EP3351764B1 - Module hydraulique de commande d'un flux de liquide hydraulique d'une bielle pour un moteur à combustion interne à compression variable ainsi que bielle - Google Patents

Module hydraulique de commande d'un flux de liquide hydraulique d'une bielle pour un moteur à combustion interne à compression variable ainsi que bielle Download PDF

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Publication number
EP3351764B1
EP3351764B1 EP18150946.4A EP18150946A EP3351764B1 EP 3351764 B1 EP3351764 B1 EP 3351764B1 EP 18150946 A EP18150946 A EP 18150946A EP 3351764 B1 EP3351764 B1 EP 3351764B1
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EP
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Prior art keywords
hydraulic
hydraulic module
connecting rod
module according
working
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EP18150946.4A
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German (de)
English (en)
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EP3351764A1 (fr
Inventor
David Huber
Dietmar Schulze
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Eco Holding 1 GmbH
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Eco Holding 1 GmbH
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Priority claimed from DE102017121432.1A external-priority patent/DE102017121432A1/de
Application filed by Eco Holding 1 GmbH filed Critical Eco Holding 1 GmbH
Publication of EP3351764A1 publication Critical patent/EP3351764A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length

Definitions

  • the invention relates to a hydraulic module for controlling a hydraulic fluid flow of a connecting rod for an internal combustion engine with variable compression with an eccentric adjusting device for adjusting an effective connecting rod length and a connecting rod with such a hydraulic module.
  • a high compression ratio has a positive effect on the efficiency of the internal combustion engine.
  • compression ratio is generally understood the ratio of the entire cylinder space before compression to the remaining cylinder space after compression.
  • the compression ratio may only be selected so high that a so-called "knocking" of the internal combustion engine is avoided during full load operation.
  • the compression ratio could be selected with higher values without "knocking" occurring.
  • the important part load range of a Internal combustion engine can be improved if the compression ratio is variably adjustable. To adjust the compression ratio, for example, systems with variable connecting rod length are known.
  • a hydraulic module for a connecting rod for an internal combustion engine with variable compression with an eccentric adjustment device for adjusting an effective connecting rod length is for example from DE 10 2012 020 999 A1 as well as from the DE 10 2015 100 662 A1 known.
  • An object of the invention is to provide a hydraulic module for a connecting rod for a variable compression internal combustion engine with an eccentric adjusting device for adjusting an effective connecting rod length, which has a stable operating behavior.
  • Another object is to provide an improved connecting rod with such a hydraulic module.
  • a hydraulic module for controlling a hydraulic fluid flow of a connecting rod for a variable compression internal combustion engine with an eccentric adjusting device for adjusting an effective connecting rod length, wherein the eccentric adjusting device has at least a first cylinder and a second cylinder as hydraulic chambers and wherein both each have an inlet for supplying hydraulic fluid into the cylinder via a supply line and in each case a drain for discharging Hydraulic fluid are provided by the cylinders.
  • At least one movable piston in a housing is present, which is selectively displaceable in a first switching position or a second switching position, wherein in the first switching position, the flow of the second cylinder and in the second switching position, the outlet of the first cylinder is connected to the supply line.
  • the cylinders are each associated with a check valve, which allows a supply of hydraulic fluid into the cylinder and prevents discharge of hydraulic fluid from the cylinders. In this case, the cylinders are connected such that in the second switching position hydraulic fluid can be conducted from the first cylinder into the second cylinder via a channel in the hydraulic module.
  • the first cylinder may be connected as a hydraulic chamber of the adjustable connecting rod, for example the cylinder on a gas side (GKS) of the connecting rod, and at the second working connection, the second cylinder as a hydraulic chamber, for example the cylinder on the mass side ( MKS) of the connecting rod.
  • GKS gas side
  • MKS mass side
  • the corresponding chambers are commonly referred to as GKS chamber or MBS chamber.
