EP3791055A1 - Bielle à longueur réglable, moteur à pistons alternatifs et véhicule - Google Patents

Bielle à longueur réglable, moteur à pistons alternatifs et véhicule

Info

Publication number
EP3791055A1
EP3791055A1 EP19727922.7A EP19727922A EP3791055A1 EP 3791055 A1 EP3791055 A1 EP 3791055A1 EP 19727922 A EP19727922 A EP 19727922A EP 3791055 A1 EP3791055 A1 EP 3791055A1
Authority
EP
European Patent Office
Prior art keywords
valve
connecting rod
hydraulic
length
recess
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.)
Withdrawn
Application number
EP19727922.7A
Other languages
German (de)
English (en)
Inventor
Martin Rath
Siegfried Lösch
Christian Gallob
Klaus Landfahrer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
AVL List GmbH
Iwis Motorsystem GmbH and Co KG
Original Assignee
AVL List GmbH
Iwis Motorsystem GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from ATA50382/2018A external-priority patent/AT520821B1/de
Priority claimed from ATA50877/2018A external-priority patent/AT521469B1/de
Application filed by AVL List GmbH, Iwis Motorsystem GmbH and Co KG filed Critical AVL List GmbH
Publication of EP3791055A1 publication Critical patent/EP3791055A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/06—Adjustable connecting-rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F16K11/0704—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides comprising locking elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/04—Check valves with guided rigid valve members shaped as balls
    • F16K15/044—Check valves with guided rigid valve members shaped as balls spring-loaded

Definitions

  • the present invention relates to a length-adjustable connecting rod for a reciprocating engine, in particular for a reciprocating internal combustion engine, wherein an effective connecting rod length of the connecting rod is variable.
  • the connecting rod has a hydraulic length adjustment device which has at least one hydraulic working space, at least one hydraulic channel for discharging hydraulic medium from the hydraulic working space, at least one valve recess with a valve recess longitudinal axis, and a valve device with a valve space arranged in the valve recess having.
  • the valve device is designed to open and / or block a Hydraulikmediumabhnes from the hydraulic working space.
  • the hydraulic channel is arranged in a flow path between the valve device and the hydraulic working space and opens into the valve recess with a first end at a connection opening in an inner wall section of the valve recess.
  • the invention relates to a reciprocating engine with such a connecting rod and a vehicle with such a reciprocating engine.
  • Compression ratio in a reciprocating engine various measures from the prior art are well known.
  • One of these measures is, for example, to vary the absolute positions of the top and bottom dead centers of a cyclically reciprocally movable piston in a cylinder of the reciprocating internal combustion engine by an effective length of a connecting rod, which is defined in particular by a distance between a first axis of rotation, around which the connecting rod is preferably rotatable about a crankshaft with its large connecting rod eye in a functional condition of use in a reciprocating engine, and a second axis of rotation about which the connecting rod is preferably rotatable about a piston pin with its small connecting rod is changed accordingly.
  • To change the effective connecting rod length is known to provide a suitably trainedCentralnverstell Surprise, with different concepts for length adjustment are known.
  • a hydraulic length adjustment device with relatively displaceable, in particular telescopically nested or mecanicschiebbaren, connecting rods
  • the associatedConnectnverstell 180 usually has one or more hydraulic chambers, which filled or drained depending on the desired connecting rod length with a hydraulic medium can be.
  • the control device has a first and a second valve space in each of which a, in a closed state by means of a spring pressed against a valve seat valve body is arranged, wherein the valve chambers are in each case fluidly connected to one of the hydraulic channels.
  • one of the valve bodies arranged in the valve bodies which can be pressed by the restoring force of the spring against the valve seat and are operatively connected to each other via a sliding connection means, can be lifted from the valve assembly against the restoring force of a valve spring from the valve seat and thus the respective valve chamber to flow communication with the hydraulic medium supply passage, while the other valve body blocks the flow connection to the hydraulic medium supply passage, whereby the length adjustment, in particular a hydraulic medium inflow and outflow into and out of the hydraulic chambers of the clauses of the clauses can be controlled.
  • This object is achieved by a length-adjustable connecting rod, by a reciprocating piston engine with such a connecting rod and by a vehicle with such a reciprocating piston engine according to the independent claims.
  • a first aspect of the invention relates to a length-adjustable connecting rod for a reciprocating engine, in particular for a reciprocating internal combustion engine, wherein an effective connecting rod length of the connecting rod is variable, in particular adjustable, wherein the connecting rod for changing the effective connecting rod length has a hydraulic length adjustment, the at least one hydraulic working space, at least one hydraulic channel for discharging hydraulic medium from the hydraulic working space, at least one valve recess with a
  • Ventilausnaturalungungs L Kunststoffsachse and having a valve disposed in the Ventilaus fundamentalung valve means having a valve chamber, wherein the valve means for opening and / or blocking a Hydraulikmediumabhnes from the hydraulic working space is formed, and wherein the hydraulic channel is arranged in a flow path between the valve means and the hydraulic working space and opens with a first end at an orifice in an inner wall portion of the valve recess in the valve recess.
  • the valve device has at least one, the
  • Opening wall opposite the outer wall portion which is formed closed at least in a region opposite to the mouth opening, that has no through holes, and the valve chamber of the valve means at least partially surrounds and in particular has no through-openings into the interior of the valve chamber, wherein the closed outer wall portion of the valve means together with the inner wall section of the valve recess surrounding the inlet opening forms a flow channel, wherein the flow channel is configured to at least partially separate from the hydraulic channel with a first flow direction and entering the VentilausEnglishung hydraulic medium before entering the valve chamber of the valve means in a different second from the first flow direction To redirect flow direction.
  • the closed outer wall section which at least partially surrounds the valve space, it is possible to prevent hydraulic fluid draining from the hydraulic working space from entering directly into the valve space.
  • components arranged in the valve chamber can be protected against damage by the hydraulic medium, which can occur when the valve device is opened at high flow velocity as a result of the high working pressures which can occur in the associated hydraulic working space and exceed 3,000 bar Hydraulic channel flows, in particular "shoots", and consequently hits with a strong pulse on the valve device.
