EP3071805A1 - Mécanisme de commande de soupape hydraulique d'un moteur à combustion interne - Google Patents

Mécanisme de commande de soupape hydraulique d'un moteur à combustion interne

Info

Publication number
EP3071805A1
EP3071805A1 EP14793777.5A EP14793777A EP3071805A1 EP 3071805 A1 EP3071805 A1 EP 3071805A1 EP 14793777 A EP14793777 A EP 14793777A EP 3071805 A1 EP3071805 A1 EP 3071805A1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
housing
pressure chamber
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14793777.5A
Other languages
German (de)
English (en)
Other versions
EP3071805B1 (fr
Inventor
Steve Beier
Arno BÄCHSTÄDT
Hendrik THOMANN
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG 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
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3071805A1 publication Critical patent/EP3071805A1/fr
Application granted granted Critical
Publication of EP3071805B1 publication Critical patent/EP3071805B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/16—Silencing impact; Reducing wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/205—Adjusting or compensating clearance by means of shims or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem

Definitions

  • the invention relates to a hydraulic valve brake for a hydraulically variable valve train of an internal combustion engine.
  • the hydraulic valve brake comprises a housing having a housing wall and a housing bottom, a piston extending axially in the housing, whose one end side bounds a hydraulic pressure chamber with the housing wall and the housing bottom and whose other end actuates a gas exchange valve, wherein the housing wall in the region of the pressure chamber of a or several overflow openings is interspersed, the opening cross-sections are controlled by a pressure chamber side end limiting the control edge of the piston.
  • the invention also relates to an internal combustion engine with a hydraulic valve train having such a hydraulic valve brake.
  • Hydraulic valve trains which operate according to the lost-motion principle and in which between the drive side, usually the cam of a camshaft, and the output side, ie the gas exchange valve, a so-called hydraulic linkage with variable Ab Kunststoffbarem hydraulic volume, is a hydraulic valve brake that controls the touchdown speed of the closing gas exchange valve independently of the cam position and limits it to preset values that are acoustically and mechanically acceptable.
  • Hydraulic valve trains each with a generic hydraulic valve brake, are known, for example, from US Pat. No. 6,550,433 B2 and from EP 0 507 521 A1.
  • the pressure chamber which decreases with closing gas exchange valve, is relieved of pressure via one or more overflow openings which run laterally in the housing wall and increasingly reduce their opening cross-sections from a pressure chamber-side control edge of the piston entering the housing become. Since the components of the hydraulic valve brake can not be economically produced with arbitrarily high precision, component tolerances remain, which result in different brake characteristics even within a single production lot.
  • the change of charge with gas exchange valves which close at the same operating point with mutually different Hubverierin to different crank angles with respect to the Kolbentot is, but affects the performance and emissions behavior of the internal combustion engine.
  • the present invention has for its object to provide with simple structural means Vorrausgueen for an improved performance of an internal combustion engine with hydraulic valve train and a hydraulic valve brake of the type mentioned.
  • This object is achieved in that the axial distance of the control edge of the retracted completely in the housing piston is adjusted to the housing bottom by means of a spacer of predetermined thickness.
  • This setting significantly reduces and ideally eliminates the effects of component tolerances that significantly affect the brake characteristics of the valve brake. Because shortly before the placing of the gas exchange valve whose delay curve at constant hydraulic fluid viscosity is highly dependent on the course of coverage of the controlled by the piston control edge opening cross-sections in the housing wall.
  • Valve brakes set in accordance with the invention are suitable not only for valve trains with (automatic) hydraulic valve clearance compensation, but also for valve drives with (manual) mechanical valve clearance compensation, in which case large motors with hydraulically variable valve train are in focus in the latter case.
  • the overlap profile of the piston control edge and opening cross-section (s) merely has an offset around the (uniformly set) valve clearance. Because in this case, the piston and the decisive for the axial distance housing bottom are spaced around the valve clearance when the gas exchange valve closes.
  • the adjustment of the axial distance between the piston control edge and the housing bottom can be done in various ways.
  • an adjustment is provided in discrete thickness graduations of the spacer, wherein the respective thickness is predetermined as a result of a previous test or measurement of the delay course of the unadjusted valve brake and accordingly removed the spacer of a group sorting and paired with the valve brake.
  • the spacer can then be joined either firmly to the housing or fixed to the piston.
  • the spacer causes in the path-time course of the retracting into the valve brake piston, that the cross sections of the overflow openings are covered only at a larger piston travel of the piston control edge.
  • spacer is not necessarily limited to a single part, but may also include a group of two or more parts, which are then summed up as stacks of the predetermined thickness. Due to the variety of possible combinations, the group sorting can be limited to a few individual thicknesses and, in the limiting case, to a single thickness in this case.
  • the spacer may be integrally formed as a non-separate part as a projection of the piston on the pressure chamber side end face or as a projection of the housing on the housing bottom.
  • the axial distance can then be adjusted by machining the projection thickness.
  • Figure 1 is a schematic representation of a hydraulically variable valve drive according to the prior art
  • Figure 2 is a schematic representation of a hydraulic valve train with mechanical valve clearance compensation and inventive valve brake
  • Figure 4 is a schematic diagram for the dimensional predetermination and assignment of a spacer
  • FIG. 5 shows the valve brake according to Figures 2 and 3 in an enlarged view
  • FIG. 6 shows a simplified diagram for the check of the set valve brake
  • FIG. 7 is a longitudinal sectional view of the assembled valve brake in a constructive embodiment; tion;
  • Figure 8 shows the housing according to Figure 7 as a single part in longitudinal section; 9 shows the detail Z according to FIG. 7
  • Figure 1 shows the basic structure of a known hydraulic valve drive for variable-stroke actuation of a valve spring 1 in the closing direction kraftbeaufschlagten gas exchange valve 2 in the cylinder head 3 of an internal combustion engine.
  • the following components are shown:
  • a non-return valve 1 1 opening in the direction of the medium-pressure space, via which the medium-pressure space is connected to the lubricant circuit of the internal combustion engine
  • the variability of the valve lift is generated by the fact that the high-pressure space 8 between the master piston 5 and the slave piston 6 'acts as a so-called hydraulic linkage, the hydraulic volume displaced by the master piston proportional to the stroke of the cam 4, neglecting leaks, depending on the Opening time and the opening duration of the hydraulic valve 7 in a first, the slave piston acting on sub-volume and in a second, in the medium-pressure chamber 9 including piston accumulator 10 and in the low-pressure chamber 12 outflowing partial volume is split.
  • the slave piston 6 ' is equipped with a hydraulic valve brake 14', which reduces the contact speed of the closing gas exchange valve 2 decoupled from the movement of the cam 4 to a mechanically and acoustically acceptable level.
  • the valve brake is a throttle gap, which is formed during the final closing phase of the gas exchange valve by the overlap of a cylindrical projection 15 on the pressure chamber side end face of the slave piston with an overflow 16 which extends concentrically to the slave piston housing wall 17 ' ,
  • Figure 2 shows the slave side of a hydraulically variable valve train of a large engine, the gas exchange valves 2 are actuated via rocker arm 18 with mechanical valve clearance compensation.