  • the speed-dependent acceleration of the relatively long hydraulic fluid columns in the connecting rod of the engine oil used as hydraulic fluid can produce pressure differences. These can be both positive and negative, ie the hydraulic fluid columns can be accelerated to assist in draining and filling the hydraulic chambers of the cylinder of the connecting rod, but also to hinder this. Especially with a cylinder on the mass force side (MBS) of the connecting rod, this effect can have a negative effect.
  • the acceleration of the hydraulic fluid columns can cause that in front of and behind the MKS-side check valve no positive pressure difference longer forms, which causes hydraulic fluid can be nachgeschreibt in the MKS chamber.
  • the GKS chamber can direct the nachge felicitte in the position of low compression ( ⁇ low ) hydraulic fluid directly and unthrottled in the MKS chamber.
  • ⁇ low low compression
  • the hydraulic fluid which presses the GKS chamber in the direction of pressure in the MKS chamber by the connecting rod acting on the gas and mass forces has a substantially higher pressure than the hydraulic fluid pressure of the hydraulic supply in the bearing shell of the connecting rod.
  • the hydraulic fluid can be pressed from the GKS chamber into the MKS chamber.
  • the position stability on the rotation, or the stiffness of the connecting rod can increase.
  • the eccentric lever since the hydraulic fluid columns also have a certain flexibility and there is always a certain sinking of the support piston in the filled chamber. If the connecting rod completely returns to the end of the turn, it is called “stable in position". Nevertheless, with a change in the angle of the eccentric, or the lever assembly when resetting the respective support piston could hit the bottom of the chamber, which can affect the life of negative.
  • a pressure-loaded prestressed MBS hydraulic fluid column advantageously sinks less than a non-prestressed hydraulic fluid column. Less sinking means less lever movement, whereby the positional stability can be improved in the position ⁇ low .
  • the hydraulic module according to the invention represents an advantageous design solution for biasing the MBS chamber combined with a hydraulic switching valve and integrated check valves.
  • An advantageous feature is that the hydraulic fluid supply of the MBS chamber is deactivated or activated via a circumferential groove in a step piston of the hydraulic module can be.
  • frontal bores introduced into the housing of the hydraulic module are interconnected.
  • the hydraulic module according to the invention advantageously makes possible a hydraulic adjustment of a connecting rod via a quasi-static change of the hydraulic bearing shell pressure. Due to the change in the hydraulic pressure at the supply connection, the stepped piston is displaced in the axial direction counter to or in the direction of the spring force and thus opens or closes the GKS or MKS drain holes in order to initiate the eccentric adjustment.
  • the stepped piston is also provided with a circumferential groove, the already introduced in the housing holes in a defined switching position ⁇ low together and thus allows a bias of the MKS chamber.
  • band check valves are incorporated over the outer periphery of the hydraulic module, which simplify the overall system connecting rod.
  • the band elements can advantageously be provided with slots or holes to allow for a compact space, consistent functionality, and similar band rigidities sufficiently large flow cross-sections and to ensure high functionality in a small space. Conveniently, only 3 holes in Pleuelground stresses are necessary.
  • a locking ring can be introduced in combination with a sealing washer in the housing and the front side welded to the housing.
  • Another alternative hydraulic module could push two inclined planes in one of the two end positions of the stepped piston, which in turn deactivate or activate a hydraulic fluid connection.
  • a switching element may be provided in the piston for controlling the hydraulic fluid flow in the channel.
  • the hydraulic fluid supply of the MBS chamber can advantageously be deactivated or activated via the switching element in the piston.
  • the switching element connects the holes introduced in the housing in one of the two switching positions, preferably in the first switching position for low compression ⁇ low and thus allows a bias of the MKS chamber.
  • the switching element may be provided as a contour shape on the piston.
  • a circumferential groove in the stepped piston can also be a shape contour on the stepped piston be present, which opens a certain spring stroke slider or slider system opens when a certain stroke, which in turn allows a connection between the MKS chamber and GKS chamber.
  • a circumferential groove of the piston which forms part of the channel.
  • the circumferential groove can connect holes introduced in the housing in one of the two switch positions, preferably in the second switch position for low compression ⁇ low , and thus advantageously enable a pretensioning of the MBS chamber.
