EP2013451B1 - Asservissement d'une soupape à mouvement alternatif dans un moteur à combustion interne - Google Patents

Asservissement d'une soupape à mouvement alternatif dans un moteur à combustion interne Download PDF

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Publication number
EP2013451B1
EP2013451B1 EP07727278.9A EP07727278A EP2013451B1 EP 2013451 B1 EP2013451 B1 EP 2013451B1 EP 07727278 A EP07727278 A EP 07727278A EP 2013451 B1 EP2013451 B1 EP 2013451B1
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EP
European Patent Office
Prior art keywords
cam
tappet
valve
closer
opener
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.)
Not-in-force
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EP07727278.9A
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German (de)
English (en)
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EP2013451A1 (fr
Inventor
Harald Elendt
Andreas Nendel
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2013451A1 publication Critical patent/EP2013451A1/fr
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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
    • F01L1/30—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 closer cam, which ⁇ ffnernocken the lift valve via a mounted in a longitudinal guide of the engine and a Abgriffs Type for ⁇ ffnernocken having ⁇ ffnerst Schemeel operated in the opening direction and which closing cam the lift valve is actuated in the closing direction via a rocker arm mounted in the internal combustion engine.
  • Such a forced control which is also referred to as desmodromic valve control, goes out of the generic DE 35 39 812 A1 out.
  • 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 sweeping design of the rocker arm contributes significantly to a limitation of the valve train stiffness, so that the achievement of an essential objective of such positive controls, namely the high speed resistance of the valve train, at least in question.
  • 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.
  • a push rod mounted on both sides is arranged between one or both arms and the associated plunger bottoms.
  • rocker arm may be formed cross-shaped and supported with a third arm and with a fourth arm on stationary mounted in the engine pivot bearings, of which preferably a pivot bearing is provided with a hydraulic clearance compensation.
  • pivot bearings for example, as known in the art, used for the storage of rocker arms supporting elements with or without hydraulic 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 plunger are formed as equal parts, the potential of low manufacturing costs of the positive control can be opened up.
  • valve clearance compensation between the closed lift valve and the ⁇ ffnernocken take place 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 Ventil mecanicinstellin with a given thickness.
  • opener side basically a hydraulic valve clearance compensation can be provided
  • the mechanical clearance compensation in the form of Ventilassiinstellhunt prevents unfavorable mutual influence of hydraulic valve clearance compensation elements, which are provided both opener side and closing side. This influence can lead to malfunctions of the internal combustion engine as a result of a no longer completely closing globe valve on the one hand or even destruction of the engine as a result of a tearing valve due to high valve seat forces on the other hand.
  • 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 starting from the closing cam tension of the valvetrain 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 lash adjuster 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 camshaft is part of a camshaft system known per se with at least one actuator axially displaceable cam piece, the at least two juxtaposed ⁇ ffnernocken and at least two juxtaposed closing cam each with different cam elevations and / or phases at the same base circle diameters having.
  • the inventive combination of the present positive control with the known camshaft system makes it possible to significantly mitigate the rigidly required in rigid cam surveys compromise in terms of partially conflicting engine targets torque, power, fuel consumption and exhaust emissions. This is particularly beneficial for the positive control present here with the considerable potential for increasing the speed of the internal combustion engine, since in this case no speed-limiting influences exist on the part of a valve spring acting on the gas exchange valve in the closing direction.
  • 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.