  • the hydraulic medium can occur when the valve device is opened at high flow velocity as a result of the high working pressures which can occur in the associated hydraulic working space and exceed 3,000 bar Hydraulic channel flows, in particular "shoots", and consequently hits with a strong pulse on the valve device.
  • cavitation effects can occur, which can lead to damage of the component surfaces and, as a result, to mechanical weakening and ultimately to failure.
  • the closed outer wall portion opposite the mouth which acts like a shield
  • a direct entry of the hydraulic medium into the valve space at high flow velocity and / or high pressure into the valve space can be easily prevented and the components arranged in the valve space can be protected , This can reduce the mechanical stress on these components and, in some cases, increase their life.
  • deflecting the flow can be achieved in a corresponding embodiment of the deflection throttling and reduce flow energy, in particular reduce a flow velocity. This can reduce the risk of cavitation.
  • the outer wall section has at least one hardened surface or coating, for example a wear protection layer or the like, for example a PVD or CVD coating.
  • the closed outer wall section may have a surface structure which is advantageous for this purpose and / or correspondingly suitable flow influencing elements, with a surface structure minimizing in particular a flow energy minimizing, in particular friction-generating and / or direction-changing, surface structure and / or correspondingly influencing flow influencing elements can be viewed.
  • coating the closed outer wall section with a friction-enhancing coating may also be advantageous.
  • the coating should not be able to be removed by the hydraulic medium, since in an advantageous embodiment of a connecting rod according to the invention, a hydraulic circuit of the hydraulic length adjustment with an oil circuit of an associated reciprocating engine is fluid-connected or in an inventive
  • Reciprocating engine is fluidly connected. This removed particles of the coating could lead to damage to the reciprocating engine.
  • At least one valve recess of a connecting rod according to the invention can be produced as a blind hole-like recess or blind hole, in particular with a valve recess opening on one side in the longitudinal direction of the valve recess, in particular as a valve recess which has at least one section with an internal thread, in particular with one the Ventilaus originallyungsö réelle adjacent internal thread.
  • This requires only on one side to secure the valve device against falling out of the valve recess and in particular allows the use of a screw, in particular a screw plug as securing means.
  • the flow channel may be configured to deflect the hydraulic medium in a second flow direction which is parallel to the valve recess longitudinal axis of the valve recess.
  • the flow channel is in particular configured to reduce a flow velocity of a hydraulic medium emerging from the hydraulic channel and entering the valve recess prior to entry into the valve chamber of the valve device.
  • a throttle may be arranged in a hydraulic channel section adjoining the valve recess or this hydraulic channel section may be designed as a throttle.
  • the hydraulic channel can have, for example, a reduced flow cross-section, in particular compared to a previous, in particular adjacent, hydraulic channel section, for example a flow cross-section reduced to 50% or less of a previous flow cross-section, or a flow cross-section reduced to 25% or less of a previous flow cross-section or directly adjacent to the inlet opening ,
  • a reduced flow cross-section in particular compared to a previous, in particular adjacent, hydraulic channel section, for example a flow cross-section reduced to 50% or less of a previous flow cross-section, or a flow cross-section reduced to 25% or less of a previous flow cross-section or directly adjacent to the inlet opening .
  • the flow velocity of the hydraulic medium can be reduced even before it enters the valve recess, ie, before the inlet opening and before hitting the closed wall section.
  • the throttle is arranged only shortly before the mouth opening in the hydraulic channel.
  • the flow channel is in particular configured such that from the hydraulic channel with the first Flow direction exiting and entering the Ventilaus Principleung hydraulic medium before entering the valve chamber of the valve means by at least 50 °, preferably at least 60 °, 70 °, 80 ° or 85 ° is deflected, but in particular at most by 90 °, 100 °, 120 ° , 150 ° or 180 °.
  • the hydraulic channel can open into the valve recess via a circumferential wall of the valve recess, the hydraulic channel preferably at an angle of at least 30 °, 45 °, 60 °, 70 °, 80 ° or 85 ° to the Ventilaus originallyungs longitudinal axis of the valve recess, but in particular at most at an angle of 90 ° and thus perpendicular to the valve recess longitudinal axis of the valve opening, opens into the valve recess.
  • the hydraulic channel opens in particular with the portion of the hydraulic channel adjoining the valve recess in the radial direction to the valve recess longitudinal axis.
  • This can be achieved with a corresponding configuration of the other components of the valve device that the hydraulic medium impinges perpendicular to the closed outer wall portion, whereby a particularly high reduction of the flow velocity and thus a particularly good reduction of the risk of cavitation can be achieved.
  • Possible damage to the closed outer wall section can be counteracted in a simple manner by a corresponding wear protection layer or the like.
  • the hydraulic channel can open into the valve recess in such a way that a hydraulic channel longitudinal axis of a hydraulic channel section adjoining the valve recess intersects the valve recess longitudinal axis of the valve recess, the hydraulic channel longitudinal axis of the valve recess adjoining the valve recess Hydraulic channel section, in particular with the Ventilaus originallyungs longitudinal axis in a common longitudinal central plane of the valve recess.
  • the hydraulic medium does not enter the valve space with a twist, since this can lead to negative effects, in particular to a negative influence on the components of the valve device. This can, for example, lead to an undesired rotation of the valve body and thus to a non-precise valve lift.
  • the hydraulic channel opens off-center into the valve recess and thus offset, in particular eccentrically to Ventilaus originallyungs longitudinal axis. If necessary, additional flow control elements can be provided, in particular in this case, with which the flow effects which may be undesirable due to the off-center junction can be reduced or compensated.
  • the closed outer portion of the valve device which at least partially surrounds the valve chamber of the valve means, based on the Ventilaus strictlyungs longitudinal axis of the valve recess, the valve space at least partially surrounded in the circumferential direction.
  • a particularly advantageous inflow of hydraulic medium into the valve recess can be achieved.