  • the highly schematic representation is with respect to the valve train on the hydraulic valve brake 14 with housing 19 and slave piston, hereinafter referred to as piston 6, reduced.
  • the hollow-cylindrical housing with a housing wall 17 and a housing bottom 20 serves to guide the piston traveling axially therein, one end of which with the housing wall and the housing bottom defining a hydraulic pressure chamber 21.
  • the other end of the piston actuates the gas exchange valve 2 by means of the mechanical valve clearance compensation device in the form of a valve clearance adjustment screw 22 in the rocker arm.
  • overflow openings 23 and 24 via which the pressure chamber 21 communicates with the sensor-side hydraulic system (not shown here) run (see FIG. 1).
  • the overflow opening 23 serves with a relatively large opening cross-section as the main flow opening, via which, when the piston 6 moves in and out, the lowest possible volume flow reaches and leaves the pressure chamber.
  • the overflow opening 24 forms with a relatively small opening A cross section of the flow restrictor, over which the pressure chamber in the final closing phase of the gas exchange valve 2 can relieve only under significant delay of the retracting piston.
  • the control of the opening cross-sections via a control edge 25 of the piston, which is formed in the simplified representation by the peripheral edge between the outer surface of the piston and the pressure chamber side end face.
  • the illustration shows the piston 6 in fully retracted in the housing 19 position in which the piston during the valve clearance adjustment on the between see the adjusting screw 22 and the valve-side end face of the piston measured valve clearance L is.
  • the valve clearance is largely or completely shifted to the pressure chamber side end side.
  • the axial distance between the piston control edge 25 and the housing bottom 20 is adjusted according to the invention by means of a spacer 26, which influences the deceleration curve of the retracting into the housing piston so that all valve brakes of the internal combustion engine have substantially the same braking characteristics and that accordingly all gas exchange valves 2 of the internal combustion engine close with about the same stroke course.
  • FIGS. 3a-c show the (still) unadjusted hydraulic valve brake 14 with three different retraction positions of the piston 6 during the basic measurement of the course of movement s (t).
  • the temporal stroke course of the piston acted upon by a defined force is detected until it reaches the housing bottom 20.
  • the measurement result is shown very simplified in Figure 4 based on the curve with thick line width.
  • the upper branch of the curve with a large gradient, ie with a comparatively high closing speed of the gas exchange valve 2 3a corresponds to the piston position in Figure 3a until the pressure chamber 21 can still largely unrestricted over the main flow opening 23 relieve.
  • the subsequent branch of the curve with medium gradient, ie with a comparatively average closing speed corresponds to the piston position in Figure 3b, wherein the piston control edge 25, the main flow opening already completely covered and the pressure relief mainly only via the throttle flow opening 24 takes place.
  • the lower curve branch with a small gradient, ie with low closing speed corresponds to the piston position in Figure 3c, wherein the piston control edge completely covers both the main flow opening and the throttle flow opening and the pressure relief only via leakage gaps and ggfls. Further, not shown here Drosselstromöffnun- conditions in the housing bottom 20 is carried out.
  • the measured curve of a relatively “slow” valve brake is more in line with one of the right reference curves, so that this valve brake is assigned a spacer with a greater thickness than a relatively “fast” valve brake, which more closely matches one of the left reference curves and their course of motion already closer to the default setting.
  • Figure 5 shows the valve brake 14 with the thus sorted and mounted spacer 26, by means of which the axial distance h between the piston control edge 25 and the housing bottom 20 is set offset by the predetermined thickness d with respect to the unconfined valve brake.
  • FIGS. 7 to 9 show various views of an engineered example of a hydraulic valve brake 14 according to the invention, which actuates a gas exchange valve 2 of a large engine with a mechanical valve clearance adjustment by means of a rocker arm 18 in accordance with FIG.
  • the screwed by means of an external thread 27 in the cylinder head 3 of the engine housing 19 of the valve brake comprises a tubular housing wall 17 and a side of the pressure chamber 21 joined housing bottom 20 which is formed by a valve seat 28 with a check valve 29 inserted therein.
  • the axially displaced in the housing and secured for transport purposes by means of a snap ring 30 against complete extension piston 6 is hollow cylindrical with a gas exchange valve side end face forming piston crown 31.
  • the pressure chamber-side end face of the piston is provided with a recess 32 in the form of a countersink, in which a serving as a spacer 26 shim with a predetermined thickness d is fixed by means of a longitudinal compression bandage.
  • a bore 33 passing through the piston crown serves as a vent and - in the case of a leak-prone longitudinal compression bandage - as pressure relief of the piston interior.
  • the housing wall 17 is penetrated in each case by four main flow openings 23 and throttle flow openings 24 in the form of bores via which the pressure space 21 communicates with the sensor-side hydraulic system (not illustrated here), as explained above.
  • the main flow openings extend in a first transverse plane and the significantly smaller flow restrictor openings extend in a second transverse plane, which is offset from the first transverse plane in the retraction direction of the piston 6.
  • the valve receptacle 28 comprises an outer annular collar 34 which is inserted in a pressure-reducing means 35 of the housing wall 17 and clamped by means of the screw 27 against a shoulder 36 in the cylinder head 3, and a relative to the annular collar in the direction of the recess 32 projecting hollow cylinder portion 37.
  • the non-return valve 29 comprises a valve carrier 38 likewise inserted in the valve receptacle 28 and having a valve ball 40 spring-loaded therein against a valve seat 39. This opens in the direction of the pressure chamber 21 and controls a further overflow opening 41, via which the pressure chamber also communicates the encoder-side hydraulic system communicates to initialize the extension of the piston 6 when opening the gas exchange valve 2.
  • shim 26 of the hydraulic medium is transferred into the pressure chamber initially via beads 42 on the annular end face 43 of the hollow cylinder portion.
  • the opening cross-sections of the main and throttle flow openings 23 and 24 are controlled by the control edge 25 of the piston 6 passing over it and are all in the illustrated, completely retracted piston position as well as in the piston position extended by the set valve clearance L according to FIG locked.
  • the annular collar 34 is penetrated by a permanently open, further throttle flow opening 44 whose hydraulic resistance ultimately determines the touchdown speed of the gas exchange valve 2.
  • the unadjusted valve brake 14 is provided with a dummy shim (not shown) of known thickness, so that in the above-described basic measurement (see Figures 3a-c) of the piston with the dummy shim on the ring front side and not on the Ring collar of the valve seat touches down.
  • the dummy shim to be disassembled according to the basic measurement may, if necessary, be provided with a circumferential O-ring which, on the one hand, holds the dummy shim easily removable in the recess 32 and, on the other hand, seals the pressure chamber 21 with respect to the bleed bore 33.
  • the axial distance h is then adjusted by the thickness d of the adjusting disk 26 such that all hydraulic valve brakes 14 of the internal combustion engine have substantially the same braking characteristics and accordingly all the gas exchange valves 2 are largely uniform within a very small one Close the crank angle range.
  • shims 26 are provided with five different thicknesses in each case 0.1 mm gradation in the embodiment shown here.
  • the spacer 26 is pressed against its outer casing 45 in the inner casing 46 of the recess 32 of the piston 6.
  • alternative fasteners may be provided.
  • the spacer may be provided with a central bore, which is pressed on the one hand on a pin-like projection of the then solid piston or through the other a pin or screw is guided, which adds the spacer with the piston.
  • Ring face of the valve seat further throttle flow opening Outer jacket of the spacer Inner jacket of the recess