  • a timing characteristic is contrary to the residual gas-sensitive idling and idle operating points of the internal combustion engine, since the focus here on short valve opening times and small valve overlaps at moderate valve strokes to produce lowest exhaust emissions with the best possible concentricity quality of the engine.
  • a first ⁇ ffnernocken and the associated closer cam to meet the engine requirements for idling and part load operating points of the engine could be adjusted while a second ⁇ ffnernocken and a second associated Schelleernocken in terms of a full torque curve with the greatest possible performance Internal combustion engine can be tuned.
  • 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 independently controllable actuators are alternately radially retractable into the associated displacement grooves. Accordingly, each shift direction of the cam piece is associated with a separate slide groove and the associated actuator, which dips to initiate the sliding operation in the sliding groove, axially displaces the cam piece and finally returns to its original position, while the cam piece can be locked in its new axial position.
  • FIG. 1 The structure and operation of a first embodiment of a positive control 1 a of an internal combustion engine 2 according to the invention is in the Figures 1 and 2 illustrated by a lift valve 3a and a portion of a cooperating with the lift valve 3a camshaft 4a with a rigidly arranged thereon ⁇ ffnernocken 5a and a rigidly arranged thereon cam 6a.
  • ⁇ ffnerst Schemeel 8a formed here as a roller bearing roller 9
  • 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 plunger 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.
  • the lift 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 Schwinernockens 6a follows.
  • the lifting valve 3a is actuated in the closing direction by the then increasing again stroke of the closing cam 6a the rocker arm 19a pivoted about the closer plunger 12a in the opposite direction, so that the ⁇ ffnerst Schemeel 8a followed by the lifting valve 3a then the decreasing stroke of the ⁇ ffnernockens 5a ,
  • 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.
  • FIG. 3 a second embodiment of a positive control 1b according to the invention is disclosed, which with both a rigid camshaft according to the Figures 1 and 2 as well as with a variably shaped camshaft 4b as part of a known per se and explained later camshaft system 30 can be combined.
  • a longitudinally movably mounted in a hollow cylindrical recess 31 of the engine 2 insert part 32 is provided, in which a longitudinal guide 7b for a ⁇ ffnerst Congressel 8b and an adjacent further longitudinal guide 11 b for a Schlie-ßst Congressel 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 here formed with two arms and is on the both sides hingedly mounted push rods 20 in operative connection with the ⁇ ffnerst Congressel 8b and the closer plunger 12b.
  • the Abgriffs simulation 10 of the ⁇ ffnerst formulateels 8b and the Abgriffs Chemistry 14 of the Schschreiberst formulateels 12b as the Ventiltriebsreib reducing roller bearing rollers 9 and 13 are formed, wherein the ⁇ ffnerstsammlungel 8b and the closer plunger 12b respectively via a here designed as a radially protruding needle body anti-rotation 34 relative to the Insert 32 are positioned radially.
  • the structural design of the ⁇ ffnerst Congressels 8b and the closer plunger 12b is shown in more detail in the sectional view according to FIG. 4 seen.
  • 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.
  • the lash adjuster 45 is here as plug-in construction and functional unit, as used in conventional bucket tappet, tilt or rocker arm valve drives, designed and provides analogous to the Figures 1 and 2 relevant embodiments with the lift valve 3b closed for the fact that the insert member 32 is subjected to a force 4b together with the attached rocker arm 19b in the direction of the camshaft shown here simplified.
  • An additional increase in the contact force with respect to the valve seat 29 may be required in particular if the force of the spring means 46 is limited to the space available for the spring means 46 or if the lift valve 3b in the case of a supercharged internal combustion engine by comparatively high pressures Intake or exhaust duct in the opening direction is subjected to force.
  • 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 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 shift groove 58 and 59 are each circumferentially formed, which is mirror-symmetrical to the other displacement groove 59 and 58, respectively.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (16)

