EP1892387A1 - Verfahren und Vorrichtung zur Steuerung eines schaltbaren Schlepphebels - Google Patents

Verfahren und Vorrichtung zur Steuerung eines schaltbaren Schlepphebels Download PDF

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Publication number
EP1892387A1
EP1892387A1 EP07075619A EP07075619A EP1892387A1 EP 1892387 A1 EP1892387 A1 EP 1892387A1 EP 07075619 A EP07075619 A EP 07075619A EP 07075619 A EP07075619 A EP 07075619A EP 1892387 A1 EP1892387 A1 EP 1892387A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
gallery
lash adjuster
hla
engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07075619A
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English (en)
French (fr)
Inventor
Nick John Hendriksma
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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP1892387A1 publication Critical patent/EP1892387A1/de
Withdrawn legal-status Critical Current

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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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • 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
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves

Definitions

  • the present invention relates to variable valve activation mechanisms for combustion valves of internal combustion engines; more particularly, to methods and apparatus for controllably supplying activating engine oil to such variable valve activation mechanisms including switchable cam followers; and most particularly, to an improved hydraulic lash adjuster and control scheme for such controllable valve actuation.
  • a typical prior art selective valve deactivation mechanism includes a switchable cam follower such as an articulated two-step deactivation roller finger follower (DRFF) disposed between an engine camshaft lobe and a valve stem.
  • the DRFF includes a hydraulically-actuated lock pin to engage or disengage the articulated members.
  • the lock pin is engaged between the articulated members by a return spring, such that the valve train is in high-lift mode by default at shutdown or other times as desired.
  • the lock pins are disengaged by application of high pressure hydraulic fluid, typically engine oil provided by the engine's oil distribution system to overcome the return spring.
  • the DRFF is pivoted on a hydraulic lash adjuster (HLA) at an end opposite to the valve-engaging end.
  • HLA hydraulic lash adjuster
  • the HLA is mounted rotatably about its axis in a residence bore in the engine, typically in the engine head.
  • the HLA is supplied with engine oil from a molded or bored engine gallery to feed the lash adjuster mechanism therein, and oil also flows from the HLA to the DRFF through a central opening in the ball head of the HLA and a mating passage in the DRFF.
  • the lock pin spring overcomes the oil pressure and the DRFF is in high-lift mode.
  • the oil pressure is increased via a regulating oil control valve (ROCV) to a higher pressure sufficient to cause the lock pin to be retracted, placing the DRFF in low-lift or no-lift mode.
  • the engine oil gallery thus doubles as a switching gallery and an oil supply gallery for top engine functions such as camshaft bearings.
  • the function may be provided by a combination of a three-way on/off valve in the switching gallery coupled to a pressure relief valve and an in-line flow restrictor to maintain low switching pressure at between about 0.3 bar and about 0.8 bar.
  • this approach can be difficult to package on existing engine block or head arrangements because of the common oil gallery shared by the HLAs and the cam bearings.
  • HLA arrangement that may be packaged in an existing head wherein the camshaft bearings are lubricated via an existing first oil gallery and the HLA switching and lash adjusting functions are satisfied, at least in part, from a second, independently controlled oil gallery remote from the first oil gallery, and wherein the first and second galleries are readily purged of air.
  • an internal combustion engine is equipped to supply the camshaft bearings with pressurized oil via a first dedicated oil gallery independently of the hydraulic lash adjusters and any valve deactivation devices which are supplied from a second dedicated oil gallery.
  • the galleries are connected and a small-orifice flow restriction is placed either in a connecting passage between the first and second galleries or within the HLAs themselves.
  • the primary engine oil gallery is as in the prior art, to minimize required retooling of engine molds.
  • An improved hydraulic lash adjuster, formed in accordance with the invention is identical with a prior art HLA except that the prior art annular oil distribution groove in the outer surface of the body is eliminated to prevent communication of the primary engine oil gallery with the HLA.
