US20030033998A1 - Hybrid multi-position cam indexer having controls located in rotor - Google Patents

Hybrid multi-position cam indexer having controls located in rotor Download PDF

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Publication number
US20030033998A1
US20030033998A1 US10/198,318 US19831802A US2003033998A1 US 20030033998 A1 US20030033998 A1 US 20030033998A1 US 19831802 A US19831802 A US 19831802A US 2003033998 A1 US2003033998 A1 US 2003033998A1
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United States
Prior art keywords
rotor
recess
fluid
spool
cylindrical recess
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Abandoned
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US10/198,318
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English (en)
Inventor
Marty Gardner
Michael Duffield
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BorgWarner Inc
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BorgWarner Inc
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Priority to US10/198,318 priority Critical patent/US20030033998A1/en
Assigned to BORGWARNER INC. reassignment BORGWARNER INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DUFFIELD, MICHAEL, GARDNER, MARTY
Publication of US20030033998A1 publication Critical patent/US20030033998A1/en
Priority to US10/714,159 priority patent/US6883481B2/en
Abandoned legal-status Critical Current

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    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34409—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear by torque-responsive means
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves

Definitions

  • the invention pertains to the field of variable camshaft timing (VCT) systems. More particularly, the invention pertains to an infinitely variable camshaft indexer with controls in the center of the rotor.
  • VCT variable camshaft timing
  • U.S. Pat. No. 5,386,807 uses torque effects at high speed, and engine pressure at low speed.
  • the control valve is in the phaser core.
  • the phaser has a built-in oil pump to provide oil pressure at low speeds.
  • the oil pump is preferably electromagnetically controlled.
  • U.S. Pat. No. 6,053,138 discloses a device for hydraulic rotational angle adjustment of a shaft to a drive wheel, especially the camshaft of an internal combustion engine.
  • This device has ribs or vanes that are nonrotatably connected with the shaft. These ribs or vanes are located in the compartments of a compartmented wheel.
  • the compartments of the compartmented wheel and the ribs and/or vanes produce pressure chambers by whose hydraulic pressurization the two structural elements can be rotated relative to one another.
  • a common end face of the compartmented wheel and of the ribs and/or vanes works with an annular piston that exerts a releasable clamping action on the parts that are rotatable relative to one another.
  • a related patent, U.S. Pat. No. 6,085,708, shows a device for changing the relative rotational angle of the camshaft of an internal combustion engine relative to its drive wheel.
  • This device has an inner part connected with ribs or vanes that is located rotationally movably in a compartmented wheel.
  • This driven compartmented wheel has a plurality of compartments distributed around the circumference divided by ribs or vanes into two pressure chambers each. The change in rotational angle is produced by their pressurization.
  • a damping structure is integrated into this device to hydraulically damp the change in rotational position.
  • U.S. Pat. No. 5,002,023 describes a VCT system within the field of the invention in which the system hydraulics includes a pair of oppositely acting hydraulic cylinders with appropriate hydraulic flow elements to selectively transfer hydraulic fluid from one of the cylinders to the other, or vice versa, to thereby advance or retard the circumferential position on of a camshaft relative to a crankshaft.
  • the control system utilizes a control valve in which the exhaustion of hydraulic fluid from one or another of the oppositely acting cylinders is permitted by moving a spool within the valve one way or another from its centered or null position.
  • the movement of the spool occurs in response to an increase or decrease in control hydraulic pressure, P c , on one end of the spool and the relationship between the hydraulic force on such end and an oppositely direct mechanical force on the other end which results from a compression spring that acts thereon.
  • U.S. Pat. No. 5,107,804 describes an alternate type of VCT system within the field of the invention in which the system hydraulics include a vane having lobes within an enclosed housing which replace the oppositely acting cylinders disclosed by the aforementioned U.S. Pat. No. 5,002,023.
  • the vane is oscillatable with respect to the housing, with appropriate hydraulic flow elements to transfer hydraulic fluid within the housing from one side of a lobe to the other, or vice versa, to thereby oscillate the vane with respect to the housing in one direction or the other, an action which is effective to advance or retard the position of the camshaft relative to the crankshaft.
