EP2013451A1 - Zwangsteuerung für ein hubventil einer brennkraftmaschine - Google Patents
Zwangsteuerung für ein hubventil einer brennkraftmaschineInfo
- Publication number
- EP2013451A1 EP2013451A1 EP07727278A EP07727278A EP2013451A1 EP 2013451 A1 EP2013451 A1 EP 2013451A1 EP 07727278 A EP07727278 A EP 07727278A EP 07727278 A EP07727278 A EP 07727278A EP 2013451 A1 EP2013451 A1 EP 2013451A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cam
- valve
- plunger
- internal combustion
- combustion engine
- 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
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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/30—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of positively opened and closed valves, i.e. desmodromic valves
Definitions
- the invention relates to a positive control for at least one lift valve of an internal combustion engine, with a camshaft having at least one ⁇ ffnernocken and at least one NO cam, which ⁇ ffnernocken the lift valve via a mounted in a longitudinal guide of the engine and a tap area for the ⁇ ffnernocken having ⁇ ffnerst Schemeel operated in the opening direction and which closing cam actuates the lifting valve via a rocker arm mounted in the internal combustion engine in the closing direction.
- Such a forced control which is also referred to as desmodromic valve control, is apparent from the generic DE 35 39 812 A1.
- the rocker arm which actuates the lifting valve in the closing direction is, guided by the camshaft, guided in an arc around the longitudinal guide of the opener tappet and accordingly designed to be wide.
- the associated lack of rigidity of the rocker arm can then be compensated only by the illustrated material and thus mass and inertia-intensive design or possibly by the use of material-saving, but relatively expensive high-strength materials to produce sufficient structural strength of the rocker arm.
- the invention is therefore based on the object to avoid these disadvantages and thus to provide a positive control whose stiffness also allows operation of the internal combustion engine at very high speeds and which is also characterized by a compact and space-saving design.
- an adjacent to the longitudinal guide extending further longitudinal guide is provided in which further longitudinal guide is arranged between the closing cam and the rocker arm closer tappet is mounted with a tap surface for the closing cam.
- the adjacent arrangement of the longitudinal guides with the opener plunger and the closer plunger allows a compact design of the positive control and in particular also of the rocker arm in favor of the greatest possible valve train stiffness with a comparatively small space requirement.
- This is according to a preferred embodiment of the invention, especially when the longitudinal guide and the further longitudinal guide axially parallel to each other and preferably axially parallel to the lift valve.
- a first arm of the rocker arm with a cam-distant plunger bottom of the ⁇ ffnerst Formulaels and a second arm of the rocker arm cooperate with a cam-distant plunger bottom of the closer plunger, wherein the ⁇ ffnerst Congressel for transmitting acting in the closing direction tensile forces on the lift valve force, form or cohesively with the shaft end connected is.
- this embodiment offers extensive freedom in terms of the invention kinematic interaction of the rocker arm with the opener and closer tappets.
- the decoupled from the rocker arm tension-pressure connection of the ⁇ ffnerst Schemeels with the lifting valve allows an articulation of the Kipphebelarme as far as possible spaced contact points of the ⁇ ffner- and the closer plunger corresponding to large lever arms to keep the leverage despite the compact design of the positive control as low as possible.
- a push rod mounted on both sides is arranged between one or both arms and the associated plunger bottoms.
- rocker arm can be designed in the shape of a cross and be supported with a third arm and with a fourth arm on pivot bearings mounted stationarily in the internal combustion engine, of which a pivot bearing is preferably provided with a hydraulic clearance compensation.
- pivot bearings can be used, for example, as support elements known to the person skilled in the art and used for the storage of rocker arms with or without hydroforming. Raulischen play compensation be formed.
- the hydraulic clearance compensation serves in the present case to compensate for the component tolerances and wear as well as by different thermal expansions game between the closed globe valve and the closing cam.
- the ⁇ ffnerstumbleel a pot-like outer part with a serving for storage in the longitudinal guide plunger shirt and the plunger bottom and an outer part received in the inner part, on which the Abgriffs simulation for the ⁇ ffnernocken and arranged on a cam-distal bottom portion of the inner part valve stem support are arranged include.
- pressure forces acting in the opening direction on the front side over the Ventilschaftauflage and acting in the closing direction tensile forces circumferentially in the projecting through a recess of the plunger bottom into the outer part shaft end of the lift valve via a transmission device which extends between the plunger bottom and the shaft end initiated.
- Such a trained ⁇ ffnerst Schemeel forms the basis for a mounting-friendly and space-saving train-duck connection of the ⁇ ffnerst formulateels with the globe valve. Moreover, in the event that such an opener tappet and the closer tappet are designed as equal parts, the potential of low production costs of the positive control can be opened up.