  • the hydraulic medium first flows around the valve device at least partially in the circumferential direction before the hydraulic medium is conducted into the valve chamber.
  • a flow path, which the hydraulic medium has to cover as far as entry into the valve chamber can be lengthened significantly without any appreciable, in particular almost no, additional installation space.
  • a significantly improved reduction of the flow rate can be achieved.
  • the flow channel may be at least partially in the axial direction and at least partially extending in the circumferential direction annular space segment, or at least partially in the axial direction and over the entire circumference extending annular space, ie a circumferentially completely closed annulus. This allows a particularly advantageous flow guidance of the hydraulic medium can be achieved before entering the valve chamber.
  • a particularly simple annular space can be formed when the valve recess in the region of the inner wall portion surrounding the mouth opening is at least partially cylindrical along the VentilausEnglishungs longitudinal axis, wherein an associated inner lateral surface preferably the annular space bounded radially outwardly, and if the closed outer wall portion of the valve means at least partially along the Ventilausappelungs longitudinal axis is formed cylinder jacket-shaped, wherein the cylinder jacket-shaped, closed-shaped outer wall portion of the annular space preferably limited in the radial direction inwards.
  • the closed outer wall portion of a length-adjustable connecting rod does not have to have a constant outer diameter in the axial direction, it may also have a changing outer diameter, in which case, however, a gap width of the annular space or annulus segment preferably increases in the flow direction.
  • a particularly simple annular space segment can be designed accordingly, but does not extend over the entire circumference of the valve device, but only over part of it, i. for example, only over 180 ° instead of over 360 °, such as a closed annular space in the circumferential direction.
  • An annular space segment can in one possible embodiment, for example, by an axial groove in the closed outer wall portion of the valve device be formed, which bounds the annulus segment radially inward, or have one or more introduced into a closed outer wall surface grooves.
  • the inner wall portion of the valve recess may alternatively or additionally also have corresponding grooves. He is preferred but cylindrical. This simplifies the manufacture of the valve recess.
  • the closed outer wall portion of the valve device is preferably by a closed outer surface of a cylinder jacket-shaped portion of
  • Valve device in particular formed by a closed outer surface of a cylinder jacket-shaped portion or a plurality of cylinder jacket-shaped portions of one or more components of the valve device, in particular by a cylinder jacket-shaped region of one or more components of the valve device, the opposite the Ventilaus Principleung in the region around the mouth of the hydraulic channel around a reduced outer diameter exhibit. This makes it possible to achieve a particularly simple deflection of the hydraulic medium in a second flow direction which runs parallel to the valve recess longitudinal axis.
  • Flow channel may be formed closed at a first side and open at an opposite, second side, wherein the flow channel is fluidkommunijackd connected in particular via the second side with the valve chamber, wherein the flow channel, in particular the annulus segment or the annulus, in particular on the first side in axial Direction is formed closed and open at the opposite, second side in the axial direction, based on the Ventilaus predominantlyungs longitudinal axis.
  • the flow channel, in particular the annular space segment or the annular space, in particular on the first side in the axial direction for example, by an outer wall portion of the valve means, in particular by an adjacent to a sealing surface or designed as a sealing surface outer wall portion, be closed.
  • an advantageous hydraulic medium flow within the valve recess can be achieved in a particularly simple manner, in particular until it enters the valve chamber.
  • the closed outer wall section of the valve device which forms the flow channel together with the inner wall section of the valve recess surrounding the inlet opening, can have a groove and / or a chamfer, in particular one at least partially extending in the circumferential direction groove and / or a chamfer, in particular an adjacent to a shoulder or to a radially extending paragraph heel.
  • an advantageous hydraulic medium flow within the valve recess, in particular until it enters the valve chamber can be achieved in a particularly simple manner.
  • the groove or the chamfer or the undercut in particular in the region of the first side, on which the flow channel is preferably closed in the axial direction, be arranged in the outer wall portion and in particular adjacent to a sealing surface ,
  • the groove or chamfer or the undercut may thereby form at least partially, alternatively completely, a surface radially delimiting the annular space, in particular a surface radially inwardly delimiting the annular space, wherein the groove or chamfer or the undercut can be formed in particular completely circumferential.
  • an "undercut” is understood to mean removal from a rotationally symmetrical inner edge with a specific shape and specified dimensions, in particular a groove with a geometry according to DIN 509.
  • Valve device in particular a arranged in the valve chamber, for opening the valve device against a restoring force, in particular against a restoring force of a valve spring, liftable from a valve seat along a Ventilhubachse valve body, wherein the closed formed outer portion of the valve means, with the surrounding the mouth opening
  • Inner wall portion forms the flow channel, the valve space at least partially in the region of the valve body and / or the valve spring surrounds, wherein the valve means is arranged with the Ventilhubachse particular parallel to the VentilausEnglishungs longitudinal axis of the VentilausEnglishung, i. in particular such that the valve stroke axis of the valve body runs parallel to the valve recess longitudinal axis of the valve recess.
  • valve device By means of such a valve device can be achieved in a particularly advantageous, simple manner, the opening and locking of a Hydraulikmediumabhnes from an associated hydraulic working space.
  • the closed-formed outer portion surrounds the valve space at least partially in the region of the valve body and / or the valve spring and in particular prevents entry of hydraulic medium in this area in the valve chamber, the valve body and / or the valve spring in a simple manner from damage be protected by a direct impact of the hydraulic medium and consequently, for example, resulting cavitation and thus the loads acting on the valve body and / or the valve spring loads are reduced.
  • the life of the valve body and / or the valve spring can be increased.
  • At least one such trained valve device based on a functional use state of the connecting rod in a reciprocating engine, with the valve lift arranged in particular parallel to a crankshaft longitudinal axis.
  • the valve device has a valve seat unit with a valve seat, wherein the closed outer wall section, which forms the flow channel together with the inner wall section of the valve recess surrounding the inlet opening, passes through an outer wall section Valve seat unit is formed.