  • the control system of this VCT system is identical to that divulged in U.S. Pat. No. 5,002,023, using the same type of spool valve responding to the same type of forces acting thereon.
  • U.S. Pat. Nos. 5,172,659 and 5,184,578 both address the problems of the aforementioned types of VCT systems created by the attempt to balance the hydraulic force exerted against one end of the spool and the mechanical force exerted against the other end.
  • the improved control system disclosed in both U.S. Pat. Nos. 5,172,659 and 5,184,578 utilizes hydraulic force on both ends of the spool.
  • the hydraulic force on one end results from the directly applied hydraulic fluid from the engine oil gallery at full hydraulic pressure, Ps.
  • the hydraulic force on the other end of the spool results from a hydraulic cylinder or other force multiplier which acts thereon in response to system hydraulic fluid at reduced pressure, Pc, from a PWM solenoid.
  • a camshaft has a vane secured to an end for non-oscillating rotation.
  • the camshaft also carries a timing belt driven pulley which can rotate with the camshaft but which is oscillatable with respect to the camshaft.
  • the vane has opposed lobes which are received in opposed recesses, respectively, of the pulley.
  • the camshaft tends to change in reaction to torque pulses which it experiences during its normal operation and it is permitted to advance or retard by selectively blocking or permitting the flow of engine oil from the recesses by controlling the position of a spool within a valve body of a control valve in response to a signal from an engine control unit.
  • the spool is urged in a given direction by rotary linear motion translating means which is rotated by an electric motor, preferably of the stepper motor type.
  • U.S. Pat. No. 5,497,738 shows a control system which eliminates the hydraulic force on one end of a spool resulting from directly applied hydraulic fluid from the engine oil gallery at full hydraulic pressure, Ps, utilized by previous embodiments of the VCT system.
  • the force on the other end of the vented spool results from an electromechanical actuator, preferably of the variable force solenoid type, which acts directly upon the vented spool in response to an electronic signal issued from an engine control unit (“ECU”) which monitors various engine parameters.
  • the ECU receives signals from sensors corresponding to camshaft and crankshaft positions and utilizes this information to calculate a relative phase angle.
  • a closed-loop feedback system which corrects for any phase angle error is preferably employed.
  • variable force solenoid solves the problem of sluggish dynamic response.
  • Such a device can be designed to be as fast as the mechanical response of the spool valve, and certainly much faster than the conventional (fully hydraulic) differential pressure control system.
  • the faster response allows the use of increased closed-loop gain, making the system less sensitive to component tolerances and operating environment.
  • the present invention is an infinitely variable camshaft timing device (phaser) with a control valve located in the rotor. Since the control valve is in the rotor, the camshaft need only provide a single passage for supplying engine oil or hydraulic fluid, and does not need multiple passageways for controlling the phaser, as was the prior art.
  • the main advantage to putting the spool in the rotor is to reduce leakage and to improve response of the phaser. This design allows for shorter fluid passages when compared to a control system mounted at the cam bearing.
  • the rotor is connected to the camshaft, and the outer housing and gear move relative to the rotor and camshaft.
  • Source oil is supplied through the center of the camshaft.
  • the oil passes through an inlet check valve and is ported to the center of the spool valve.
  • the inlet check valve eliminates oil from back flowing through the source during a torque reversal. The position of the spool valve determines if the phaser will advance or retard.
  • FIG. 1 shows a blown-up side view of the camshaft in an embodiment of the present invention.
  • FIG. 2 shows a top-down view of the camshaft of FIG. 1.
  • FIG. 3 shows a less-detailed top-down view of the camshaft of FIG. 1.
  • FIG. 4 shows a fragmentary view of the camshaft taken along line A-A of FIG. 3.
  • FIG. 5 shows a fragmentary view of the camshaft taken along line B-B of FIG. 3.
  • FIG. 6 shows a cam indexer with a center spool and inlet check valve in the null position in a preferred embodiment of the invention.
  • FIG. 7 shows a cam indexer with a center spool and inlet check valve in the advance position in a preferred embodiment of the invention.
  • FIG. 8 shows a cam indexer with a center spool and inlet check valve in the retard position in a preferred embodiment of the invention.
  • an internal combustion engine has a crankshaft, to which is driven by the connecting rods of the pistons, and one or more camshafts, which actuate the intake and exhaust valves on the cylinders.
  • the timing gear on the camshaft is connected to the crankshaft with a timing drive, such as a belt, chain or gears.