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne un frein de soupape hydraulique (14) destiné à un mécanisme de commande de soupape hydraulique d'un moteur à combustion interne. Le frein de soupape comprend un boîtier (19) comportant une paroi de boîtier (17) et un fond de boîtier (20), et un piston (6) qui se déplace axialement dans le boîtier, dont une face frontale délimite avec la paroi du boîtier et le fond du boîtier une chambre de pression hydraulique (21) et dont l'autre face frontale actionne une soupape d'échange de gaz (2). La paroi du boîtier est traversée au niveau de la chambre de pression (21) par un ou plusieurs orifices de trop-plein (24, 25) dont les sections transversales sont commandées par un bord de commande (25) du piston délimitant la face frontale du côté chambre de pression. Selon l'invention, la distance axiale (h) entre le bord de commande du piston complètement enfoncé dans le boîtier et le fond du boîtier est réglée au moyen d'une pièce d'écartement (26) d'une épaisseur (d) prédéterminée.
EP14793777.5A 2013-11-22 2014-10-08 Mécanisme de distribution hydraulique d'un moteur à combustion interne Active EP3071805B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013223926.2A DE102013223926B4 (de) 2013-11-22 2013-11-22 Hydraulische Ventilbremse für einen hydraulisch variablen Ventiltrieb und Verfahren zur Einstellung der hydraulischen Ventilbremse
PCT/DE2014/200539 WO2015074652A1 (fr) 2013-11-22 2014-10-08 Mécanisme de commande de soupape hydraulique d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP3071805A1 true EP3071805A1 (fr) 2016-09-28
EP3071805B1 EP3071805B1 (fr) 2017-12-13

