WO2011040997A1 - Procédé de lubrification de bossage d'arbre à came de frein moteur - Google Patents

Procédé de lubrification de bossage d'arbre à came de frein moteur Download PDF

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Publication number
WO2011040997A1
WO2011040997A1 PCT/US2010/036121 US2010036121W WO2011040997A1 WO 2011040997 A1 WO2011040997 A1 WO 2011040997A1 US 2010036121 W US2010036121 W US 2010036121W WO 2011040997 A1 WO2011040997 A1 WO 2011040997A1
Authority
WO
WIPO (PCT)
Prior art keywords
follower
oil
flat face
oil passage
improvement according
Prior art date
Application number
PCT/US2010/036121
Other languages
English (en)
Inventor
Michael D. Bartkowicz
Qianfan Xin
Original Assignee
International Engine Intellectual Property Company, Llc
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 International Engine Intellectual Property Company, Llc filed Critical International Engine Intellectual Property Company, Llc
Priority to US13/498,138 priority Critical patent/US20120174887A1/en
Priority to EP10820964A priority patent/EP2483533A1/fr
Priority to BR112012007065A priority patent/BR112012007065A2/pt
Priority to CN2010800547992A priority patent/CN102656343A/zh
Publication of WO2011040997A1 publication Critical patent/WO2011040997A1/fr

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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • 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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
    • 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
    • F01L2810/00—Arrangements solving specific problems in relation with valve gears
    • F01L2810/02—Lubrication

