US20040244751A1 - Deactivating valve lifter - Google Patents

Deactivating valve lifter Download PDF

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Publication number
US20040244751A1
US20040244751A1 US10859024 US85902404A US2004244751A1 US 20040244751 A1 US20040244751 A1 US 20040244751A1 US 10859024 US10859024 US 10859024 US 85902404 A US85902404 A US 85902404A US 2004244751 A1 US2004244751 A1 US 2004244751A1
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US
Grant status
Application
Patent type
Prior art keywords
lifter
oil
valve
body
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.)
Abandoned
Application number
US10859024
Inventor
Alan Falkowski
Mark McElwee
Joel Baker
Glen Hendershott
Constantin Hagiu
Mark Koeroghlian
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.)
DIAMLERCHRYSLER Corp
Original Assignee
DIAMLERCHRYSLER Corp
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

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005Deactivating valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12Transmitting gear between valve drive and valve
    • F01L1/14Tappets; Push rods
    • F01L1/146Push-rods
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02Valve drive
    • F01L1/04Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047Camshafts
    • F01L2001/054Camshafts in cylinder block
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2105/00Valve arrangements comprising rollers

Abstract

A valve lifter for an internal combustion engine comprises an outer body, an inner body and at least one pin. The inner body is movable with respect to the outer body, and the at least one pin is movable in response to hydraulic pressure into the groove to lock the outer body against movement relative to the inner body.