  • the valve seat unit is designed such that the flow channel is preferably closed towards the valve seat in the axial direction and the valve spring open, wherein the closed outer wall portion preferably extends from the valve seat in the direction of the valve spring, in particular jacket-shaped and preferably at least partially around the valve body and / or the valve spring around, in particular cylinder jacket-shaped and particularly preferably completely encircling, ie over the entire circumference.
  • the valve seat unit may have a particular sleeve-shaped portion, wherein an outer surface of the sleeve-shaped portion at least partially forms the closed outer wall portion.
  • the closed outer wall section of a length-adjustable connecting rod in this case need not have a constant outer diameter in the axial direction, it can in particular also decrease starting from the valve seat, depending on the advantageous flow contour.
  • the valve device has a spring guide unit for axially supporting and / or guiding the valve spring, wherein the closed outer wall section, which forms the flow channel together with the inner wall section of the valve recess surrounding the inlet opening, is formed in particular by an outer wall section of the spring guide unit.
  • the spring guide unit may have a particular sleeve-shaped portion, wherein an outer surface of the sleeve-shaped portion at least partially forms the closed outer wall portion.
  • the closed outer wall section preferably extends from the valve spring in the direction of the valve seat, preferably jacket-shaped and at least partially around the valve spring and / or the valve body, in particular cylinder jacket-shaped and / or cone-shaped, and particularly preferably completely circumferential, ie. over the entire circumference, wherein the closed outer wall portion extends in the axial direction, in particular to over the valve body.
  • the closed outer wall portion of a length-adjustable connecting rod does not have to have a constant outer diameter in the axial direction, it can in particular also decrease starting from the valve spring, depending on the advantageous flow contour.
  • the closed outer wall section can also be formed by another component, in particular by the outer wall of another component, for example by the outer wall of a sleeve or the like surrounding the valve chamber in this area.
  • the spring guide unit in particular additionally, a Have spring guide element, preferably with a cylindrical recess in which the valve spring is at least partially guided and at the bottom of the valve spring, in particular with its remote from the valve body end, may be supported.
  • the valve device comprises a securing means, in particular a screw plug, by means of which parts of the valve device or the entire valve device are secured against falling out of the valve recess, wherein in particular the securing means for axial support and / or is designed to guide the valve spring.
  • the securing means may additionally be designed in particular as a spring guide element and form part of the spring guide unit or the spring guide unit, wherein the securing means may in particular have a cylindrical recess in which the valve spring may be at least partially guided and at the bottom of the valve spring, in particular with its from the valve body remote end, can be supported.
  • an inner wall section adjacent to the valve seat of the valve body and / or surrounding the valve body in the region of the valve seat at least partially overlaps at least over a defined area in the circumferential direction and at least in the radial direction have outside and in the axial direction extending recess, preferably at least one recess with a semicircular, semi-elliptical, kidney-shaped or atomic radial cross-section, in particular a plurality of evenly distributed circumferentially such recesses.
  • the valve device is an actuatable control valve device, in particular an actuatable by means of a rod-like, axially displaceable actuating element control valve device, wherein the valve body de control valve device is lifted in a first actuation position of the rod-like actuator from the valve seat and a Hydraulikmediumabkg is opened from the hydraulic chamber via the hydraulic channel, into the valve recess and through the valve chamber, and in a second actuation position of the actuator, the valve body of the control valve device rests against the valve seat and a Hydraulikmediumabkg from the hydraulic chamber via the hydraulic channel, into the Ventilaus predominantlyung and through the valve chamber Is blocked.
  • the rod-like actuating element is preferably axially displaceable along an actuating axis oriented parallel to the valve stroke axis, in particular along an actuating axis coinciding with the valve stroke axis, as for example in some embodiments of length-adjustable connecting rods with hydraulic length adjustment disclosed in WO 2016/203047 A1.
  • the rod-like actuating element can also be axially displaceable along an actuating axis oriented perpendicular to the valve lifting axis.
  • control valve device may further comprise an actuating body which is arranged between the valve body and the rod-like actuating element, and which serves in particular for the mechanical transmission of an actuation of the actuating element on the valve body.
  • an actuating body which is arranged between the valve body and the rod-like actuating element, and which serves in particular for the mechanical transmission of an actuation of the actuating element on the valve body.
  • a length-adjustable connecting rod has an adjacent to a valve seat of the actuating body and / or the actuating body in the region of the associated valve seat at least partially shell-shaped surrounding inner wall portion at least over a defined region in the circumferential direction and at least in the radial direction outwardly and axially extending bypass passage opening, preferably at least one bypass passage opening with a semicircular, semi-elliptical, kidney-shaped or atomic radial cross-section, in particular a plurality of evenly distributed in the circumferential direction arranged such bypass passage opening.
  • the connecting rod in particular thejurinverstell noticed, a hydraulic cylinder with a first hydraulic working space and a second hydraulic working space, which in particular by a double-acting hydraulic piston, in particular as a stepped piston, i. with two different sized active surfaces, is formed, are separated.
  • the connecting rod also has a hydraulic medium supply line and / or a drainage line which can be connected to communicate with the first hydraulic working space and / or the second hydraulic working space in a fluid-communicating manner.
  • the length of the connecting rod can be adjusted directly via the position of the hydraulic piston in the hydraulic cylinder.
  • the length adjustment device can in particular an inflow and outflow of a Hydraulic medium can be controlled in and out of the two hydraulic working spaces of the hydraulic cylinder.
  • the forces acting on the movement of the connecting rod can be absorbed by the hydraulic cylinder and passed on to the hydraulic medium. If the hydraulic medium supply line and, if appropriate, the drainage are closed, a change in the length of the connecting rods can be prevented. On the other hand, if the hydraulic medium supply line or the drainage is opened, in particular by the corresponding switching position of the switching valve, a change in the length of the connecting rods can be effected, depending on the applied forces or pressures.
  • the Computingnverstellvoriques can in this case for each hydraulic working space, in particular in each case a control valve device, preferably egg vorgeriebene
  • Control valve device for opening and / or locking a Hydraulikmediumabhnes from the associated hydraulic working space, and a check valve device, via which in the associated hydraulic working space during a stroke hydraulic medium can be sucked, but can not drain.