  • the secondary gallery is formed remotely from the first oil gallery in the HLA residence bore in the engine, and the HLA is prevented from rotating within the residence bore.
  • the HLA can communicate for actuation with only the new, second oil gallery.
  • a first prior art oil supply system 100 includes a pressurizing pump 102 which draws intake hydraulic fluid 104 from a sump 106.
  • Fluid 104 is typically engine oil and sump 106 is typically an engine crankcase.
  • Pressurized output oil 108 from pump 102 is directed through a regulating oil control valve (ROCV) 110 which regulates pressure in a conventional oil gallery 112 to about 0.5 bar.
  • Pressurized oil is supplied from gallery 112 to cam bearings 114 and to a conventional hydraulic lash adjuster 116 disposed rotatably about its axis in a residence bore 115 in an engine head 117.
  • ROV regulating oil control valve
  • An outer annular groove 119 in HLA body 120 coincides with first port 118, and HLA 116 thus is free to rotate about its longitudinal axis while oil is supplied to port 118 from groove 119 at any angular orientation of the HLA.
  • ROCV 110 is controlled by an engine control module (not shown).
  • the "normal" ("low") operating pressure 134 is about 0.5 bar.
  • ROCV 110 opens to permit higher oil pressure 136 (which may be the same as pressure 108 or not) to flow to HLA 116 and thence into the DRFF.
  • higher oil pressure is also felt by cam bearings 114.
  • a low oil pressure 134 required for full valve activation can rob the cam bearings 114 of adequate oil flow.
  • a second prior art oil supply system 200 includes pressurizing oil pump 102 which draws intake oil 104 from sump 106, as in prior art system 100 (FIG. 1a). Pressurized output oil 108 from pump 102 is fed through a first flow restriction 240 into a conventional oil gallery 112 at an unregulated intermediate pressure 242 sufficient to lubricate cam bearings 114 and fill the low-pressure reservoir 228 and lash adjusting mechanism 230 of a second prior art HLA 216 disposed in a residence bore 215 in an engine head 217.
  • a second (switching) gallery 244 is provided in engine head 217 in parallel with conventional gallery 112 and communicates with a switchable cam follower such as DRFF 246 via a passage 248 independent of low-pressure reservoir 228.
  • first flow restriction 240 is simply a small-diameter port where the oil feed passes through the engine head gasket.
  • a three-way on/off valve 250 controlled by an engine control module (not shown) governs flow of oil into switching gallery 244. Oil flow into switching gallery 244 is either at high pressure 108 or a very low pressure 254. Although the three-way valve 250 is only either open or closed, a bypass "bleed" 252 preferably is provided to maintain a slight charge pressure 254 in switching gallery 244, as is desirable for some valve deactivation systems.
  • Prior art system 200 desirably divorces the lash adjusting and cam bearing lubrication functions from the valve deactivation functions.
  • the presence of conventional oil gallery 112 where formed in existing engine heads leaves little room for the addition of a switching gallery 244 adjacent thereto.
  • a longer HLA is required, having in some designs a two-piece plunger, and the volume of the low-pressure reservoir is quite small, making an engine equipped with this system vulnerable to cold-starting clatter.
  • a third prior art oil supply system 300 includes pressurizing oil pump 102 which draws intake oil 104 from sump 106, as in prior art systems 100 and 200 (FIGS. 1a and 2a).
  • pressurized output oil 108 from pump 102 is fed through a first flow restriction 240 into a conventional oil gallery 112 at an unregulated intermediate pressure 242 sufficient to lubricate cam bearings 114.
  • the HLA is entirely divorced from gallery 112.
  • a second gallery 244 is provided in engine head 217 adjacent conventional gallery 112 and supplies an HLA 316 similar to HLA 116, filling the low-pressure reservoir and lash adjusting mechanism via a single feed.
  • a three-way on/off valve 350 governs flow of oil into switching gallery 244.
  • Oil flow into switching gallery 244 is either at low pressure 334 (FIG. 3, DRFF engaged for high valve lift)) or high pressure 108 (FIG. 4, DRFF disengaged for no or low valve lift).
  • three-way valve 350 is only either open or closed, a second flow restriction 352 around valve 350 and a pressure relief valve 356 maintains low pressure 334 in switching gallery 244, preferably about 0.5 bar similar to pressure 134 as in first system 100 for lash adjusting functions of HLA 316.
  • valve 350 opens to oil pressure 108 and closes to relief valve 356.
  • Third prior art system 300 achieves the objective of divorcing cam bearing lubrication from HLA activities while utilizing a substantially unmodified production HLA such as HLA 116 (FIGS. 1a and 1b).
  • HLA 116 a substantially unmodified production HLA