  • the hydraulic fluid flow in the channel via the circumferential groove by an axial displacement of the piston in the first or switchable second switching position.
  • the drain holes of the GKS chamber and the MBS chamber can be opened or closed in an advantageous manner, so as to initiate an eccentric adjustment.
  • the outlet of the first cylinder in the second switching position, can be connectable via the peripheral groove to the inlet of the second cylinder.
  • the connecting rod can advantageously be switched to a low compression position ⁇ low , in that the hydraulic fluid can be conducted unthrottled from the GKS chamber into the MBS chamber.
  • the outlet of the first cylinder in the second switching position, can be connectable to the circumferential groove via an end-side transverse bore and / or via an oblique bore.
  • end-side bores of the housing can be sealed by means of an annular sealing washer and / or a locking ring.
  • the check valves may be integrated into the hydraulic module.
  • the integration of the check valves in the hydraulic module results in a particularly compact design of the entire hydraulic system of the connecting rod, since only the combined supply and discharge of the hydraulic chambers and a supply line in Pleuelgrund stresses and / or connecting rod cover are provided.
  • At least one of the check valves as a closing element is a substantially annular Have band member which surrounds the housing at least partially on its circumference and is at least partially supported on the housing and by means of which in a closed position working ports are closed.
  • a so-called band check valve represents a particularly compact design of a check valve and also allows a particularly compact design of the hydraulic module including integration in the Pleuelground stresses and / or connecting rod cover.
  • the at least one check valve can open radially outward.
  • Such a band-check valve can be arranged particularly favorable on the outer circumference of the housing of the hydraulic module.
  • the check valve is very easy to install in this way and results in a compact design of the hydraulic module.
  • the band member may have at least one arranged in its peripheral surface radial opening. In this way, a compact space, consistent functionality and similar tape stiffness can be achieved and it can be particularly favorable parallel throttle points to the check valves.
  • the opening may be formed in the circumferential direction as a slot.
  • a favorable throttle point in a band element of a check valve is a slot, which defines the flow resistance by forming its length, which can be suitably varied by the geometric design.
  • the band element may have at least one radially inwardly disposed on its circumference groove.
  • Such arranged on the inside of the band member groove is a favorable alternative to an opening such as a hole or a slot in the circumferential direction of the band member.
  • a connecting rod is proposed for an internal combustion engine with variable compression with an eccentric adjusting device for adjusting an effective connecting rod length with a hydraulic module.
  • the eccentric adjusting device has at least a first cylinder and a second cylinder. In this case, both an inlet for supplying hydraulic fluid into the cylinder via a supply line and in each case a drain for discharging hydraulic fluid from the cylinders are provided in each case.
  • the connecting rod according to the invention advantageously requires only three hydraulic fluid lines in the connecting rod main body, whereby a favorable production can be achieved. Further, only a 3/2-way valve is required as a changeover valve in the hydraulic module, which advantageously simplifies the construction of the connecting rod.
  • the MBS hydraulic chamber can be biased by the GKS hydraulic chamber in the first low compression position ⁇ low . Conveniently, only differential volumes of hydraulic fluid between GKS and MBS hydraulic chamber are thus exchanged with the bearing shell of the connecting rod, ie no additional hydraulic fluid flows via the hydraulic fluid lines in the bearing shells.
  • Check valves and chokes can conveniently be structurally integrated in a hydraulic module. Thus, the hydraulic circuit diagram for both variants without or with additional check valve can be accommodated in a hydraulic module.
  • FIGS. 1 to 17 is an inventive hydraulic module 10 can be seen in various representations and sections. It shows FIG. 1 a side view of the hydraulic module 10 with various marked sectional planes, which for the representations in the FIGS. 3 to 17 were used while FIG. 2 the hydraulic module off FIG. 1 in a perspective view.
  • FIGS. 3 to 7 is the hydraulic module 10 in a first switching position S1 for high compression ⁇ high and in the FIGS. 13 to 17 shown in a second switching position S2 for low compression ⁇ low .