  • both control valve means can be actuated by means of a common, rod-shaped, axially displaceable actuating element, wherein the actuating element in particular by means of a double-acting actuating piston in response to an applied hydraulic pressure, in particular depending on a in a reciprocating engine, in particular a reciprocating internal combustion engine, applied oil pressure can be actuated.
  • a second aspect of the invention relates to a reciprocating engine, in particular reciprocating internal combustion engine, with a length-adjustable connecting rod, which is formed according to the first aspect of the invention.
  • a third aspect of the invention relates to a vehicle, in particular a motor vehicle, with a reciprocating engine, which is formed according to the third aspect of the invention.
  • Embodiment of the invention can be realized and can represent an advantageous and self-protective design, if they are technically feasible.
  • FIG. 1 shows a first embodiment of a length-adjustable connecting rod according to the invention in side view
  • FIG. 2 shows a first connecting rod part of the length-adjustable connecting rod from FIG. 1, likewise in side view, with partial representation of hidden contours, FIG.
  • Fig. 3a is a schematic functional diagram of the hydraulic
  • Fig. 3b is a schematic functional diagram of the hydraulic length adjustment of the connecting rod of FIGS. 1 and 2, shown in a second state for setting a minimum effective connecting rod length
  • Fig. 4a shows a detail of a section through the connecting rod according to the invention from FIGS. 1 and 2 along the Cutting plane YY 'in a second state for setting a minimum effective connecting rod length
  • FIG. 4b shows a detail of a section through the connecting rod according to the invention from FIGS. 1 and 2 along the sectional plane Y-Y 'in a first state for setting a maximum effective connecting rod length
  • Fig. 5 is an enlarged section of Fig. 4a in the region of the upper
  • Fig. 6 shows a greatly enlarged section of FIG. 5 in a perspective
  • FIG. 7 shows a detail of a partial section through the connecting rod according to the invention from FIGS. 1 and 2 in the area of the lower control valve device 14A along a different sectional plane than in FIGS. 4a and 4b;
  • FIG. 8 shows a section of a longitudinal section along a plane perpendicular to one
  • FIGS. 9 shows a detail of a partial section through the connecting rod according to the invention from FIGS. 1 and 2 in the region of the lower control valve device 14A along a further sectional plane
  • valve recess 6A of the lower control valve device 14A View substantially obliquely from above into or into the valve recess 6A of the lower control valve device 14A, 1 1 in side view, the valve recess 6A of FIG. 10 with actuator body,
  • Fig. 12 shows a detail of a first section through a second
  • FIG. 13 shows a section of a second section of the length-adjustable connecting rod from FIG. 12 along a second sectional plane Y-Y 'analogous to FIG. 1.
  • first connecting rod 2 of the connecting rod 1 shows a first exemplary embodiment of a length-adjustable connecting rod 1 in a side view, wherein the connecting rod 1 has a first connecting rod part 2 or a first connecting rod section 2 and a second connecting rod part 4 or a second connecting rod section 4.
  • first connecting rod 2 of the connecting rod 1 a large connecting rod 3 for connecting the connecting rod 1 with a crankshaft not shown here and the second connecting rod 4 of the connecting rod 1, a small connecting rod 5 to connect the connecting rod 1 with a reciprocating piston, also not shown.
  • the first Pleuelteil 2 and the second Pleuelteil 4 are along a Pleuell horrsachse Z relative to each other displaceable, in particular telescopically into one another and pushed apart, so that an effective Pleuelin L of the connecting rod 1 changeable, in particular adjustable, wherein the effective Pleuelin means of a length adjustment.
  • 7 is adjustable, in particular, a minimum effective connecting rod length and a maximum effective connecting rod length are adjustable.
  • the connecting rod 1, in particular the first connecting rod part 2, in the present example, two control valve recesses 6A and 6B and two check valve recesses 8A and 8B, preferably above the large connecting rod 3 and between the large connecting rod 3 and the small connecting rod 5, in particular in one area of the connecting rod 1 on the large connecting rod eye 3, are arranged and extend in a preferred manner perpendicular to Pleuell Kunststoffsachse Z and parallel to a crankshaft axis, based on a functional installation state of the connecting rod 1 in a reciprocating engine.
  • a respective control valve device 14A or 14B (see FIG. 2) is arranged and by a securing means 9, in particular a screwed into the respective control valve recess 6A and 6B
  • Closure screw 9 fixed, and thus in particular on the one hand against falling out of the associated control valve recess 6A and 6B secured and further fixed in this case in the axial direction in the control valve recess 6A and 6B.
  • a check valve device 15A or 15B (see FIG. 2) is arranged and likewise fixed by a securing means 9 and thereby likewise secured against falling out of the associated non-return valve recess 8A or 8B and furthermore in the axial direction fixed in the check valve recess 8A and 8B, respectively.
  • Fig. 2 shows the first Pleuelteil 2 of the length-adjustable connecting rod 1 of FIG. 1, also in side view, with partial representation of hidden contours, which are indicated by the dashed lines.
  • the first connecting rod part 2 has, in particular, a guide and hydraulic cylinder 10 extending along the connecting rod longitudinal axis Z.
  • the hydraulic cylinder 10 is designed and configured to at least partially receive the second connecting rod part 4 of the connecting rod 1 shown in FIG.
  • the part of the second connecting rod part 2 of the connecting rod 1 which is received in front of the hydraulic cylinder 10 is preferably designed as a hydraulic piston 17 (cf., FIGS. 3a and 3b), in particular as a stepped piston, and together with the hydraulic cylinder 10 forms two not shown in FIG. However, from FIGS. 3a and 3b recognizable hydraulic working spaces 10A and 10B or (high) pressure chambers.
  • the hydraulic piston 17 and the hydraulic cylinder 10 are part of the length adjustment 7 for changing, in particular adjustment, the effective connecting rod L. With reference to FIGS. 3a and 3b, the basic operation of the length adjustment device 7 is explained below, wherein in Fig.