- a structurally simple, space-saving and cost-effective Ven- tilspielaus manifest effected between the closed lift valve and the ⁇ ffnernocken characterized in that the valve stem support is formed on a between the shaft end and the cam-distal bottom portion of the inner part Ventilindustrialinstellhunt with a given thickness.
- the mechanical clearance compensation in the form of the valve clearance adjustment disc prevents an unfavorable mutual influence of hydraulic valve clearance compensation elements, which are provided on both the opener side and the closing side. This influence can lead to malfunctions of the internal combustion engine as a result of a stroke valve which no longer closes completely on the one hand, or even to destruction of the internal combustion engine as a result of a disruptive lift valve due to valve seat forces that are too high.
- an insert mounted in the internal combustion engine in which the longitudinal guide and the further longitudinal guide extend, and an axis supporting the rocker arm is fastened.
- the insert member is longitudinally movably mounted in a hollow cylindrical recess of the internal combustion engine, wherein between a base of the recess and a bottom of the insert facing the ground, a hydraulic clearance compensation element is arranged, which forces the insert part in the direction of the camshaft.
- valve clearance compensation elements as they are known as a housing, a pressure piston, a compression spring and a check valve comprehensive assembly unit of conventional bucket tappet or rocker arm valve drives.
- valve seat force of the closed lift valve with respect to the valve seat generated in conventional valve controls is usually generated in forced controls by a defined and the clamping cam outgoing tension of the valve train members by the closing cam pulls the lift valve via the closer plunger and the rocker arm in the valve seat.
- the clearance compensation element clamped between the insert part and the internal combustion engine which has to absorb the support forces generated, it should be noted that the clearance compensation element is in the state of load freedom required for the compensation process for a sufficiently long period of time.
- the closer cam in development of the invention should have a Grund Vietnamese superimposed additional lift to increase the valve seat force of the lift valve.
- the beginning of such a supplementary stroke is expediently to be positioned on the base circle such that the angular range between the currently closed lifting valve and the additional stroke corresponds to a time period which is always sufficient for the balancing phase of the clearance compensation element.
- valve seat force can also be increased by the fact that the insert part is additionally subjected to a force in the direction of the camshaft by a spring means connected in parallel to the play compensation element and clamped between the bottom of the recess and the bottom of the insert part.
- the increase in valve seat force can be expedient or necessary, in particular in supercharged internal combustion engines, since increased gas pressures act in the opening direction of the lift valve both in the intake and in the exhaust gas duct.
- the Abgriffs Colour the ⁇ ffnerst Formulaels and / or the Abgriffs Colour of the closer plunger are designed to be rotatable and optionally roller bearings rollers.
- the camshaft is part of a known camshaft system with at least one axially displaceable cam actuator cam piece, the at least two juxtaposed ⁇ ffnernocken and at least two adjacently arranged closer cam with mutually different cam lobes and / or phases having the same base circle diameters.
- valve timing of a positive control to produce the highest possible power to the occurring at very high speeds gas-dynamic effects during the charge change may be adjusted by the valve timing lead to a long valve duration at high maximum stroke and a large overlap between the exhaust and intake valves.
- the adjusting device may comprise fixedly arranged in the internal combustion engine actuators and at both ends of the cam piece extending cylindrical sections in which each circumferentially a helical Verschiebenut that is mirror-symmetrical to the other displacement groove of the cam piece is formed, wherein the actuators which can be controlled independently of one another are alternately radially retractable into the associated displacement grooves. Accordingly, each shift direction of the cam piece is associated with its own shift groove and the associated actuator, which dips into the sliding groove for initiating the sliding operation, axially displaces the cam piece and finally returns to its initial position, while the cam piece can be locked in its new axial position.
- Figure 1 shows a first embodiment of an inventive
- Figure 2 shows the positive control of Figure 1 in a rotated by 90 °
- Figure 3 is a perspective view of a second embodiment of a positive control according to the invention in optional combination with a cam switching system;
- Figure 4 shows a detail of the positive control according to Figure 3 in an enlarged view;
- FIG. 5 shows an insert according to FIG. 4 in an enlarged longitudinal section.
- FIG. 1 The structure and operation of a first embodiment of a positive control according to the invention 1 a of an internal combustion engine 2 is in Figures 1 and 2 based on a lift valve 3a and a portion of a cooperating with the lifting valve 3a camshaft 4a with a rigidly arranged thereon cam 5a and a rigidly arranged thereon Closing cam 6a illustrated.
- Shown is a mounted in a longitudinal guide 7a of the internal combustion engine 2 ⁇ ffnerst Schemeel 8a formed here as a roller bearing roller 9 tap surface 10 for the ⁇ ffnernocken 5a and adjacent to the longitudinal guide 7a extending further longitudinal guide 11a of the engine 2 mounted closer plunger 12a with a also as roller bearing roller 13 trained tap area 14 for the make cam 6a.