  • the FIGS. 8 to 12 show the hydraulic module 10 and the corresponding sections during a switching operation, ie in a position between the two switching positions S1 and S2.
  • Corresponding hydraulic circuit diagrams of a connecting rod 1 according to the invention are the FIGS. 18 and 19 refer to.
  • the connecting rod 1 according to the invention is in the hydraulic circuit diagrams according to the FIGS. 18 and 19 shown only schematically, but for example from the DE 10 2013 107 127 A1 known, to which express reference is made.
  • the connecting rod 1 for an internal combustion engine with variable compression for example, a not entirely and in detail illustrated eccentric adjusting device 40 for adjusting an effective connecting rod length.
  • This eccentric adjusting device 40 comprises a first cylinder 4 and a second cylinder 5 as hydraulic chambers, wherein both an inlet 6, 7 for supplying hydraulic fluid into the cylinders 4, 5 and in each case a drain 11, 12 for discharging hydraulic fluid from the Cylinders 4, 5 are provided.
  • the trained as a switching valve 41 and functioning hydraulic module 10 has a movable in a housing 3 stage piston 17th which is selectively displaceable in a first switching position S1 or a second switching position S2, wherein in the first switching position S1, the outlet 12 of the second cylinder 5 and in the second switching position S2, the outlet 11 of the first cylinder 4 is connected to a supply line 8.
  • the basic function of the switching valve 41 is also from the DE 10 2013 107 127 A1 known.
  • the cylinders 4, 5 are connected in the hydraulic module 10 according to the invention such that in the second switching position S2 hydraulic fluid from the first cylinder 4 into the second cylinder 5 via a channel 32 in the hydraulic module 10 can be conducted.
  • a switching element 36 is provided for controlling the hydraulic fluid flow in the channel 32, which is provided for example as a circumferential groove 27 of the piston 17, which forms part of the channel 32.
  • the hydraulic fluid flow is in the channel 32 via the circumferential groove 27 by an axial displacement of the piston 17 in the first or second switching position S1, S2 switchable.
  • the outlet 11 of the first cylinder 4 can be connected via the peripheral groove 27 to the inlet 7 of the second cylinder 5.
  • the cylinder 4 represents a hydraulic chamber on the gas-force side (GKS) of the connecting rod 1
  • the cylinder 5 represents a hydraulic chamber on the mass-force side (MCS) of the connecting rod 2.
  • the cylinders 4, 5 each have a check valve 18, 19 assigned in the inlet 6, 7, which allows a supply of hydraulic fluid into the cylinders 4, 5 and prevents the discharge of hydraulic fluid from the cylinders 4, 5.
  • a check valve 18, 19 assigned in the inlet 6, 7, which allows a supply of hydraulic fluid into the cylinders 4, 5 and prevents the discharge of hydraulic fluid from the cylinders 4, 5.
  • Only two check valves 18, 19 are necessary in the context of the invention. Further check valves need not be provided.
  • Inlet 6, 7 and outlet 11, 12 of a cylinder 4, 5 each open into a common line 13, 14 in the cylinder 4, fifth
  • the check valves 18, 19 are integrated in the hydraulic module 10 and have as closing element a substantially annular band member 33, 34 which surrounds the housing 3 at least partially on its circumference and is at least partially supported on the housing 3 and by means of which in a closed position Working connections 21, 22 are closable.
  • the two check valves 18, 19 open radially outward.
  • the band element 33, 34 has in each case at least one radial opening 35 arranged in its peripheral surface, wherein the opening 35 is designed as a slot in the circumferential direction.
  • the band element 33, 34 have at least one radially inwardly disposed on its circumference groove.
  • the outlet 11 of the first cylinder 4 can be connected to the peripheral groove 27 in the second switch position S2 via an end-side transverse bore 28 and / or via an oblique bore 29.
  • the connecting rod 1 In the starting position, the connecting rod 1 is in the switching position S1 for high compression ⁇ high .