  • FIG. 3a is a schematic functional diagram 1 and 2 is shown in a first state for setting a maximum effective connecting rod length and in Fig. 3b in a second state for setting a minimum effective connecting rod length.
  • the length adjustment device 7 has a first, lower hydraulic working space 10A and a second, upper hydraulic working space 10B, which can be filled with a hydraulic medium in a preferred manner known in principle from the prior art (see, for example, WO 2016/064193 A1) for changing the effective connecting rod length L.
  • Hydraulic passages 1 A and 1 B and control valve means 14A and 14B and check valve means 15A and 15B incorporated in the control valve recesses 6A and 6B and the check valve recesses 8A and 8B are the hydraulic working spaces 10A and 10B with a hydraulic medium supply line 12, via which the length adjusting device 7 in particular hydraulic medium from the connecting rod bearing in the region of the large connecting rod 3 of the first connecting rod 2 can be supplied, fluidkommuniplasticd connectable.
  • control valve devices 14A and 14B and check valve devices 15A and 15B are configured to supply a hydraulic fluid flow from the
  • the check valve devices 15A and 15B are in particular configured to supply a hydraulic medium flow from the large connecting rod eye 3 via the
  • Hydraulic medium supply line 12 and the hydraulic channels 11A and 1 1 B in the associated hydraulic working space 10A or 10B of the length adjustment device 7 to allow, however, to prevent a return or outflow in the other direction.
  • the control valve devices 14A and 14B are also configured to supply a hydraulic fluid flow from the large connecting rod eye 3 via the hydraulic medium supply line 12 and to allow the hydraulic channels 1 1A and 11 B in the associated hydraulic working space 10A or 10B, but serve primarily for selectively opening and / or blocking a Hydraulikmediumabhnes from the associated hydraulic working space 10A and 10B.
  • control valve devices 14A and 14B each have at least two actuation states, wherein in a first actuation state a return flow from the associated hydraulic working chamber 10A or 10B is blocked and released in a second actuation state.
  • the control valve devices 14A and 14B each have one in a valve chamber 31 A and 31 B by means of a valve spring unspecified here against a likewise unspecified valve seat pressed valve body, which is also not designated in Figs. 3a and 3b. If the valve body is seated against the valve seat or the valve body is pressed against the valve seat by means of the valve spring, the respective control valve device 14A or 14B is closed and a hydraulic fluid drain from the associated hydraulic working chamber 10A or 10B is blocked.
  • valve body can be pushed away from the valve seat in each case by means of a rod-shaped actuating element 16 which is axially displaceable along an actuation axis and thereby lifted off.
  • the control valve device 14A or 14B is opened and a hydraulic medium drain from the associated hydraulic working chamber 10A or 10B is released.
  • the actuating element 16 itself is actuated hydraulically, in particular as a function of an applied oil pressure in a reciprocating piston engine, as described for example in WO 2016/203047, while the control valve devices 14A and 14B can be mechanically actuated.
  • the actuating means 16 could alternatively also be actuated electromechanically or likewise mechanically or the like.
  • the actuating means and the control valve devices 14A and 14B are designed and act in such a way that in each case one of the two control valve devices 14A and 14B is in the first operating state, i. a hydraulic medium return from one of the two hydraulic working spaces 10A or 10B is blocked while the other control valve device 14B or 14A is in the second operating state, so that a hydraulic medium return from the other hydraulic working space 10B or 10A is released.
  • a return via the left hydraulic channel 1 1A blocked and a return via the right hydraulic channel 1 1 B released can with each upstroke by in the direction of the hydraulic cylinder 10 respectively opening valve means 14A and hydraulic fluid is drawn in via the hydraulic medium supply line 12, through the valve devices 14A and 15A, and via the hydraulic lines 1A in the hydraulic cylinder 10, in particular the lower hydraulic working space 10A.
  • the two control valve devices 14A du 14B actuated by means of the actuating element 16, wherein the first control valve means 14A opens, so that the hydraulic medium can flow out of the lower hydraulic working chamber 10A, and the second control valve means 14B closes, so that a return from the upper hydraulic working space 10B is locked in the region of the hydraulic cylinder 10, hydraulic medium is pushed out of the lower working space 10A on each downward stroke, while the upper working space 10B increasingly fills, whereby the effective connecting rod length L is increasingly reduced, in particular to its minimum.
  • FIG. 4 a shows a detail of a section through the connecting rod according to the invention from FIGS. 1 and 2 along the sectional plane YY 'in a second state for setting a minimum effective connecting rod length, and FIG. 4 b in a first state for setting a maximum effective one Pleu length, wherein in these two Figs. 4a and 4b in particular a structure of the control valve devices 14A and 14B is clearly visible.
  • Each of the two control valve devices 14A and 14B has a valve body 20A or 20B designed as a valve ball and inserted into the associated valve recess 6A or 6B 6B, wherein the valve balls within an associated valve space 31A and 31B, respectively, along a valve lift axis, which in this case coincides with a valve-recess longitudinal axis L1 and L2, respectively, from the valve seat 22A and 22B, respectively can be withdrawn.
  • control valve devices 14A and 14B By means of a common, rod-shaped, axially displaceable and biased by a spring element 19 actuating element 16 that is arranged in an actuating recess 13 and by a securing means 24 in shape a closure screw is secured against falling out, the control valve devices 14A and 14B, as previously explained with reference to FIGS. 3a and 3b, simultaneously and alternately operated.
  • the actuator 16 is displaceable perpendicular to the valve lift axes of the control valves 14A and 14B and is not aligned with them as shown schematically in Figs. 3a and 3b.
  • the operating principle is the same.
  • the actuating element 16 does not act directly on the valve bodies 20A and 20B, but in each case on an actuating body 23A or 23B arranged therebetween, by means of which a distance between the actuating element 16 and the valve bodies 20A and 20B is bridged
  • a more advantageous embodiment of the valve seats 22A and 22B is made possible.