  • the presence of the conventional oil gallery 112 where formed in existing engine heads leaves little room for the addition of a switching gallery 244 adjacent thereto.
  • the first and second galleries and the HLA are not readily purged of air and may have dead legs at various points therein.
  • a first improved oil supply system 400 in accordance with the invention is similar to but improves upon prior art system 300.
  • Improved system 400 includes pressurizing oil pump 102 which draws intake oil 104 from sump 106 as in prior art system 300 (FIGS. 3 and 4).
  • pressurized output oil 108 from pump 102 is fed through a first flow restriction 240 into a conventional oil gallery 112 at an unregulated intermediate pressure 242 sufficient to lubricate cam bearings 114.
  • HLA 416 is entirely divorced from gallery 112.
  • a second gallery 244 is provided in engine head 217 in addition to the conventional gallery 112 and supplies an improved HLA 416 similar to conventional HLA 116, filling the low-pressure reservoir and lash adjusting mechanism via a single feed.
  • HLA 416 differs from HLA 116 in having no annular oil supply groove 119 formed in the unfeatured cylindrical exterior of HLA body 420; and further, HLA 416 is prevented from free rotation in the HLA residence bore 215 (FIG. 2b) in engine head 217 by inclusion of an anti-rotation flat or other obvious mechanical preventer as known in the art.
  • the HLA fill port 418 in body 420 is inaccessible to the conventional oil gallery 112 disposed in an existing head in which HLA 416 might be retro-fitted and is positioned to communicate with only second gallery 244 for all HLA oil supply functions.
  • a three-way on/off valve 350 governs flow of oil into switching gallery 244. Oil flow into switching gallery 244 is either at low pressure 434 (FIG. 6, DRFF engaged for high valve lift)) or high pressure 108 (FIG. 7, DRFF disengaged for no or low valve lift).
  • Switching gallery 244 is open to pressure relief valve 356. Referring to FIG. 7, when high pressure oil to HLA 416 is desired, valve 350 opens switching gallery 244 to a second position to oil pressure 108 and closes switching gallery 244 to relief valve 356.
  • First improved oil supply system 400 achieves the objective of divorcing cam bearing lubrication from HLA activities while utilizing a minimally modified production HLA such as HLA 116 (FIGS. 1a and 1b), and while accommodating a conventional oil gallery passage in a current head.
  • System 400 also provides several other important advantages not available in the prior art.
  • the conventional oil gallery 112 and the switching oil gallery 244 are formed in engine head 217 on opposite sides of HLA 416. This arrangement makes it relatively easy to form the two galleries in an existing engine head mold with minimal required retooling of the mold.
  • the arrangement also provides maximal flow separation of the two galleries within the residence bore of the HLA and thus minimizes hydraulic cross-talk between the two galleries, whereas in the prior art (FIG. 2b) the two galleries, being adjacent and on the same side of the residence bore, are separated by only a few millimeters of bore wall.
  • a second improved oil supply system 500 in accordance with the invention is similar to first improved system 400, differing only in the implementation of a pressure reducing flow restriction between the two galleries.
  • system 500 the ends of galleries 112,244 are not joined except through the final HLA in an engine bank; thus there are still no dead flow legs.
  • the pressure reducing flow restrictions are located in the body of the HLA rather than in connector 453 as in system 400.
  • Each HLA 516 (FIG. 8) is identical to HLA 416 except that an orifice or flow restriction 552 is provided through HLA body 520 in communication with conventional oil gallery 112.
  • oil flows from the conventional gallery through the flow restriction into the HLA low pressure chamber and switching gallery and eventually out the pressure relief valve.
  • the pressure relief valve and flow restrictors are sized to regulate the pressure in the switching gallery to the desired 0.5 bar pressure. This eliminates having to manufacture connector 453 containing restriction 452 of system 400.
  • Air in gallery 112 is purged into low-pressure reservoir 528 and thence out of the HLA via tip opening 532. Continued purging from gallery 112 through HLA 516 drives air in port 518 and switching gallery 244 out through three-way valve 350 and relief valve 356 (FIGS. 8 and 9).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP07075619A 2006-08-14 2007-07-20 Verfahren und Vorrichtung zur Steuerung eines schaltbaren Schlepphebels Withdrawn EP1892387A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/503,776 US20080035085A1 (en) 2006-08-14 2006-08-14 Method and apparatus for controlling a switchable cam follower