Description

    CROSS REFERENCE TO RELATED APPLICATION(S)
  • [0001]
    This application claims benefit of U.S. Provisional Application No. 60/475,276 filed on Jun. 3, 2003.
  • FIELD OF THE INVENTION
  • [0002]
    The present invention relates generally to an engine for a motor vehicle, and, more particularly, to a variable displacement engine for a motor vehicle powertrain.
  • BACKGROUND OF THE INVENTION
  • [0003]
    In vehicle design, fuel economy is becoming increasingly important. To that end, fuel conservation and engine system design play a significant role. In addition, with the popularity of sport utility vehicles and performance luxury cars, and with increasing competition in the automotive market, superior engine refinement coupled with strong engine performance are necessary deliverables for an engine to satisfy many of today's automotive consumer requirements.
  • [0004]
    To satisfy the performance aspect, larger displacement engines, such as a V-6 or V-8 engine, are typically developed for these vehicles. As is known, these larger displacement engines generally do not realize the same fuel economy as a smaller displacement engine. To that end, variable displacement engines can provide for fuel economy benefits by operating on the principle of cylinder deactivation. During operating conditions that require high output torque, such as acceleration, every cylinder of a variable displacement engine is arranged to be activated. In contrast, for low load conditions, such as steady cruising, cylinders may be deactivated to improve fuel economy for the variable displacement engine vehicle.
  • [0005]
    While such variable displacement engines provide advantages of improved fuel economy, conventional cylinder deactivation systems of these arrangements rely on add-on engine componentry, such as externally coupled hydraulic fluid passages that increase engine cost and complexity as well as create additional sources for potential hydraulic fluid leakage from the engine.
  • SUMMARY OF THE INVENTION
  • [0006]
    Accordingly, a valve lifter is provided for an internal combustion engine. In one aspect of the invention, the valve lifter comprises an outer body, an inner body and at least one pin. The inner body is movable with respect to the outer body, and the at least one pin is movable in response to hydraulic pressure into the groove to lock the outer body against movement relative to the inner body.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • [0007]
    Other aspects, features, and advantages of the present invention will become more fully apparent from the following detailed description of the preferred embodiment, the appended claims, and in the accompanying drawings in which:
  • [0008]
    [0008]FIG. 1 illustrates an isometric view of an exemplary embodiment of a V-8 engine having a main oiling circuit and a lifter oil gallery control circuit in accordance with the present invention;
  • [0009]
    [0009]FIG. 2 illustrates a front view of the engine shown in FIG. 1 and including valve train componentry in accordance with the present invention;
  • [0010]
    [0010]FIG. 3 illustrates an isometric view of the engine shown in FIG. 1 highlighting a cylinder block and aspects of the main oiling circuit and the lifter oil gallery control circuit for cylinders arranged to be selectively deactivated in accordance with the present invention; and
  • [0011]
    [0011]FIG. 4 illustrates aspects of the lifter oil gallery control circuit including a control valve and a deactivating lifter in accordance with the present invention.
  • DETAILED DESCRIPTION OF THE PREFERRED EMBODIMIENT
  • [0012]
    In the following description, several well-known features of an internal combustion engine are not shown or described so as not to obscure the present invention. Referring now to the drawings, FIGS. 1, 2 and 3 illustrate an exemplary embodiment of an engine 10 with a main oiling circuit 20 and a lifter oil gallery control circuit 30 arranged to deactivate selective cylinders to improve fuel economy. Main oiling circuit 20 provides a path for oil flow from an oil pump 35 through an oil filter 37 and into a main oil gallery 50 of cylinder block 60. Feed passages 70 provide a flow path between the main oil gallery 50 and a crankshaft oiling circuit 40. Main oil gallery 50 is then generally used to further feed a plurality of other passages and components. Most relevant to this invention are feed passages 80 that continue from feed passages 70 and serve as the feed passages to cylinder heads 90.
  • [0013]
    Cylinder heads 90 in the exemplary embodiment utilize a top down oiling arrangement where the oil feed passages 80 continue through the cylinder head 90 via interface with rocker shafts 100. From the rocker shafts, oil travels through the respective rocker arms 110 and then through hollow push rods 120. From the push rods, the oil then travels into a deactivating lifter 140 to provide hydraulic pressure to a lash adjuster 134 (FIG. 4) housed within the deactivating lifter 140. Oil then flows through conventional oil drain (not shown) back into an oil pan (not shown).
  • [0014]
    Feed passages 80, in addition to feeding the cylinder head, provide an oil supply to the lifter oil gallery control circuit 30. As oil flows through feed passages 80 towards cylinder heads 90, solenoid control valve 150 positioned in a bore 155 formed in cylinder block 60 is arranged to selectively provide high pressure oil flow to lifter oil gallery 160. Lifter oil gallery 160 is connected to and interacts with a lifter bore 170 that houses the deactivating lifter 140. Also, the lifter oil gallery control circuit 30 is laid out in a manner that naturally purges air from the lifter oil gallery control circuit passages. This is accomplished by utilizing a bottom up oil passage architecture incorporated into cylinder block 60 and the oil feeding passages of cylinder heads 90. For example, the bottom up oiling architecture allows any air that travels into feed passages 80 to travel up to the rocker shafts 100, a high point in the system and beyond the oil gallery lifter control circuit 30. In addition, any air that migrates from feed passage 80 into the lifter oil gallery 160 is allowed to purge from the system through natural oil leakage between the lifter bore 170 and the deactivating lifter 140.
  • [0015]