Family

ID=51865962

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14793777.5A Active EP3071805B1 (fr) 2013-11-22 2014-10-08 Mécanisme de distribution hydraulique d'un moteur à combustion interne

Country Status (5)

Country Link
US (2) US9957856B2 (fr)
EP (1) EP3071805B1 (fr)
CN (1) CN105765181B (fr)
DE (1) DE102013223926B4 (fr)
WO (1) WO2015074652A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3156619B1 (fr) * 2015-10-13 2018-06-06 C.R.F. Società Consortile per Azioni Système et procédé pour actionner de manière variable une soupape d'un moteur à combustion interne, avec un dispositif pour amortir les oscillations de pression
DE102016218918B4 (de) * 2016-09-29 2018-09-13 Schaeffler Technologies AG & Co. KG Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
DE102019128826B4 (de) * 2019-10-25 2022-09-29 Schaeffler Technologies AG & Co. KG Hydraulikeinheit einer elektrohydraulischen Gaswechselventilsteuerung

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JPH0396607A (ja) * 1989-09-08 1991-04-22 Nissan Motor Co Ltd エンジンの弁作動装置
US5127375A (en) 1991-04-04 1992-07-07 Ford Motor Company Hydraulic valve control system for internal combustion engines
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US6412457B1 (en) 1997-08-28 2002-07-02 Diesel Engine Retarders, Inc. Engine valve actuator with valve seating control
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ITTO20020234A1 (it) * 2002-03-15 2003-09-15 Fiat Ricerche Motore pluricilindrico a combustione interna con dispositivo idraulico a controllo elettronico per l'azionamento variabile delle valvole e d
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CN101765705B (zh) * 2007-03-16 2012-11-28 雅各布斯车辆系统公司 具有铰接摇臂和摇杆轴安装壳体的发动机制动器
FI124120B (fi) * 2008-07-31 2014-03-31 Wärtsilä Finland Oy Ohjausjärjestely mäntämoottorissa
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DE102010020755A1 (de) * 2010-05-17 2011-11-17 Schaeffler Technologies Gmbh & Co. Kg Verfahren sowie Steuereinrichtung zur Ermittlung einer Viskositäts-Kenngröße eines Motoröls
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Also Published As

Publication number Publication date
US9957856B2 (en) 2018-05-01
US10247061B2 (en) 2019-04-02
US20160273420A1 (en) 2016-09-22
WO2015074652A1 (fr) 2015-05-28
EP3071805B1 (fr) 2017-12-13
CN105765181A (zh) 2016-07-13
US20180230868A1 (en) 2018-08-16
DE102013223926B4 (de) 2018-02-08
CN105765181B (zh) 2018-11-13
DE102013223926A1 (de) 2015-05-28

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