- the ⁇ ffnerst Congressel 8a comprises a cam-side primary plunger 15 and a valve-side secondary plunger 16, which are fixedly connected to one another by a roller 17 which supports the roller 9.
- the secondary tappet 16 is non-positively connected to the stem end 18a for transmitting tensile forces acting in the closing direction on the lift valve 3a via a longitudinal compression bandage.
- the ⁇ ffnerst Congressel 8a and the closer plunger 12a are connected via a mounted in the engine 2 rocker arm 19a and push rods 20, each between a first arm 21 of the rocker arm 19a and a cam-off plunger bottom 22a of the ⁇ ffnerst formulateels 8a and between a second arm 23 of the rocker arm 19a and a cam-distant plunger bottom 24 of the closer plunger 12a are articulated on both sides, in mutual operative connection.
- the rocker arm 19a is formed in a cross shape and is supported by a third arm 25 and a fourth arm 26 on pivot bearings 27 and 28 which are mounted stationary in the internal combustion engine 2, wherein the pivot bearing 27 is provided with a hydraulic clearance compensation.
- a pivot bearing 27 is known in the art as such in particular of conventional finger lever valve trains with hydraulic support elements.
- the pivot bearing 27 can only compensate for mechanical play that occurs with the lift valve 3a closed between the closing cam 6a and a valve seat 29.
- an adjustment of the mechanical clearance between the ⁇ ffnernocken 5a and the roller 9 of the ⁇ ffnerst Formulaels 8a in this embodiment can be controlled via the insertion depth of the pressed into the secondary plunger 16 the lifting valve 3a.
- the lifting valve 3a is actuated via the ⁇ ffnerst Schemeel 8a in the opening direction, while the closer plunger 12a is driven by the pivoting rocker arm 19a and the decreasing stroke of the Schinneernockens 6a follows.
- the lifting valve 3a is actuated in the closing direction, in that the then increasing stroke of the closing cam 6a pivots the tilting lever 19a over the closer plunger 12a in the opposite direction, so that the opener plunger 8a, taking along the lifting valve 3a, reduces the then decreasing stroke of the ⁇ ffnernockens 5a follows.
- a game created in the component chain between the closer cam 6a and the valve seat 29 by sinking of the loaded during this cycle game pivot bearing 27 game can be compensated in the subsequent phase in which the lift valve 3a is closed by hydraulic adjustment of the pivot bearing 27. This is done on the one hand by contact of the closer plunger 12a to the closer cam 6a and on the other hand by applying force to the normally closed stossis 8a in the direction of ⁇ ffnernockens 5a to produce a sealing contact force between the lift valve 3a and the valve seat 29th
- a second embodiment of a positive control 1 b according to the invention is disclosed, which can be combined both with a rigid camshaft according to Figures 1 and 2 and with a variably shaped camshaft 4 b as part of a known per se and later explained camshaft system 30.
- an insertion part 32 which is longitudinally movably mounted in a hollow-cylindrical recess 31 of the internal combustion engine 2, is provided, in which a longitudinal guide 7b for an opener tappet 8b and an adjacent further longitudinal guide 11b for a closer tappet 12b.
- rocker arm 19b centrally supporting axis 33 is fixed, which extends in a direction orthogonal to the longitudinal axis of the insert member 32 level.
- the rocker arm 19b is of a double-arm design and is in operative connection with the opener tappet 8b and the closer tappet 12b via the push rods 20 articulated on both sides.
- the Abgriffs simulation 10 of the ⁇ ffnerst formulateels 8b and the Abgriffs Chemistry 14 of the closer plunger 12b as the Ventiltriebsreib reducing roller bearing rollers 9 and 13 are formed, wherein the ⁇ ffsterst Schemeel 8b and the closer plunger 12b each formed on a here as radially projecting needle body anti-rotation 34th are positioned radially relative to the insert 32.
- the structural design of the ⁇ ffnerst Congressels 8b and the closer plunger 12b is shown in more detail from the sectional view of Figure 4.
- the ⁇ ffnerst Congressel 8b includes a cup-shaped outer part 35, which has a serving for storage in the longitudinal guide 7b plunger shirt 36 and a push rod 20 hingedly mounted plunger bottom 22b, and an outer part 35 recorded inner part 37, in which the axle-mounted roller 9 and one on a Cam-distal bottom portion 38 extending valve stem support 39 are arranged.
- valve stem support 39 for adjusting the mechanical clearance between a ⁇ ffnernocken 5 b and the end face of a shaft end 18 b of a lift valve 3b on a Ventilassiinstellin 40 with a given thickness educated.
- a form-fitting transmission device 41 is provided between the shaft end 18b and the plunger bottom 22b.
- the transmission device 41 comprises a ring 42 which is supported on the inside of the plunger 22b and has an inner cone which opens in the direction of the camshaft 4b, and clamping wedges 43 which form an outer cone complementary to the inner cone on its outer circumferential surface and engage in recesses 44 formed on the shaft end 18b.