  • camshaft ( 9 ) may be the only camshaft of a single camshaft engine, either of the overhead camshaft type or the in-block camshaft type, or one of two (the intake valve operating camshaft or the exhaust valve operating camshaft) of a dual camshaft engine, or one of four camshafts in a “V” type overhead cam engine, two for each bank of cylinders.
  • phaser In a variable cam timing (VCT) system, the timing gear on the camshaft is replaced by a variable angle coupling known as a “phaser”, having a rotor connected to the camshaft and a housing connected to (or forming) the timing gear, which allows the camshaft to rotate independently of the timing gear, within angular limits, to change the relative timing of the camshaft and crankshaft.
  • phaser includes the housing and the rotor, and all of the parts to control the relative angular position of the housing and rotor, to allow the timing of the camshaft to be offset from the crankshaft. In any of the multiple-camshaft engines, it will be understood that there would be one phaser on each camshaft, as is known to the art.
  • a rotor ( 1 ) is fixedly positioned on the camshaft ( 9 ), by means of mounting flange ( 8 ), to which it (and rotor front plate ( 4 )) is fastened by screws ( 14 ).
  • the rotor ( 1 ) has a diametrically opposed pair of radially outwardly projecting vanes ( 16 ), which fit into recesses ( 17 ) in the housing body ( 2 ).
  • the inner plate ( 5 ), housing body ( 2 ), and outer plate ( 3 ) are fastened together around the mounting flange ( 8 ), rotor ( 1 ) and rotor front plate ( 4 ) by screws ( 13 ), so that the recesses ( 17 ) holding the vanes ( 16 ), enclosed by outer plate ( 3 ) and inner plate ( 5 ), form fluid-tight chambers.
  • the timing gear ( 11 ) is connected to the inner plate ( 5 ) by screws ( 12 ).
  • the vanes ( 16 ) of the rotor ( 1 ) fit in the radially outwardly projecting recesses ( 17 ), of the housing body ( 2 ), the circumferential extent of each of the recesses ( 17 ) being somewhat greater than the circumferential extent of the vane ( 16 ) which is received in such recess to permit limited oscillating movement of the housing relative to the rotor ( 1 ).
  • the vanes ( 16 ) are provided with vane tips ( 6 ) in receiving slots ( 19 ), which are biased outward by linear expanders ( 7 ).
  • each of the chambers ( 17 a ) and ( 17 b ) of the housing ( 2 ) is capable of sustaining hydraulic pressure.
  • application of pressure to chambers ( 17 a ) will move the rotor clockwise relative to the rotor ( 1 )
  • application of pressure to chambers ( 17 b ) will move the rotor counterclockwise relative to the rotor ( 1 ).
  • the spool ( 27 ) of the spool valve ( 20 ) is located within the rotor ( 1 ), in a cylindrical recess ( 25 ) along its central axis ( 26 ). Passageways lead oil from the spool valve to the chambers ( 17 a )( 17 b ), as will be seen in schematic form below.
  • the engine oil or other operating fluid enters the side of the mounting flange ( 8 ) and into the rotor ( 1 ) through passage ( 21 ).
  • the camshaft ( 9 ) is much easier to manufacture, since fluid only needs to travel through the phaser into the spool valve ( 20 ) in the rotor ( 1 )—no elaborate passages need be machined into the camshaft ( 9 ), and no externally mounted valves are needed. Having the spool valve ( 20 ) in the rotor ( 1 ) reduces leakage and improves the response of the phaser. This design allows for shorter fluid passages when compared to a control system mounted at the cam bearing.
  • the phaser operating fluid ( 122 ) flows into the recesses ( 17 a ) (labeled “A” for “advance”) and ( 17 b ) (labeled “R” for “retard”) by way of a common inlet line ( 110 ).
  • a common inlet line ( 110 ) In a preferred embodiment shown in FIGS. 6 - 8 , an inlet check valve ( 105 ) prevents the hydraulic fluid from backflow into the engine oil supply.
  • the invention also operates without the inlet check valve ( 105 ), without deviating from the spirit of the invention.
  • Inlet line ( 110 ) terminates as it enters the spool valve ( 109 ).
  • the spool valve ( 109 ) is made up of a spool ( 104 ) and a cylindrical member ( 115 ).
  • the spool ( 104 ) which is preferably a vented spool, is slidable back and forth.
  • the spool ( 104 ) includes spool lands ( 104 a ) and ( 104 b ) on opposed ends thereof, which fit snugly within cylindrical member ( 115 ).
  • the spool lands ( 104 a ) and ( 104 b ) are preferably cylindrical lands and preferably have three positions, described in more detail below.
  • Control of the position of spool ( 104 ) within member ( 115 ) is in direct response to a variable force solenoid ( 103 ).
  • the variable force solenoid ( 103 ) is preferably an electromechanical actuator ( 103 ).
  • U.S. Pat. No. 5,497,738, entitled “VCT Control with a Direct Electromechanical Actuator”, which discloses the use of a variable force solenoid, issued Mar. 12, 1996, is herein incorporated by reference. Briefly, in the preferred embodiment an electrical current is introduced via a cable through the solenoid housing into a solenoid coil which repels, or “pushes” an armature ( 117 ) in the electromechanical actuator ( 103 ).