Publications (1)

Publication Number Publication Date
EP1892387A1 true EP1892387A1 (de) 2008-02-27

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102121409A (zh) * 2011-04-08 2011-07-13 力帆实业(集团)股份有限公司 一种发动机右曲轴箱润滑油路
DE102016106885A1 (de) 2015-04-28 2016-11-03 Ford Global Technologies, Llc Externe Ölnut auf einer hydraulischen Spieleinstellvorrichtung
US9765656B2 (en) 2015-06-15 2017-09-19 Ford Global Technologies, Llc Hydraulic circuit for valve deactivation
US10465571B2 (en) 2017-06-13 2019-11-05 Ford Global Technologies, Llc Oil flow system for engine cylinder deactivation
US10544710B2 (en) 2015-03-23 2020-01-28 Ford Global Technologies, Llc Hydraulic circuit for valve deactivation
WO2021064155A3 (en) * 2019-10-04 2021-05-14 Eaton Intelligent Power Limited Hydraulic circuit and valve

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US20190309663A9 (en) 2008-07-22 2019-10-10 Eaton Corporation Development of a switching roller finger follower for cylinder deactivation in internal combustion engines
US9228454B2 (en) 2010-03-19 2016-01-05 Eaton Coporation Systems, methods and devices for rocker arm position sensing
US11181013B2 (en) * 2009-07-22 2021-11-23 Eaton Intelligent Power Limited Cylinder head arrangement for variable valve actuation rocker arm assemblies
US9885258B2 (en) 2010-03-19 2018-02-06 Eaton Corporation Latch interface for a valve actuating device
JP2015534005A (ja) * 2012-11-05 2015-11-26 イートン コーポレーションＥａｔｏｎ Ｃｏｒｐｏｒａｔｉｏｎ 内燃機関における気筒休止のためのスイッチングローラーフィンガーフォロワーの開発
JP6273837B2 (ja) 2013-12-27 2018-02-07 マツダ株式会社 弁停止機構の油圧供給装置
US9790820B2 (en) * 2014-10-10 2017-10-17 Schaeffler Technologies AG & Co. KG Switching oil gallery de-aeration
GB2539937B (en) 2015-07-01 2019-07-24 Ford Global Tech Llc A combined oil filter and restrictor assembly
KR102371063B1 (ko) 2017-11-20 2022-03-07 현대자동차주식회사 가변밸브기구 제어 시스템 및 그것을 구성하는 오일 컨트롤 밸브
US10731519B2 (en) * 2018-09-19 2020-08-04 Hyundai Motor Company Control system and control method for hydraulic variable valve
CN112211689B (zh) * 2020-10-14 2022-03-29 天津大学 基于配气凸轮的电液式全可变气门机构的控制方法

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EP1568851A1 (de) * 2004-02-25 2005-08-31 Delphi Technologies, Inc. Hydraulisches Ventilspielausgleichselement

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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102121409A (zh) * 2011-04-08 2011-07-13 力帆实业(集团)股份有限公司 一种发动机右曲轴箱润滑油路
CN102121409B (zh) * 2011-04-08 2012-07-04 力帆实业(集团)股份有限公司 一种发动机右曲轴箱润滑油路
US10544710B2 (en) 2015-03-23 2020-01-28 Ford Global Technologies, Llc Hydraulic circuit for valve deactivation
DE102016106885A1 (de) 2015-04-28 2016-11-03 Ford Global Technologies, Llc Externe Ölnut auf einer hydraulischen Spieleinstellvorrichtung
CN106089347A (zh) * 2015-04-28 2016-11-09 福特环球技术公司 液压间隙调节器上的外部油槽
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CN106089347B (zh) * 2015-04-28 2020-01-17 福特环球技术公司 液压间隙调节器上的外部油槽
US9765656B2 (en) 2015-06-15 2017-09-19 Ford Global Technologies, Llc Hydraulic circuit for valve deactivation
US10184364B2 (en) 2015-06-15 2019-01-22 Ford Global Technologies, Llc Hydraulic circuit for valve deactivation
US10465571B2 (en) 2017-06-13 2019-11-05 Ford Global Technologies, Llc Oil flow system for engine cylinder deactivation
US10774698B2 (en) 2017-06-13 2020-09-15 Ford Global Technologies, Llc Oil flow system for engine cylinder deactivation
WO2021064155A3 (en) * 2019-10-04 2021-05-14 Eaton Intelligent Power Limited Hydraulic circuit and valve

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