- the ⁇ ffnerst Schemeel 8b and the closer plunger 12b are formed as equal parts and mounted in the insert 32 rotated by 180 ° to each other.
- a hydraulic lash adjuster 45 and a spring means 46 connected in parallel therewith provided between a bottom 47 of the recess 31 and a bottom 47 of the bottom 48 of the Insert 32 are arranged.
- the lash adjuster 45 is here as plug-in construction and functional unit, as used in conventional bucket tappet, tilt or rocker valve trains formed and provides analogous to the figures 1 and 2 relevant embodiments with a closed globe valve 3b that the insert 32 is force-loaded together with the rocker arm 19b fastened thereto in the direction of the camshaft 4b shown here in simplified form.
- the closing cam 6b has a supplementary stroke 50 overlapping its base circle phase 49, which additionally applies force to the already closed lifting valve 3b in the direction of the valve seat 29.
- the here greatly exaggerated illustrated and in practice limited to a few fractions of a millimeter 1925hub 50 is positioned on the base circle 49 so that the lash adjuster 45 a sufficiently long, pressure-free period between the just closed Hubven- til 3b and for the complete compensation process the additional stroke 50 is provided.
- the camshaft 4b comprises a toothed shaft 51 as well as a cam valve 52 which is non-rotatable but axially displaceable for one or more pairs and has an internal toothing complementary to the toothed shaft 51.
- On the cam piece 52 are each two immediately adjacent arranged ⁇ ffnernocken 5 b and 5 c and normally-closed cam 6 b and 6 c.
- the ⁇ ffnernocken 5 b, 5 c and the closer cam 6 b, 6 c each different cam lobes and / or phases.
- the pitch circle diameters of the opening cams 5b, 5c and the make cam 6b, 6c are respectively identical to allow unimpeded axial displacement of the cam piece 52 with the lift valves 3b closed.
- an adjusting device 53 is provided which comprises fixedly arranged in the internal combustion engine 2 actuators 54 and 55 and at both ends of the cam piece 52 extending cylindrical portions 56 and 57.
- a helical sliding groove 58 and 59 is provided on the circumference. shaped, which is mirror-symmetrical to the other displacement groove 59 and 58, respectively.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200610018599 DE102006018599A1 (de) | 2006-04-21 | 2006-04-21 | Zwangssteuerung für ein Hubventil einer Brennkraftmaschine |
PCT/EP2007/052804 WO2007122052A1 (de) | 2006-04-21 | 2007-03-23 | Zwangsteuerung für ein hubventil einer brennkraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2013451A1 true EP2013451A1 (de) | 2009-01-14 |
EP2013451B1 EP2013451B1 (de) | 2013-09-18 |
Family
ID=38123693
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07727278.9A Expired - Fee Related EP2013451B1 (de) | 2006-04-21 | 2007-03-23 | Zwangsteuerung für ein hubventil einer brennkraftmaschine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2013451B1 (de) |
DE (1) | DE102006018599A1 (de) |
WO (1) | WO2007122052A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20180044840A1 (en) * | 2011-01-17 | 2018-02-15 | Samsung Electronics Co., Ltd. | Washing machine |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016210315B4 (de) * | 2016-06-10 | 2018-03-08 | Hanon Systems | Vorrichtung zum Umwandeln einer Drehbewegung in eine Translationsbewegung eines Ventilelements |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1541069A (en) * | 1923-01-16 | 1925-06-09 | Galen H Peters | Four-cycle internal-combustion engine |
DE1060661B (de) * | 1957-03-16 | 1959-07-02 | Daimler Benz Ag | Ventilzwangssteuerung fuer Brennkraftmaschinen |
DE3706187C2 (de) * | 1987-02-26 | 1996-05-30 | Josef Austermann | Antriebsvorrichtung für ein vorzugsweise linear verstellbar geführtes Maschinenteil |
US5636602A (en) * | 1996-04-23 | 1997-06-10 | Caterpillar Inc. | Push-pull valve assembly for an engine cylinder |
-
2006
- 2006-04-21 DE DE200610018599 patent/DE102006018599A1/de not_active Withdrawn
-
2007
- 2007-03-23 WO PCT/EP2007/052804 patent/WO2007122052A1/de active Application Filing
- 2007-03-23 EP EP07727278.9A patent/EP2013451B1/de not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2007122052A1 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20180044840A1 (en) * | 2011-01-17 | 2018-02-15 | Samsung Electronics Co., Ltd. | Washing machine |
Also Published As
Publication number | Publication date |
---|---|
WO2007122052A1 (de) | 2007-11-01 |
EP2013451B1 (de) | 2013-09-18 |
DE102006018599A1 (de) | 2007-10-25 |
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