  • the GKS hydraulic chamber 4 In this operating state, the GKS hydraulic chamber 4 is filled with hydraulic fluid, for example engine oil, and the MKS hydraulic chamber 5 is preferably throttled via the outlet 12 to the supply line 8, which is connected to a supply source P.
  • the step piston 17 of the hydraulic module 10 takes in the FIGS. 3 to 7 shown position.
  • At least one first working port 21 of the housing 3 of the hydraulic module 10 assigned to the GKS hydraulic chamber 4 is connected to a supply port 20 in communication with the supply line 8, in particular in FIG. 5 is apparent.
  • the connected to the first working port 21, preferably throttled drain 11 is closed by the piston 17, as in particular from FIG. 4 in the longitudinal section according to the sectional plane BB FIG. 2 is apparent.
  • a second, the MKS hydraulic chamber associated working port 22 is connected via the outlet 12 and the radial bore 15 to the supply port 20, so that the MKS hydraulic chamber 5 can empty. As in FIG. 4 can be seen, this is realized over a section of the stepped piston 17.
  • the supply port 20 and the working ports 21, 22 are formed as circumferential annular grooves, in which the inlets 6, 7, runs 11, 12 and other holes open. All holes (inlet 6, 7, drain 11, 12, etc.) in the housing 3 may be provided as a single bore, but are preferably distributed evenly over the circumference of the housing 3 several times.
  • the stepped piston 17 passes over at a defined switching stroke an edge 25 of an overflow channel 26, which from FIG. 8 is apparent. From this point, the pressure-acting surface of the piston 17 increases abruptly, so that the step piston 17 snaps into the other end position or in the switching position S2, which in the FIGS. 13 to 17 is shown.
  • the hydraulic fluid from the GKS hydraulic chamber 4 can flow via the outlet 11 and the supply port 20 throttled to P, while the drain 12 of the MKS hydraulic chamber 5 is closed via the step piston 17.
  • hydraulic fluid can be conducted from the first cylinder 4 into the second cylinder 5 via a channel in the hydraulic module 10.
  • the piston 17 has a circumferential groove 27, which can be activated and deactivated by the switching positions S1, S2.
  • FIGS. 16 and 17 can be removed, the outlet 11 of the first cylinder 4 via one or more end-side transverse bores 28, one or more oblique bores 29 and the circumferential groove 27 with the inlet 7 of the second cylinder 5 unthrottled connectable.
  • the MKS hydraulic chamber 5 sucks in hydraulic fluid (oil) from the circumferential groove 27 of the stepped piston 17 now connected to the GKS hydraulic chamber 4 via the check valve 19. This ensures that hydraulic fluid with GKS chamber pressure is available to the MKS hydraulic chamber 5. As a result, a more reliable filling of the MKS hydraulic chamber 5 is achieved in comparison to a direct suction from the supply source P at gallery pressure.
  • the band check valves 18, 19 are disposed over the outer periphery of the hydraulic module 10, whereby the overall system connecting rod can be simplified.
  • the band members 33, 34 are provided with openings 35 such as slots or holes to allow for a compact space, consistent functionality, and similar band rigidities sufficiently large flow cross-sections.
  • openings 35 such as slots or holes to allow for a compact space, consistent functionality, and similar band rigidities sufficiently large flow cross-sections.
  • a closure ring 30 is introduced into the housing 3 in combination with a sealing washer 31 and welded to the front side of the housing 3.
  • FIG. 20 represents a pressure-stroke diagram of the hydraulic module according to the invention with a hysteresis loop.
  • a stroke of the stepped piston 17 with increasing pressure for a switching from ⁇ high to ⁇ low (solid line) and a stroke curve at falling pressure for a Switching operation from ⁇ low to ⁇ high (wide dashed line).
  • the stroke is shown when switching (narrow dashed line).