    In operation and referring to FIGS. 2, 3 and 4, to deactivate a cylinder both the intake valve 180 and the exhaust valve 190 are turned off by decoupling these valves from the valve train. This is accomplished through a series of sequential events. At a proper time in the engine cycle, the engine solenoid control valve 150 is energized and this opens a flow path for oil from feed passage 80 through the control valve 150 and into lifter oil gallery 160. This raises the oil pressure in lifter oil gallery 160 to that of the main oiling circuit 10 (high pressure oil) and this in turn deactivates a locking mechanism in deactivating lifter 140 allowing the lifter to absorb camshaft input without activating the intake and exhaust valves as further described below.
  • [0016]
    Deactivating lifter 140, like a conventional lifter, houses the hydraulic lash adjuster 134 and also includes an outer body 142 with an inner body 144 and a lost motion spring 146 between the two bodies. The inner body has a pair of pins 148 that extend or retract in response to oil pressure below or above predetermined high or low thresholds, respectively. When extended, the pins 148 sit on a groove formed on the inside of the outer body 142, locking the inner and outer bodies together. In response to high oil pressure, the pins 148 are arranged to retract and enable relative motion between the outer and inner bodies of the lifter and decouple the camshaft input from a specific intake or exhaust valve of the respective cylinder to be deactivated. For a given cylinder that is arranged to be selectively deactivated, one solenoid control valve 150 is used to control two deactivating lifters 140, one lifter for the intake valve 180 and one lifter for exhaust valve 190. When deactivated, the lost motion spring 146 supplies a force necessary to ensure contact is maintained between valvetrain components. Applicants hereby incorporate by reference commonly owned copending patent application Ser. No. ______ filed on ______ and entitled Multiple Displacement System for an Engine (Docket No. 706670US2).
  • [0017]
    To reactivate deactivated cylinders, removing the energizing voltage source from a solenoid 151 of the control valve 150 substantially closes the flow path through the valve into the lifter oil gallery 160 and simultaneously opens a pressure relief valve 154 within control valve 150 resulting in the oil pressure falling to a nominal pressure, such as 3 psi. This resultant loss in pressure removes the hydraulic pressure necessary to force retraction of the lifter pins 148 and thus the pins 148 of the inner lifter housing 144 reengage the outer lifter housing 142 which eliminates relative motion of the lifter and re-couples the lifter to valve train cam input.
  • [0018]
    In addition to controlling hydraulic pressure necessary to activate and deactivate cylinders of the engine, the control valve 150 also maintains a nominal oil pressure in the deactivating lifter oil gallery circuit control 30 through a combination of an internal passage 152 in the control valve and the pressure relief valve 154. The internal passage allows a restricted flow of oil into the lifter gallery 160 and the pressure relief valve maintains pressure in the lifter oil gallery at a nominal 3 psi when the control valve is in the closed position. Control valve 150 seals at o-ring 156 and o-ring 158 in the bore 155 formed in cylinder block 60. O-ring 156 prevents oil from leaking external to the engine and o-ring 158 prevents oil flowing past the pressure relief valve from interacting with lifter oil gallery 160. Thus, any oil that flows past relief valve 154 collects in the lifter bore 170 between the O-rings and then drains though a conventionally designed oil drainback passage (not shown). Maintaining this nominal oil pressure is desirable to enable an optimum response time for deactivation and reactivation events such that these respective events are not discernable to a vehicle operator. A magnet 153 located on the nose of the unit collects ferrous debris to minimize the contamination of the valve and lifters.
  • [0019]
    In today's competitive automotive environment, it is increasingly important for automotive OEM's to provide a product that satisfies customer expectations in a cost effective manner. For engines, especially a larger displacement V-8 engine, this generally breaks down to providing a low warranty risk, low leak potential engine with significant horsepower while meeting government fuel economy requirements and all in a cost effective manner.
  • [0020]
    The MDS engine architecture for this exemplary embodiment represents a system fully integrated into the engine block hardware providing for a lower cost, lower complexity system while also minimizing potential oil leak paths. Integrating all of the oil control and flow passages directly into the block as well as having the control valve mount directly to the engine block via a bore formed in the block greatly reduces the amount of oil leak paths, especially when compared to an add-on or bolt-on oil hardware system. In addition, using formed passages and bores in the engine block reduces manufacturing and component complexity through both a minimization of engine assembly operations and a reduction in the number of system components, both of which also reduce cost. For example, in the exemplary embodiment there is a separate lifter oil gallery control circuit for each cylinder arranged to be selectively deactivated and each lifter oil gallery can be formed (i.e., drilled) from the front or rear face of the engine block for ease of manufacturing. Finally, the architecture of the main and lifter oil gallery circuits result in a design that naturally purges air from the system and thus eliminates the need for an additional and/or external purge air device.
  • [0021]
    The foregoing description constitutes the embodiments devised by the inventors for practicing the invention. It is apparent, however, that the invention is susceptible to modification, variation, and change that will become obvious to those skilled in the art. Inasmuch as the foregoing description is intended to enable one skilled in the pertinent art to practice the invention, it should not be construed to be limited thereby but should be construed to include such aforementioned obvious variations and be limited only by the proper scope or fair meaning of the accompanying claims.