  1. Commande desmodromique (1a, 1b) pour au moins une soupape à levée (3a, 3b) d'un moteur à combustion interne (2), comprenant un arbre à cames (4a, 4b) pourvu d'au moins une came d'ouverture (5a, 5b, 5c) et d'au moins une came de fermeture (6a, 6b, 6c), laquelle came d'ouverture (5a, 5b, 5c) actionne la soupape à levée (3a, 3b) dans le sens d'ouverture par le biais d'un poussoir d'ouverture (8a, 8b) monté dans un guide longitudinal (7a, 7b) du moteur à combustion interne (2) et comprenant une surface d'engagement (10) pour la came d'ouverture (5a, 5b, 5c), et laquelle came de fermeture (6a, 6b, 6c) actionne la soupape à levée (3a, 3b) dans le sens de fermeture par le biais d'un culbuteur (19a, 19b) monté dans le moteur à combustion interne (2), caractérisée en ce qu'il est prévu un guide longitudinal supplémentaire (11a, 11b) s'étendant de manière adjacente au guide longitudinal (7a, 7b), dans lequel guide longitudinal supplémentaire (11a, 11b) est monté un poussoir de fermeture (12a, 12b) disposé entre la came de fermeture (6a, 6b, 6c) et le culbuteur (19a, 19b) et pourvu d'une surface d'engagement (14) pour la came de fermeture (6a, 6b, 6c).
  2. Commande desmodromique (1a, 1b) selon la revendication 1, caractérisée en ce que le guide longitudinal (7a, 7b) et le guide longitudinal supplémentaire (11a, 11b) s'étendent avec leurs axes parallèles l'un à l'autre et de préférence avec leurs axes parallèles à celui de la soupape à levée (3a, 3b).
  3. Commande desmodromique (1a, 1b) selon la revendication 1, caractérisée en ce qu'un premier bras (21) du culbuteur (19a, 19b) coopère avec un fond de poussoir (22a, 22b), éloigné de la came, du poussoir d'ouverture (8a, 8b) et en ce qu'un deuxième bras (23) du culbuteur (19a, 19b) coopère avec un fond de poussoir (24), éloigné de la came, du poussoir de fermeture (12a, 12b), le poussoir d'ouverture (8a, 8b) étant, en vue de la transmission à la soupape à levée (3a, 3b) de forces de traction agissant dans le sens de fermeture, relié à force, par complémentarité de formes ou par liaison de matière à son extrémité de tige (18a, 18b).
  4. Commande desmodromique (1a, 1b) selon la revendication 3, caractérisée en ce qu'une bielle de poussée (20) respective montée de manière articulée des deux côtés est disposée entre un bras ou les deux bras (21, 23) et le fond de poussoir associé (22a, 22b, 24).
  5. Commande desmodromique (1a) selon la revendication 3, caractérisée en ce que le culbuteur (19a) est réalisé en forme de croix et s'appuie par un troisième bras (25) ainsi que par un quatrième bras (26) sur des paliers de pivotement (27, 28) montés de manière fixe dans le moteur à combustion interne (2), parmi lesquels de préférence un palier de pivotement (27) est pourvu d'une compensation de jeu hydraulique.
  6. Commande desmodromique (1b) selon la revendication 3, caractérisée en ce que le poussoir d'ouverture (8b) comporte une partie extérieure (35) en forme de pot pourvue d'un corps de poussoir (36) servant au montage dans le guide longitudinal (7b) et du fond de poussoir (22b) ainsi qu'une partie intérieure (37) reçue dans la partie extérieure (35), sur laquelle partie intérieure sont disposés la surface d'engagement (10) pour la came d'ouverture (5b, 5c) et un appui de tige de soupape (39) s'étendant sur une partie de fond (38), éloignée de la came, de la partie intérieure (37), et, dans l'extrémité de tige (18b) de la soupape à levée (3b) pénétrant dans la partie extérieure (35) à travers un évidement du fond de poussoir (22b), des forces de pression agissant dans le sens d'ouverture étant appliquées du côté frontal par le biais de l'appui de tige de soupape (39) et des forces de traction agissant dans le sens de fermeture étant appliquées du côté périphérique par le biais d'un dispositif de transmission (41) qui s'étend entre le fond de poussoir (22b) et l'extrémité de tige (18b).
  7. Commande desmodromique (1b) selon la revendication 6, caractérisée en ce que le poussoir d'ouverture (8b) et le poussoir de fermeture (12b) sont réalisés sous forme de pièces identiques.
  8. Commande desmodromique (1b) selon la revendication 6, caractérisée en ce que le dispositif de transmission (41) comporte une bague (42) s'appuyant contre le fond de poussoir (22b) et comprenant un cône intérieur s'ouvrant en direction de l'arbre à cames (4b) et des cales de serrage (43) qui viennent en prise dans une ou plusieurs entailles (44) formées sur l'extrémité de tige (18b) et forment sur leur surface d'enveloppe extérieure un cône extérieur complémentaire au cône intérieur.
