shuttle valve of internal combustion engine, comprises cam shaft, which is swivelingly stored in housing of internal combustion engine |
DE102011004912A1 (en) * | 2011-03-01 | 2012-09-06 | Schaeffler Technologies Gmbh & Co. Kg | Sliding cam system for reciprocating internal combustion engines for displacement variation of gas exchange valves, is provided with sliding cams which are arranged on main shaft |
DE102011001125B4 (en) | 2011-03-07 | 2023-06-01 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Valve train for an internal combustion engine |
DE102011075537A1 (en) * | 2011-05-10 | 2012-11-15 | Schaeffler Technologies AG & Co. KG | Reciprocating internal combustion engine with camshaft adjusting device |
DE102012112482A1 (en) * | 2012-12-18 | 2014-06-18 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Method for operating internal combustion engine of motor vehicle, involves performing axial displacement of respective slide cam dependent on axial displacement direction and/or dependent on valve clearance outside of cam base circle |
-
2014
- 2014-06-25 DE DE102014108927.8A patent/DE102014108927A1/en not_active Withdrawn
-
2015
- 2015-06-25 EP EP15738599.8A patent/EP3161282B1/en active Active
- 2015-06-25 CN CN201580034333.9A patent/CN106460595B/en active Active
- 2015-06-25 WO PCT/EP2015/064427 patent/WO2015197777A1/en active Application Filing
- 2015-06-25 US US15/322,210 patent/US10704432B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
WO2015197777A1 (en) | 2015-12-30 |
US20180119585A1 (en) | 2018-05-03 |
US10704432B2 (en) | 2020-07-07 |
DE102014108927A1 (en) | 2015-12-31 |
EP3161282B1 (en) | 2019-05-15 |
CN106460595A (en) | 2017-02-22 |
CN106460595B (en) | 2019-10-18 |
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