  • armature ( 117 ) bears against extension ( 104 c ) of spool ( 104 ), thus moving spool ( 104 ) to the right. If the force of spring ( 116 ) is in balance with the force exerted by armature ( 117 ) in the opposite direction, spool ( 104 ) will remain in its null or centered position. Thus, the spool ( 104 ) is moved in either direction by increasing or decreasing the current to the solenoid coil, as the case may be.
  • electromechanical actuator ( 103 ) may be reversed, converting the force on spool extension ( 104 c ) from a “push” to a “pull.”
  • This alternative requires the function of spring ( 116 ) to be redesigned to counteract the force in the new direction of armature ( 117 ) movement.
  • variable force electromechanical actuator ( 103 ) allows the spool valve to be moved incrementally instead of only being capable of full movement to one end of travel or the other, as is common in conventional camshaft timing devices.
  • the use of a variable force solenoid eliminates slow dynamic response. The faster response allows the use of increased closed-loop gain, making the system less sensitive to component tolerances and operating environment.
  • a variable force solenoid armature only travels a short distance, as controlled by the current from the Engine Control Unit (ECU) ( 102 ).
  • ECU Engine Control Unit
  • an electronic interface module provides electronics for the VCT. The EIM interfaces between the actuator ( 103 ) and the ECU ( 102 ).
  • variable force solenoid provides a greatly enhanced ability to quickly and accurately follow a command input of VCT phase.
  • variable force solenoids include, but are not limited to, a cylindrical armature, or variable area, solenoid, and a flat faced armature, or variable gap, solenoid.
  • the electromechanical actuator employed could also be operated by a pulse-width modulated supply.
  • other actuators such as hydraulic solenoids, stepper motors, worm- or helical-gear motors or purely mechanical actuators could be used to actuate the spool valve within the teachings of the invention.
  • the spool ( 104 ) is positioned at null, as shown in FIG. 6.
  • the camshaft ( 9 ) is maintained in a selected intermediate position relative to the crankshaft of the associated engine, referred to as the “null” position of the spool ( 104 ).
  • Make up oil from the supply fills both chambers ( 17 a ) and ( 17 b ).
  • spool lands ( 104 a ) and ( 104 b ) block both of the return lines ( 112 ) and ( 114 ), as well as inlet lines ( 111 ) and ( 113 ).
  • source hydraulic fluid ( 122 ) is ported to the advance chamber ( 17 a ) by shifting the spool valve ( 104 ) to the left.
  • the retard chamber ( 17 b ) is exhausted to atmosphere—that is, to a location of lower pressure, where the fluid may be recycled back to the fluid source.
  • “atmosphere” means into a location where the engine oil can drain back into the oil pan at the bottom of the engine, for example into the timing chain cover or a return line connected to the oil pan.
  • land ( 104 b ) blocks the entrance of hydraulic fluid into the retard chamber inlet line ( 113 ).
  • Cavity ( 119 ) is now lined up with advance chamber inlet line ( 111 ), allowing additional hydraulic fluid ( 122 ) to enter the retard chamber ( 17 a ).
  • Land ( 104 a ) blocks the exit of hydraulic fluid ( 122 ) from the advance chamber return line ( 112 ).
  • Cavity ( 121 ) allows the exhaust of hydraulic fluid ( 122 ) through the retard chamber return line ( 114 ) and out the retard chamber exhaust ( 107 ) to atmosphere.
  • the spool valve ( 104 ) is moved to the right, and source hydraulic fluid ( 122 ) is ported to the retard chamber ( 17 b ) and the hydraulic fluid ( 122 ) in the advance chamber ( 17 a ) is exhausted to the atmosphere.
  • land ( 104 b ) blocks the exit of hydraulic fluid from retard chamber return line ( 114 ).
  • Cavity ( 119 ) is now lined up with retard chamber inlet line ( 113 ), allowing hydraulic fluid ( 122 ) into the retard chamber ( 17 b ).
  • Land ( 104 a ) blocks the entry of hydraulic fluid ( 122 ) into advance chamber inlet line ( 111 ).
  • Cavity ( 120 ) allows the exhaust of hydraulic fluid ( 122 ) through the advance chamber return line ( 112 ) and out the advance chamber exhaust ( 106 ) to atmosphere.
  • a lock mechanism is included for start up, when there is insufficient oil pressure to hold the phaser in position.
  • a single position pin can be inserted into a hole, locking the rotor and housing together, or another shift and lock strategy as known to the art used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
US10/198,318 2001-08-14 2002-07-18 Hybrid multi-position cam indexer having controls located in rotor Abandoned US20030033998A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US10/198,318 US20030033998A1 (en) 2001-08-14 2002-07-18 Hybrid multi-position cam indexer having controls located in rotor
US10/714,159 US6883481B2 (en) 2001-08-14 2003-11-14 Torsional assisted multi-position cam indexer having controls located in rotor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US31228501P 2001-08-14 2001-08-14
US10/198,318 US20030033998A1 (en) 2001-08-14 2002-07-18 Hybrid multi-position cam indexer having controls located in rotor