  • the illustrated hysteresis loop of the hydraulic module 10 is reflected in a bistable behavior of the connecting rod 1 again. If the pressure in the gallery or the supply source P never increases above a certain switching pressure addition, the connecting rod 1 is always in the operating state ⁇ high . When the switching pressure is exceeded, the connecting rod 1 changes the operating state to ⁇ low . This state is maintained until the gallery pressure again falls below a certain switching pressure, which is lower than in the previous switching operation.
  • the hydraulic module according to the invention is thus a possible design solution for biasing the MKS hydraulic chamber 5 combined with a hydraulic changeover valve and integrated non-return valves 18, 19th
  • the hydraulic fluid supply of the MKS hydraulic chamber 5 via the gallery pressure can advantageously be deactivated and activated via a circumferential groove 27 in the stepped piston 17.
  • a circumferential groove 27 in the stepped piston 17 in the housing 3 of the hydraulic module 10 introduced frontal bores 15, 28, 29 interconnected.
  • a shape contour on the stepped piston 17 is also conceivable which, when a certain stroke is exceeded, opens a spring-loaded slide or slide system, which in turn enables a connection between the MBS chamber 5 and the GKS hydraulic chamber 4.
  • a similar system could push two inclined planes in one of the two end positions, which in turn deactivate or activate an oil connection.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Claims (15)

  1. Module hydraulique (10) pour commander un flux de liquide hydraulique d'une bielle (1) pour un moteur à combustion interne à compression variable avec un dispositif de réglage excentrique (40) pour le réglage d'une longueur de bielle effective,
    dans lequel il se trouve côté module au moins un piston (17) mobile dans un boîtier (3), qui peut être déplacé au choix dans une première position de connexion (S1) ou dans une deuxième position de connexion (S2),
    dans lequel le module hydraulique (10) présente au moins un premier et un deuxième raccord de travail (21, 22) ainsi qu'un raccord d'alimentation (20) et un clapet anti-retour (18, 19) est respectivement associé aux raccords de travail (21, 22), et
    dans lequel les raccords de travail (21, 22) sont connectés dans le module hydraulique (10) de telle manière que dans la première position de connexion (S1) le premier raccord de travail (21) soit raccordé par une arrivée (6) au raccord d'alimentation (20) et que le deuxième raccord de travail (22) soit raccordé par une évacuation (12) au raccord d'alimentation (20),
    dans lequel une évacuation (11) du premier raccord de travail (21) et une arrivée (7) du deuxième raccord de travail (22) sont fermées, et dans la deuxième position de connexion (S2) l'évacuation (12) du deuxième raccord de travail (22) est fermée et l'évacuation (11) du premier raccord de travail (21) est reliée par un canal (32) dans le module hydraulique (10) directement à l'arrivée (7) du deuxième raccord de travail (22), de telle manière que du liquide hydraulique puisse être conduit du premier raccord de travail (21) directement au deuxième raccord de travail (22).
  2. Module hydraulique selon la revendication 1, caractérisé en ce qu'il est prévu un élément de commutation (36) dans le piston (17) pour la commande du flux de fluide hydraulique dans le canal (32).
  3. Module hydraulique selon la revendication 2, caractérisé en ce que l'élément de commutation (36) est prévu en tant que contour de forme sur le piston (17).
  4. Module hydraulique selon la revendication 2, caractérisé en ce qu'il est prévu comme élément de commutation (36) une rainure périphérique (27) du piston (17), qui forme une partie du canal (32).
  5. Module hydraulique selon la revendication 4, caractérisé en ce que le flux de liquide hydraulique dans le canal (32) par la rainure périphérique (27) peut être commuté par un déplacement axial du piston (17) dans la première ou dans la deuxième position de connexion (S1, S2).
  6. Module hydraulique selon une revendication 4 ou 5, caractérisé en ce que dans la deuxième position de connexion (S2) l'évacuation (11) du premier raccord de travail (21) peut être connectée à l'arrivée (7) du deuxième raccord de travail (22) par la rainure périphérique (27).
  7. Module hydraulique selon l'une quelconque des revendications 4 à 6, caractérisé en ce que dans la deuxième position de connexion (S2) l'évacuation (11) du premier raccord de travail (22) peut être connectée à la rainure périphérique (27) par un perçage transversal côté frontal (28) et/ou par un perçage oblique (29).