Definitions

  • the invention relates to engine braking incorporating cam operated engine braking exhaust valves open into the engine cylinders.
  • a plurality of engine-braking cam lobes are provided on an engine cam that normally operates the engine exhaust valves.
  • a plurality of engine -braking followers or tappets respectively ride on the cam lobes and are at least partially contained in brake housings containing oil. Mechanical force from the camshaft lobes is converted to hydraulic pressure inside the brake housings by providing lift to the followers.
  • the followers act as master pistons that are driven into the brake housings. Hydraulic controls that are fluidly connected to the oil in the brake housing determine whether the movement of the followers into the oil has a hydraulic pressure effect on the oil contained in the brake housings or no effect.
  • the movement of the followers into the brake housings increases hydraulic pressure which causes movement of slave pistons moving out of their respective brake housings.
  • the slave pistons are operatively engaged to a engine -braking exhaust valves to open a the engine cylinders to the exhaust manifold.
  • the present inventors have recognized that the cam lobe and follower contact area is difficult to lubricate. When the loads and sliding speed at the contact area is high, significant contact temperature can be developed which reduces lubrication effectiveness. Because the contact geometry between the cam lobe and the flat face of the follower is counter-formal (i.e., unlike the conformal contact area in engine bearings), the contact pressure is much higher in the cam lobe/follower contact area and the oil film thickness is much lower than that in engine bearings.
  • the present inventors have recognized that Hertzian contact stress, oil entraining velocity, oil film thickness and flash temperature are all important for the cam lobe/follower friction and wear.
  • Lubricant supply can be very important for the cam lobe/follower contact area and may change positively the behavior of the wear characteristic and affect the lubrication mechanism of the contact area.
  • One exemplary embodiment of the invention is incorporated into an engine braking system of the type wherein a cam lobe lifts a follower by direct contact, wherein the follower is at least partially contained in a brake housing containing oil.
  • a slave piston is also at least partially contained in the brake housing, and during engine braking, movement of the follower causes the oil to move the slave piston outward of the brake housing. Movement of the slave piston opens an engine braking exhaust valve to open a flow path between an engine cylinder and an exhaust conduit.
  • the exemplary embodiment of the invention provides an oil passage through the follower to lubricate an interface between a flat face of the follower and the cam lobe with oil from the brake housing.
  • the oil passage has an outlet hole that is open on the flat face of the follower outside of the contact area between the flat face and the cam lobe.
  • the oil passage extends axially through the follower with a first portion and with a second portion extending obliquely from the flat face to intersect with the first portion.
  • an angle between the first portion and the second portion is about 145 degrees.
  • the oil passage includes a first linear portion that extends from an end of the follower along a first direction to an intersecting position within the follower and a second linear portion that extends from the flat face to intersect the first linear portion at the intersecting position, the first and second portions being non-collinear.
  • the first linear portion has a greater diameter than the second linear portion.
  • the follower is arranged to ride directly on a camshaft brake lobe.
  • High pressure lube oil in the brake housing will lubricate the follower to cam lobe interface.
  • the high pressure lube oil should lubricate the follower to cam lobe interface and reduce lube oil flash temperature scuffing.
  • the oil passage can be advantageously drilled through the follower at a location that avoids the highly loaded area or contact area between the follower flat face and the cam lobe.
  • the oil passage through the follower can be offset from the axis of the follower to avoid this contact area. It is anticipated that by avoiding the contact area the outlet hole will not adversely affect the lubricating condition in the highly loaded area.
  • a properly placed outlet hole position can promote the lubricating oil flow for the cam lobe surface.
  • the combination of cam stress, oil flow entrainment, flash temperature, etc. determine the life of the cam lobe-follower surface.
  • the optimum position of the oil passage outlet hole is related to cam rotation direction. Also, if the flat follower axially rotates, the offset hole position will rotate relative to camshaft rotating direction. Accordingly, a guide can be provided to prevent axial rotation of the follower so that the offset outlet hole will be maintained in the optimal position.
  • the lubricated brake cam lobe should allow higher brake pressure to be run for greater brake capability as well as longer follower/cam lobe service life.
  • Another aspect of the invention is not limited to cam/follower activation of engine brake valves but may be useful to any folio was/cam lobe mechanism.
  • the embodiment can be incorporated into an engine having a cam with cam lobes and a plurality of cam followers riding on respective cam lobes.
  • the embodiment provides an enhanced lubrication arrangement for the followers and cam lobes.
  • This aspect provides an oil passage through each of the followers to lubricate an interface between a flat face of each follower and a respective cam lobe.
  • the oil passage can comprise an outlet hole on the flat face that is outside the contact area between the flat face and the cam lobe.
  • the oil passage can include an axial portion extending from an end of each follower opposite the flat face and an oblique portion extending from the outlet hole to the axial portion.
  • the angle between the axial portion and the oblique portion can be about 145 degrees.
  • the axial portion can have a diameter that is greater than the oblique portion.
  • Figure 1 is a schematic diagram of a prior art lost motion engine braking system
  • Figure 2 is a schematic cross-sectional view of a cam lobe and follower arrangement in an engine
  • Figure 3 is a view taken along line 3-3 of Figure 2.
  • Figure 4 is a view taken along line 4-4 of Figure 2 with portions removed to view underlying components.
  • Figure 1 illustrates a portion of an engine 10.
  • the engine includes a camshaft 30 having cam lobes 36.
  • a plurality of tappets or followers 44 respectively ride on the cam lobes 36.
  • the cam lobes are shown as circular for simplicity but would have a protruding lobe such as shown in Figure 1.
  • Each follower 44 is at least partially contained in one of a plurality of brake housings 52.
  • Each brake housing 52 contains oil 54 within an internal oil manifold 55.
  • each follower 44 By force from the rotating lobes 36, each follower 44 is moved in and out of the respective brake housing according to a predetermined profile of a respective lobe 36.
  • the followers 44 act as master pistons.
  • a slave piston 58 is at least partially contained in each brake housing 52 and during an engine braking operation, the slave piston 58 is driven out of the brake housing 52 by hydraulic pressure created within the oil manifold 55 in the brake housing 52 by movement into the brake housing 52 of the respective follower 44 acting as a master piston.
  • a hydraulic control circuit 66 is in fluid communication with the oil manifold 55.
  • the hydraulic control circuit either contains the oil within the oil manifold 55, or relieves the oil manifold 55 of oil pressure to allow movement of the follower 44 into the brake housing 52 to have no hydraulic effect on the slave piston 58.
  • Oil is supplied to the oil manifold 55 by a pump circuit 67.
  • Each slave piston 58 is pressed to a braking exhaust valve 70 that opens each engine cylinder 72 to an exhaust manifold 73.
  • the exhaust valves 70 By opening the exhaust valves 70 to exhaust during engine braking, the engine can be effectively tasked as an air compressor to absorb vehicle kinetic energy to compress air.
  • a more complete description of such engine brake systems can be found for example in U.S. Patents 5,680,841; 6,415,752 and 6,321,701 and published application US20030164153, all herein incorporated by reference to the extent the references are not inconsistent with the present disclosure.
  • FIGS 2-4 illustrate an exemplary embodiment of the invention.
  • a system for lubricating the interface between a modified follower 44a and the cam lobe is provided.
  • the follower 44a is shown in section.
  • An oil path 80 is provided through each follower 44a between the oil manifold 55 within the brake housing 52 and the cam lobe 36.
  • the oil path 80 includes a first portion 84 that extends from a brake housing end 86 of the follower 44a to an intersecting position 88 within the follower 44a, and a second portion 94 that extends from the intersecting position 88 to a flat face 96 of the follower 44a.
  • the first portion 84 extends axially through the follower 44a and the second portion 94 extends at an oblique angle A to the first portion.
  • the angle A comprises about 145 degrees.
  • the first portion 84 defines an inlet hole 84a and the second portion defines an outlet hole 94a.
  • Figure 4 shows the brake housings removed to show the hole 94a at the top of each follower 44a.
  • the first portion 84 can have a greater diameter than the second portion 94.
  • the first portion 84 may be drilled into each follower 44a and the second portion 94 may be laser drilled into each follower 44a to intersect the first portion 84. Based on the reduced diameter, the flow resistance of the second portion 94 would be far greater than the first portion 84 so a precise tuning of the oil flow can be achieved by only the laser drilling of the second portion 94.
  • the outlet hole 94a will be outside an area of contact 100 between the flat face 96 and the lobe 36 so that the presence of the hole in a high contact stress area is not detrimental to the lubrication of the interface or service life of the follower or cam lobe.
  • guides can be provided to prevent the followers from axially rotating so that a predetermined, constant location of the hole 94a can be ensured.