Related Child Applications (1)

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US10/714,159 Continuation US6883481B2 (en) 2001-08-14 2003-11-14 Torsional assisted multi-position cam indexer having controls located in rotor

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US10/198,318 Abandoned US20030033998A1 (en) 2001-08-14 2002-07-18 Hybrid multi-position cam indexer having controls located in rotor
US10/714,159 Expired - Lifetime US6883481B2 (en) 2001-08-14 2003-11-14 Torsional assisted multi-position cam indexer having controls located in rotor

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US10/714,159 Expired - Lifetime US6883481B2 (en) 2001-08-14 2003-11-14 Torsional assisted multi-position cam indexer having controls located in rotor

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EP (1) EP1284340B1 (enrdf_load_stackoverflow)
JP (1) JP4209152B2 (enrdf_load_stackoverflow)
DE (1) DE60220122T2 (enrdf_load_stackoverflow)

Cited By (3)

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EP1596041A3 (de) * 2004-05-14 2008-07-16 Schaeffler KG Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
GB2487227A (en) * 2011-01-14 2012-07-18 Mechadyne Plc Spool valve for simultaneous control of two output members
US20200141289A1 (en) * 2018-11-07 2020-05-07 Aisin Seiki Kabushiki Kaisha Valve timing controller

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WO2006127347A1 (en) * 2005-05-23 2006-11-30 Borgwarner Inc Integrated check valve
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US20060096562A1 (en) * 2006-01-20 2006-05-11 Borgwarner Inc. Reed valve with multiple ports
US7318401B2 (en) 2006-03-15 2008-01-15 Borgwarner Inc. Variable chamber volume phaser
DE102006019543A1 (de) * 2006-04-27 2007-10-31 Schaeffler Kg Plattenrückschlagventil mit seitlicher Abströmung und Steuerkante
WO2008042622A1 (en) * 2006-09-29 2008-04-10 Borgwarner Inc Variable event duration reduction (vedr) cam phaser
WO2008140897A1 (en) * 2007-05-14 2008-11-20 Borgwarner Inc. Cam mounted accumulator
JP5162659B2 (ja) * 2007-06-19 2013-03-13 ボーグワーナー インコーポレーテッド 移相器を有する同心カム
WO2009005999A1 (en) 2007-07-02 2009-01-08 Borgwarner Inc. Concentric cam with check valves in the spool for a phaser
DE112008001522B4 (de) 2007-07-06 2018-10-04 Borgwarner Inc. In der Nockenwelle angebrachter Elektromagnet für einen variablen Nockenverstellmechanismus
US8145404B2 (en) * 2008-08-15 2012-03-27 Delphi Technologies, Inc. Method for synchronizing an oil control valve as a virtual check valve
WO2010033417A2 (en) * 2008-09-19 2010-03-25 Borgwarner Inc. Cam torque actuated phaser using band check valves built into a camshaft or concentric camshafts
DE102009022869A1 (de) * 2009-05-27 2010-12-09 Hydraulik-Ring Gmbh Flügelzellennockenwellenverstellersystem
DE102009050779B4 (de) 2009-10-27 2016-05-04 Hilite Germany Gmbh Schwenkmotornockenwellenversteller mit einer Reibscheibe und Montageverfahren
DE102009052841A1 (de) * 2009-11-13 2011-05-19 Hydraulik-Ring Gmbh Nockenwelleneinsatz
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JP2003065011A (ja) 2003-03-05
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US20040099232A1 (en) 2004-05-27
DE60220122D1 (de) 2007-06-28
EP1284340A2 (en) 2003-02-19
JP4209152B2 (ja) 2009-01-14
US6883481B2 (en) 2005-04-26
EP1284340A3 (en) 2003-11-05

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