  8. Module hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu des perçages frontaux (6, 28) du boîtier (3) rendus étanches au moyen d'une rondelle d'étanchéité annulaire (31) et/ou d'un anneau de fermeture (30).
  9. Module hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que les clapets anti-retour (18, 19) sont intégrés dans le module hydraulique (10).
  10. Module hydraulique selon la revendication 9, caractérisé en ce qu'au moins un des clapets anti-retour (18, 19) présente comme élément de fermeture un élément de bande essentiellement annulaire (33, 34), qui entoure le boîtier (3) au moins partiellement sur sa périphérie et est supporté au moins en partie sur le boîtier (3) et au moyen duquel des raccords de travail (21, 22) peuvent être fermés dans une position fermée.
  11. Module hydraulique selon la revendication 10, caractérisé en ce que ledit au moins un clapet anti-retour (18, 19) s'ouvre radialement vers l'extérieur.
  12. Module hydraulique selon une revendication 10 ou 11, dans lequel l'élément de bande (33, 34) présente au moins une ouverture radiale (35) dans sa surface périphérique.
  13. Module hydraulique selon la revendication 12, caractérisé en ce que l'ouverture (35) est formée par un trou oblong dans la direction périphérique.
  14. Module hydraulique selon une revendication 10 ou 11, caractérisé en ce que l'élément de bande (33, 34) présente au moins une rainure disposée radialement à l'intérieur sur sa périphérie.
  15. Bielle (1) pour un moteur à combustion interne à compression variable avec un dispositif de réglage excentrique (40) pour le réglage d'une longueur de bielle effective, avec un module hydraulique (10) selon l'une quelconque des revendications 1 à 14, dans laquelle le dispositif de réglage excentrique (40) présente au moins un premier cylindre (4) connecté au premier raccord de travail (21) du module hydraulique (10) et un deuxième cylindre (5) connecté au deuxième raccord de travail (22) du module hydraulique (10) et dans laquelle il est prévu aussi bien chaque fois une arrivée (6, 7) pour amener du liquide hydraulique dans les cylindres (4, 5) par une conduite d'alimentation (8) que chaque fois aussi une évacuation (11, 12) pour évacuer du liquide hydraulique des cylindres (4, 5).
EP18150946.4A 2017-01-18 2018-01-10 Module hydraulique de commande d'un flux de liquide hydraulique d'une bielle pour un moteur à combustion interne à compression variable ainsi que bielle Active EP3351764B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017100859 2017-01-18
DE102017121432.1A DE102017121432A1 (de) 2017-01-18 2017-09-15 Hydraulikmodul zum Steuern eines Hydraulikflüssigkeitsstroms eines Pleuels für eine Brennkraftmaschine mit variabler Verdichtung sowie Pleuel

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Publication Number Publication Date
EP3351764A1 EP3351764A1 (fr) 2018-07-25
EP3351764B1 true EP3351764B1 (fr) 2019-09-11

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012020999B4 (de) 2012-07-30 2023-02-23 FEV Europe GmbH Hydraulischer Freilauf für variable Triebwerksteile
DE102013103685B4 (de) * 2013-04-12 2023-09-21 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem solchen Umschaltventil
DE102013107127A1 (de) * 2013-07-05 2015-01-08 Hilite Germany Gmbh Pleuel für eine zweistufige variable Verdichtung
DE102015100662A1 (de) * 2014-12-19 2016-06-23 Hilite Germany Gmbh Hydraulikventil zum Schalten eines Stellkolbens eines Pleuels
JP2016118277A (ja) * 2014-12-22 2016-06-30 トヨタ自動車株式会社 可変長コンロッド及び可変圧縮比内燃機関
DE102015202535A1 (de) * 2015-02-12 2016-08-18 Schaeffler Technologies AG & Co. KG Wegeventil

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EP3351764A1 (fr) 2018-07-25

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