Claims (20)

  1. 1. A valve lifter comprising:
    an outer body having a groove;
    an inner body movable with respect to the outer body;
    at least one pin movable in response to hydraulic pressure, the at least one pin being movable into the groove to lock the outer body against movement relative to the inner body.
  2. 2. The valve lifter of claim 1 further comprising a lost motion spring disposed between the outer body and the inner body.
  3. 3. The valve lifter of claim 1 wherein the at least one pin is retractable out of the groove and within the inner body.
  4. 4. The valve lifter of claim 1 wherein the at least one pin is retractable out of the groove and within the inner body in response to relatively high hydraulic pressure.
  5. 5. The valve lifter of claim 1 wherein the at least one pin is retractable out of the groove against a spring force.
  6. 6. The valve lifter of claim 1 wherein the at least one pin comprises a pair of pins.
  7. 7. The valve lifter of claim 1 wherein the hydraulic pressure is developed by engine oil.
  8. 8. The valve lifter of claim 1 further comprising a hydraulic lash adjuster disposed within the inner body.
  9. 9. A valve lifter comprising:
    an outer body having a pair of grooves;
    an inner body movable with respect to the outer body;
    a pair of pins movable in response to hydraulic pressure, each pin being movable into a respective groove to lock the outer body against movement relative to the inner body.
  10. 10. The valve lifter of claim 9 further comprising a lost motion spring disposed between the outer body and the inner body.
  11. 11. The valve lifter of claim 9 wherein the at least one pin is retractable out of the groove and within the inner body.
  12. 12. The valve lifter of claim 9 wherein the at least one pin is retractable out of the groove and within the inner body in response to relatively high hydraulic pressure.
  13. 13. The valve lifter of claim 9 wherein the at least one pin is retractable out of the groove against a spring force.
  14. 14. The valve lifter of claim 9 wherein the hydraulic pressure is developed by engine oil.
  15. 15. The valve lifter of claim 9 further comprising a hydraulic lash adjuster disposed within the inner body.
  16. 16. A valve lifter for an internal combustion engine, the valve lifter comprising:
    an outer body having a groove;
    an inner body movable with respect to the outer body;
    at least one pin movable into the groove to lock the outer body against movement relative to the inner body, the at least one pin being retractable out of the groove and within the inner body in response to relatively high oil pressure developed by the engine.
  17. 17. The valve lifter of claim 1 further comprising a lost motion spring disposed between the outer body and the inner body.
  18. 18. The valve lifter of claim 1 wherein the at least one pin is retractable out of the groove against a spring force.
  19. 19. The valve lifter of claim 1 wherein the at least one pin comprises a pair of pins.
  20. 20. The valve lifter of claim 1 further comprising a hydraulic lash adjuster disposed within the inner body.
US10859024 2003-06-03 2004-06-02 Deactivating valve lifter Abandoned US20040244751A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US47527603 true 2003-06-03 2003-06-03
US10859024 US20040244751A1 (en) 2003-06-03 2004-06-02 Deactivating valve lifter

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Cited By (13)