  • the actuating element 16 has a plurality of unspecified projections and ramps on which the actuating bodies 23A and 23B can each slide along.
  • closure screws 9 serve in each case as a spring guide element for guiding and supporting the valve springs 21 A and 21 B.
  • Fig. 4a shows the connecting rod 1 and the length adjustment 7 in a second state for setting a minimum effective Pleuelales in which, based on the illustration, upper control valve means 14 B is closed (the valve body 20 B is applied to the valve seat 22 B), while the lower control valve device 14A is opened.
  • Fig. 4b the connecting rod 1 and the length adjustment 7 is shown in a first state for setting a maximum effective connecting rod length, in which the upper control valve device 14B is opened (valve body 20B is lifted from valve seat 22B) while lower control valve device 14A is closed.
  • the associated hydraulic working chamber 10A and 10B Due to the high pressures in the associated hydraulic working chamber 10A and 10B, which can be up to 3,000 bar, it can when switching the length adjustment 7, in particular each case when opening one of the two control valve devices 14A and 14B to a sudden, sudden outflow or "shooting out Come from hydraulic medium with high flow velocities from the associated working space 10A and 10B in the associated hydraulic channel 1 1A and 11B.
  • control valve devices 14A and 14B according to the invention in each case with respect to a mouth of the hydraulic channel 1 1 A and 11 B lying, closed outer wall portion 25A and 25B, which are clearly visible with reference to FIGS. 5 and 6.
  • FIG. 5 shows an enlarged detail of FIG. 4a in the region of the upper control valve device 14B, wherein both the first state for setting the maximum effective connecting rod length and the second state for setting the minimum effective connecting rod length are indicated.
  • FIG. 6 shows a greatly enlarged section of this region from FIG. 5 in a perspective half section from another perspective.
  • the closed outer wall portion 25B forms a flow channel together with the inner wall portion 27A surrounding the mouth opening 29B in the form of an annular space, wherein the flow channel is configured according to the invention in such a way that the hydraulic medium exiting from the hydraulic channel 11 B with a first flow direction S1 is deflected into a second flow direction S2, which in this embodiment runs parallel to the valve recess longitudinal axis L2 ,
  • closed-formed outer wall portion 25 B extends at least partially over the valve body 20 B and the valve spring 21 B and the valve chamber 31 B sleeve-shaped and circumferentially completely surrounds, a direct impact of the hydraulic fluid on the valve body 20 B and the valve spring 21 B be avoided and thus reduce the risk of damage to these components.
  • the hydraulic medium can first be distributed in the annular space, which is completely closed in the circumferential direction, before it can then be deflected by 90 ° in order to flow parallel to the valve recess longitudinal axis L2 in the direction of an inlet opening which is not recognizable and then through it into the valve chamber 31 B to enter. After flowing around the valve body 20 B and actuator body 23 B, the hydraulic medium can then flow further in the direction of the actuating means 16 in a drainage hydraulic passage from the valve chamber 31 B.
  • the hydraulic channel 1 1 B of the control valve device 14 B in particular the last section in the region of the throttle 18 B, opens at an entry angle of 90 ° in the flow channel, in particular at an angle of 90 ° to Ventilaus predominantlyungs longitudinal axis L2.
  • the closed outer wall portion 25B is in this case formed by an outer surface of a cylindrical portion of the plug screw 9 of the valve device 14B and reaches up to a sealing surface 26B, whereby the flow channel is closed on a first side in the axial direction and hydraulic fluid with reduced flow velocity in the direction of the valve body 20B and passed past this in the valve chamber 31 B.
  • a connecting rod according to the invention has a plurality of valve devices and a plurality of hydraulic channels, these can each open at different angles into the associated valve recess.
  • both hydraulic channels 1 1A and 1 1 B which a section of a longitudinal section along a plane oriented perpendicular to a crankshaft axis plane through the connecting rod according to the invention from Figs. 1 and 2 in the region above the valve means 14A and 14B of the length adjustment device 7 above the large connecting rod eye 3, respectively in such a way in the associated valve recess 6A and 6B that a hydraulic channel longitudinal axis of the adjacent to the Ventilausappelung 6A and 6B section intersects the associated VentilausEnglishungs longitudinal axis.
  • the generation of a swirl in the hydraulic medium flow can be avoided.
  • FIG. 9 shows a detail of a partial section through the connecting rod according to the invention from FIGS. 1 and 2 in the region of the lower control valve device 14A along a further sectional plane, it being clearly recognizable in this illustration that the control valve devices 14A and 14B, in particular in each case the closure screw 9 , In their closed outer wall portion 25A and 25B each have an adjacent to a radial shoulder recess 28A and 28B. With each of these, an improved deflection of the hydraulic medium in the direction of the valve body 20A can be achieved.
  • Fig. 10 shows a highly simplified, schematic representation in perspective view substantially obliquely from above or in the Ventilaus Principleung 6A of the lower control valve device 14A, in this view, the four, circumferentially evenly distributed arranged kidney-shaped or atomic depressions 30A well can be seen.
  • kidney-shaped bypass passages or recesses 32A are also visible, which are arranged in the region of the actuating body (not shown here) and are also distributed uniformly in the circumferential direction. These allow an improved flow around the actuating body, in particular a larger volume flow of hydraulic medium when emptying the associated hydraulic working chamber 10A.
  • FIG. 12 shows a section of a first section through a second exemplary embodiment of a length-adjustable connecting rod 40 according to the invention along a first sectional plane XX 'analogous to FIG. 1, and FIG. 13 shows a second section along a second sectional plane YY' analogous to FIG. 1 through the connecting rod 40, wherein functionally identical, but geometrically different from the first embodiment formed components are marked with an apostrophe.
  • valve devices 14A ', 14B', 15A 'and 15B' differ substantially thereby from those of the above-described connecting rod 1 in that the guide unit 33A or 33B or 34A or 34B for the valve spring 21 A 'and 21, respectively B ', in each case not by the screw plug 9 or 9' is formed, but by a bottom of the associated Ventilaus originallyung supported sleeve 33A and 33B and 34A and 34B.