Abstract

L'invention concerne un système de freinage moteur du type dans lequel un bossage de came soulève un suiveur par contact direct, le suiveur étant au moins partiellement contenu dans un logement de frein contenant de l'huile. Un piston esclave est également au moins partiellement contenu dans le logement de frein, et pendant le freinage moteur, le mouvement du suiveur permet à l'huile de déplacer le piston esclave vers l'extérieur. Le mouvement du piston esclave ouvre une valve d'échappement de freinage moteur pour ouvrir une trajectoire d'écoulement entre un cylindre de moteur et un conduit d'échappement. Un passage d'huile au travers du suiveur permet de lubrifier une interface entre une face plate du suiveur et le bossage de came à l'aide de l'huile provenant du logement de frein. Le passage d'huile a un trou de sortie qui est ouvert sur la face plate à l'extérieur de la zone de contact entre la face plate et le bossage de came.
PCT/US2010/036121 2009-09-29 2010-05-26 Procédé de lubrification de bossage d'arbre à came de frein moteur WO2011040997A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US13/498,138 US20120174887A1 (en) 2009-09-29 2010-05-26 Engine brake camshaft lobe lubrication method
EP10820964A EP2483533A1 (fr) 2009-09-29 2010-05-26 Procédé de lubrification de bossage d'arbre à came de frein moteur
BR112012007065A BR112012007065A2 (pt) 2009-09-29 2010-05-26 método de lubrificação de lóbulo de eixo de cames de freio motor
CN2010800547992A CN102656343A (zh) 2009-09-29 2010-05-26 发动机制动凸轮轴凸部的润滑方法

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US24658009P 2009-09-29 2009-09-29
US61/246,580 2009-09-29

Publications (1)

Publication Number Publication Date
WO2011040997A1 true WO2011040997A1 (fr) 2011-04-07

Family

ID=43826580

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2010/036121 WO2011040997A1 (fr) 2009-09-29 2010-05-26 Procédé de lubrification de bossage d'arbre à came de frein moteur

Country Status (5)

Country Link
US (1) US20120174887A1 (fr)
EP (1) EP2483533A1 (fr)
CN (1) CN102656343A (fr)
BR (1) BR112012007065A2 (fr)
WO (1) WO2011040997A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9458744B2 (en) 2014-10-29 2016-10-04 Ford Global Technologies, Llc Engine with external cam lubrication
US11002160B2 (en) 2019-08-22 2021-05-11 Caterpillar Inc. Lifter providing improved cam lobe lubrication

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3656582A (en) * 1967-08-16 1972-04-18 Ricardo & Co Engineers Lubrication of bearings of reciprocating engines or pumps
US4788947A (en) * 1983-04-29 1988-12-06 Eaton Corporation Cap retainer for hydraulic lash adjuster
US5839453A (en) * 1995-08-08 1998-11-24 Diesel Engine Retarders, Inc. Internal combustion engines with combined cam and electro-hydraulic engine valve control
US6782855B1 (en) * 2003-05-14 2004-08-31 General Motors Corporation Valve train and method for reducing oil flow to deactivated engine valves
US20070125334A1 (en) * 2005-12-02 2007-06-07 Koerner Jeffrey S Roller Type hydrocushion mechanical tappet

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4708102A (en) * 1986-09-08 1987-11-24 Navistar International Transportation Corp. Roller cam follower with positive lubrication
US5860398A (en) * 1997-10-28 1999-01-19 Koerner; Jeffrey Scott Engine tappet
JP3891756B2 (ja) * 2000-03-31 2007-03-14 本田技研工業株式会社 内燃機関の潤滑構造

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3656582A (en) * 1967-08-16 1972-04-18 Ricardo & Co Engineers Lubrication of bearings of reciprocating engines or pumps
US4788947A (en) * 1983-04-29 1988-12-06 Eaton Corporation Cap retainer for hydraulic lash adjuster
US5839453A (en) * 1995-08-08 1998-11-24 Diesel Engine Retarders, Inc. Internal combustion engines with combined cam and electro-hydraulic engine valve control
US6782855B1 (en) * 2003-05-14 2004-08-31 General Motors Corporation Valve train and method for reducing oil flow to deactivated engine valves
US20070125334A1 (en) * 2005-12-02 2007-06-07 Koerner Jeffrey S Roller Type hydrocushion mechanical tappet

Also Published As

Publication number Publication date
BR112012007065A2 (pt) 2016-04-19
US20120174887A1 (en) 2012-07-12
EP2483533A1 (fr) 2012-08-08
CN102656343A (zh) 2012-09-05

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