* Cited by examiner, † Cited by third party
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US7013866B1 (en) 2005-03-23 2006-03-21 Daimlerchrysler Corporation Airflow control for multiple-displacement engine during engine displacement transitions
US7021273B1 (en) 2005-03-23 2006-04-04 Daimlerchrysler Corporation Transition control for multiple displacement engine
US7025035B1 (en) 2005-02-24 2006-04-11 Daimlerchrysler Corporation Method and code for determining event-based control delay of hydraulically-deactivatable valve train component
US7028661B1 (en) 2005-02-24 2006-04-18 Daimlerchrysler Corporation Method and code for controlling temperature of engine component associated with deactivatable cylinder
US7044107B1 (en) 2005-03-23 2006-05-16 Daimlerchrysler Corporation Method for enabling multiple-displacement engine transition to different displacement
US7085647B1 (en) 2005-03-21 2006-08-01 Daimlerchrysler Corporation Airflow-based output torque estimation for multi-displacement engine
US20060185426A1 (en) * 2005-02-24 2006-08-24 Falkowski Alan G Method and code for controlling actuator responsive to oil pressure using oil viscosity measure
US20060211539A1 (en) * 2005-03-21 2006-09-21 Bonne Michael A Torque converter slip control for multi-displacement engine
US20090266320A1 (en) * 2008-04-25 2009-10-29 Mechadyne Plc Valve actuating system
US20150369087A1 (en) * 2013-01-31 2015-12-24 Eaton Corporation Centrifugal Process to Eliminate Air in High Pressure Chamber of Hydraulic Lash Adjuster
EP2975230A1 (en) * 2014-07-15 2016-01-20 Jacobs Vehicle Systems, Inc. Lost motion valve actuation systems with locking elements including wedge locking elements
CN105874175A (en) * 2013-12-27 2016-08-17 马自达汽车株式会社 Hydraulic supplying device for valve stopping mechanism
US9790824B2 (en) 2010-07-27 2017-10-17 Jacobs Vehicle Systems, Inc. Lost motion valve actuation systems with locking elements including wedge locking elements

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US6615782B1 (en) * 2002-04-12 2003-09-09 Delphi Technologies, Inc. Two-step finger follower rocker arm
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US20060185426A1 (en) * 2005-02-24 2006-08-24 Falkowski Alan G Method and code for controlling actuator responsive to oil pressure using oil viscosity measure
US7107828B2 (en) 2005-02-24 2006-09-19 Daimlerchrysler Corporation Method and code for controlling actuator responsive to oil pressure using oil viscosity measure
US7025035B1 (en) 2005-02-24 2006-04-11 Daimlerchrysler Corporation Method and code for determining event-based control delay of hydraulically-deactivatable valve train component
US7028661B1 (en) 2005-02-24 2006-04-18 Daimlerchrysler Corporation Method and code for controlling temperature of engine component associated with deactivatable cylinder
US7085647B1 (en) 2005-03-21 2006-08-01 Daimlerchrysler Corporation Airflow-based output torque estimation for multi-displacement engine
US7288046B2 (en) 2005-03-21 2007-10-30 Chrysler Llc Torque converter slip control for multi-displacement engine
US20060211539A1 (en) * 2005-03-21 2006-09-21 Bonne Michael A Torque converter slip control for multi-displacement engine
US7044107B1 (en) 2005-03-23 2006-05-16 Daimlerchrysler Corporation Method for enabling multiple-displacement engine transition to different displacement
US7021273B1 (en) 2005-03-23 2006-04-04 Daimlerchrysler Corporation Transition control for multiple displacement engine
US7013866B1 (en) 2005-03-23 2006-03-21 Daimlerchrysler Corporation Airflow control for multiple-displacement engine during engine displacement transitions
US20090266320A1 (en) * 2008-04-25 2009-10-29 Mechadyne Plc Valve actuating system
US7921819B2 (en) * 2008-04-25 2011-04-12 Mechadyne Plc Valve actuating system
US9790824B2 (en) 2010-07-27 2017-10-17 Jacobs Vehicle Systems, Inc. Lost motion valve actuation systems with locking elements including wedge locking elements
US20150369087A1 (en) * 2013-01-31 2015-12-24 Eaton Corporation Centrifugal Process to Eliminate Air in High Pressure Chamber of Hydraulic Lash Adjuster
US9650921B2 (en) * 2013-01-31 2017-05-16 Eaton Corporation Centrifugal process to eliminate air in high pressure chamber of hydraulic lash adjuster
CN105874175A (en) * 2013-12-27 2016-08-17 马自达汽车株式会社 Hydraulic supplying device for valve stopping mechanism
US20160319707A1 (en) * 2013-12-27 2016-11-03 Mazda Motor Corporation Hydraulic supply device for valve stopping mechanism
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