  • closed outer wall sections 25A 'and 25B' of the control valve devices 14A 'and 14B' according to the invention are each formed by an outer wall surface 25A 'or 25B' of a valve seat unit.
  • Hydraulic channel also open into the valve recess such that a
  • Flow channel also be configured to deflect the hydraulic medium in a second flow direction which is perpendicular to the valve recess longitudinal axis of the valve recess.
  • the closed-formed outer portion of the valve device which at least partially surrounds the valve chamber of the valve device, at least partially extend in a plane perpendicular to the Ventilausappeltells longitudinal axis of the valve recess, based on the Ventilausappeltells- longitudinal axis of the Ventilausappelung ,

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lift Valve (AREA)

Abstract

L'invention concerne une bielle à longueur réglable pour un moteur à pistons alternatifs, un moteur à pistons alternatifs et un véhicule, une longueur active de bielle de la bielle pouvant être modifiée et la bielle comportant un équipement hydraulique de réglage de longueur qui comporte un espace de travail hydraulique, un canal hydraulique (11B), un orifice de soupape pourvu d'un axe longitudinal (L2) d'orifice de soupape, et un équipement de soupape (14B) agencé dans l'orifice de soupape pourvu d'un espace de soupape (31B), l'équipement de soupape (14B) étant destiné à ouvrir et/ou à bloquer une évacuation de fluide hydraulique de l'espace de travail hydraulique, et le canal hydraulique (11B) débouchant à une ouverture de débouché dans une section de paroi intérieure (27B) de l'orifice de soupape dans l'orifice de soupape. À cet effet, l'équipement de soupape (14B) comporte au moins une section de paroi extérieure (25B) fermée opposée à l'ouverture de débouché qui entoure au moins partiellement l'espace de soupape (31B) de l'équipement de soupape (14B), la section de paroi extérieure (25B) réalisée de manière fermée de l'équipement de soupape (14B) constituant un canal d'écoulement conjointement avec la section de paroi intérieure (27B) de l'orifice de soupape entourant l'ouverture de débouché, le canal d'écoulement étant configuré pour dévier au moins partiellement du fluide hydraulique sortant du canal hydraulique (11B) avec une première direction d'écoulement (S1) et entrant dans l'orifice de soupape avant l'entrée dans l'espace de soupape (31B) de l'équipement de soupape (14B) dans une deuxième direction d'écoulement (S2) différente de la première direction d'écoulement.
EP19727922.7A 2018-05-08 2019-05-08 Bielle à longueur réglable, moteur à pistons alternatifs et véhicule Withdrawn EP3791055A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ATA50382/2018A AT520821B1 (de) 2018-05-08 2018-05-08 Verfahren zur Herstellung eines längenverstellbaren Pleuels, längenverstellbares Pleuel, Hubkolbenmaschine sowie Fahrzeug
ATA50877/2018A AT521469B1 (de) 2018-10-08 2018-10-08 Längenverstellbares Pleuel, Hubkolbenmaschine sowie Fahrzeug
PCT/AT2019/060156 WO2019213683A1 (fr) 2018-05-08 2019-05-08 Bielle à longueur réglable, moteur à pistons alternatifs et véhicule

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EP3791055A1 true EP3791055A1 (fr) 2021-03-17

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US (1) US11512629B2 (fr)
EP (1) EP3791055A1 (fr)
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EP4278118A1 (fr) * 2021-01-12 2023-11-22 The Oil Gear Company Régulateur haute stabilité
AT524567B1 (de) * 2021-06-14 2022-07-15 Avl List Gmbh Längenverstellbare Pleuelstange mit kompaktem Ablassventil

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US2681644A (en) * 1950-01-05 1954-06-22 Gen Motors Corp Hydraulic lash adjuster
JP4464916B2 (ja) * 2005-12-28 2010-05-19 本田技研工業株式会社 ピストンにおける油圧アクチュエータの制御装置
DE102012020999B4 (de) 2012-07-30 2023-02-23 FEV Europe GmbH Hydraulischer Freilauf für variable Triebwerksteile
US20170339679A1 (en) 2014-10-21 2017-11-23 Lg Electronics Inc. Method for transmitting/receiving d2d signal in wireless communication system and apparatus therefor
DE102015202056A1 (de) 2015-02-05 2016-08-11 Schaeffler Technologies AG & Co. KG Ventilgehäuse für ein bivalentes Schaltventil
AT517217B1 (de) 2015-06-18 2016-12-15 Avl List Gmbh Längenverstellbare pleuelstange
CN108026834B (zh) 2015-06-18 2020-07-24 Avl 里斯脱有限公司 长度可调节的连杆
AT518563B1 (de) * 2016-04-29 2018-01-15 Avl List Gmbh Längenverstellbare pleuelstange
US10954849B2 (en) * 2015-12-14 2021-03-23 Avl List Gmbh Length-adjustable connecting rod with electromagnetically-actuatable switching valve
EP3219954B1 (fr) * 2016-03-14 2018-06-06 ECO Holding 1 GmbH Soupape de commutation destinée à réguler un flux de liquide hydraulique et bielle comprenant une soupape de commutation
AT519156B1 (de) 2016-09-30 2018-11-15 Avl List Gmbh Längenverstellbares Pleuel für eine Hubkolbenmaschine, Hubkolbenmaschine und Fahrzeug
DE102017110380A1 (de) 2017-05-12 2018-11-15 Avl List Gmbh Ablassventil für hohe Drücke
DE102018107076A1 (de) * 2017-06-27 2018-12-27 ECO Holding 1 GmbH Umschaltventil zum Steuern eines Hydraulikflüssigkeitsstroms eines Pleuels für eine Brennkraftmaschine mit variabler Verdichtung sowie Pleuel

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US20210164390A1 (en) 2021-06-03
CN112204236A (zh) 2021-01-08
US11512629B2 (en) 2022-11-29
CN112204236B (zh) 2022-09-09
WO2019213683A1 (fr) 2019-11-14

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