  9. Commande desmodromique (1b) selon la revendication 6, caractérisée en ce que l'appui de tige de soupape (39) est réalisé sur une rondelle de rattrapage de jeu de soupape (40) d'épaisseur définie disposée entre l'extrémité de tige (18b) et la partie de fond (38), éloignée de la came, de la partie intérieure (37).
  10. Commande desmodromique (1b) selon la revendication 1, caractérisée en ce qu'il est prévu une partie d'insertion (32) montée dans le moteur à combustion interne (2), dans laquelle partie d'insertion (32) le guide longitudinal (7b) et le guide longitudinal supplémentaire (11b) s'étendent et un axe (33) supportant le culbuteur (19b) est fixé.
  11. Commande desmodromique (1b) selon la revendication 10, caractérisée en ce que la partie d'insertion (32) est montée de manière mobile longitudinalement dans un évidement (31) cylindrique creux du moteur à combustion interne (2), un élément de compensation de jeu hydraulique (45) étant disposé entre une base (47) de l'évidement (31) et un fond (48) de la partie d'insertion (32) tourné vers la base (47), lequel élément de compensation de jeu (45) soumet la partie d'insertion (32) à une force dans la direction de l'arbre à cames (4b).
  12. Commande desmodromique (1b) selon la revendication 11, caractérisée en ce que la came de fermeture (6b) présente une course supplémentaire (50) se superposant à sa phase de cercle de base (49) pour augmenter la force d'appui de soupape de la soupape à levée (3b).
  13. Commande desmodromique (1b) selon la revendication 11, caractérisée en ce que la partie d'insertion (32) est en outre sollicitée par une force dans la direction de l'arbre à cames (4b) par un moyen de ressort (46) monté en parallèle à l'élément de compensation de jeu (45) et serré entre la base (47) de l'évidement (31) et le fond (48) de la partie d'insertion (32).
  14. Commande desmodromique (1a, 1b) selon la revendication 1, caractérisée en ce que la surface d'engagement (10) du poussoir d'ouverture (8a, 8b) et/ou la surface d'engagement (14) du poussoir de fermeture (12a, 12b) sont réalisées sous forme de rouleaux (9, 13) rotatifs et montés sélectivement sur roulement.
  15. Commande desmodromique (1b) selon la revendication 1, caractérisée en ce que l'arbre à cames (4b) fait partie d'un système de commutation de cames (30) connu en soi comprenant au moins une pièce à cames (52) pouvant être déplacée axialement par un dispositif de réglage (53), laquelle pièce à cames comprend au moins deux cames d'ouverture (5b, 5c) juxtaposées et au moins deux cames de fermeture (6b, 6c) juxtaposées présentant respectivement des levées et/ou phases de came différentes les unes des autres pour un même rayon de cercle de base.
  16. Commande desmodromique (1b) selon la revendication 15, caractérisée en ce que le dispositif de réglage (53) comporte des actionneurs (54, 55) disposés de manière fixe dans le moteur à combustion interne (2) ainsi que des parties cylindriques (56, 57) s'étendant aux deux extrémités de la pièce à cames (52), dans lesquelles parties (56, 57) est formée respectivement du côté périphérique une rainure de déplacement hélicoïdale (58, 59) qui est réalisée en symétrie spéculaire par rapport à l'autre rainure de déplacement (59, 58) de la pièce à cames (52), les actionneurs (54, 55) pouvant être commandés indépendamment l'un de l'autre pouvant être insérés radialement en alternance dans les rainures de déplacement associées (58, 59).
EP07727278.9A 2006-04-21 2007-03-23 Asservissement d'une soupape à mouvement alternatif dans un moteur à combustion interne Not-in-force EP2013451B1 (fr)

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 (fr) 2006-04-21 2007-03-23 Asservissement d'une soupape à mouvement alternatif dans un moteur à combustion interne

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EP2013451A1 EP2013451A1 (fr) 2009-01-14
EP2013451B1 true EP2013451B1 (fr) 2013-09-18

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DE (1) DE102006018599A1 (fr)
WO (1) WO2007122052A1 (fr)

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US11242639B2 (en) * 2011-01-17 2022-02-08 Samsung Electronics Co., Ltd. Washing machine
US11649579B2 (en) 2011-01-17 2023-05-16 Samsung Electronics Co., Ltd. Washing machine
US12152332B2 (en) 2011-01-17 2024-11-26 Samsung Electronics Co., Ltd. Washing machine

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DE102006018599A1 (de) 2007-10-25

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