Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
  • F16K31/00—Actuating devices; Operating means; Releasing devices
  • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
  • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
  • F16K31/0603—Multiple-way valves
  • F16K31/061—Sliding valves
  • F16K31/0613—Sliding valves with cylindrical slides
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
  • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
  • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic

Definitions

• the present invention relates to a control valve assembly for controlling hydraulic actuators, and more particularly, to a control valve assembly having a valve member that is held in an open position by a hydrodynamic force.
• a camless internal combustion engine valve actuation system typically includes hydraulic valve lifters for each engine valve.
• the valve lifters are typically controlled by a pair of control valve assemblies-each control valve assembly having a two-position valve spool selectively moved by a pair of solenoid actuators. Fluid pressure is distributed to each control valve by a switching valve, which also includes a two-position valve spool controlled by a pair of solenoid actuators.
• the control valve assemblies and the switching valve are controlled by an engine controller, so that timing of the valve spool movement from one position to the other is a function of engine crankshaft position.
• Each engine valve is selectively opened and closed as one of the control valve spools selectively connects an engine valve actuator to a control pressure or to a low-pressure reservoir.
• control valve spools for each engine valve actuator are switched between their two positions by alternately energizing and de-energizing the solenoid actuators.
• Designers continue to improve upon conventional control valve assembly designs to enhance the overall efficiency of the system.
• a control valve assembly includes a valve body having a valve opening, a first pressure passage, a second pressure passage, and a valve body land.
• a valve member is received in the valve opening for movement between an open and a closed position.
• the valve member includes a first valve member land and a second valve member land.
• the first valve member land and the valve body land cooperate to define a first metering flow passage between the first and second pressure passages
• the valve body land and the second valve member land cooperate to define a second metering flow passage between the first and second pressure passages.
• the first and second metering flow passages are configured to impart a hydrodynamic force on the valve member during fluid flow through the valve body, which biases the valve member toward the open position or the closed position.
• FIG. 1 is a schematic diagram of a hydraulically operated engine valve system using a switching valve and two control valve assemblies according to the present invention
• FIG. 3 is an enlarged cross-sectional view of the control valve assembly of FIG. 2, showing the flow of fluid between a valve member and a valve body;
• FIG. 4A is an enlarged cross-sectional view of the control valve assembly of FIG. 2, showing the valve member in a closed position;
• FIG. 4B is an enlarged cross-sectional view of the control valve assembly of FIG. 2, showing the valve member during its initial movement from the closed position;
• FIG. 4C is an enlarged cross-sectional view of the control valve assembly of FIG. 2, showing the valve member between the closed and an open position;
• FIG. 4D is an enlarged cross-sectional view of the control valve assembly of FIG. 2, showing the valve member in an open position; and [0013] FIG. 5 is a plot showing the force acting on the valve member shown in FIGS. 4A-4D at various valve member displacements.
• FIG. 1 illustrates, schematically, a hydraulically operated engine valve system 10 that includes a two-position switching valve 12.
• a pressure inlet port 14 provides a pressure distribution path to a control pressure passage 16 when a first solenoid 18 is energized.
• control pressure passage 16 is connected with a reservoir low-pressure passage 22.
• Passage 16 communicates with a pair of control valve assemblies 24, 26 according to the present invention.
• each control valve assembly 24, 26 includes a two-position valve member that is controlled by at least one, but more likely two solenoid actuators 28, 30.
• valve member When the solenoid actuator 28 is energized, the valve member is shifted to an open position to provide passage 16 in communication with engine valve actuator 32, 34.
• solenoid actuator 30 When solenoid actuator 30 is energized and solenoid actuator 28 is de-energized, the valve member is moved to a closed position to block communication between passage 16 and an engine valve actuator 32, 34.
• Actuators 32, 34 open an engine valve 36 when the actuator is pressurized and a valve spring 38 closes the engine valve 36 when the actuator is depressurized.
• FIG. 2 is a cross-sectional view of control valve assemblies 24, 26 according to an embodiment of the present invention.
• control valve assemblies 24, 26 include a valve body 40 having a valve opening or bore 42, a first pressure passage 44, a second pressure passage 46, and a valve body land 50.
• a valve member 52 is received in the valve opening 42 for movement between a closed position (see, e.g., FIG. 4A) and an open position (see, e.g., FIG. 4D).
• the valve member 52 comprises a valve spool having known magnetic properties and the solenoids 28, 30, when energized, produce magnetic flux that imparts a magnetic force on the valve spool.
• the valve member 52 may include a first valve member land 54 and a second valve member land 56. As shown in detail in FIGS. 4B-4D, the first valve member land 54 and the valve body land 50 cooperate to define a first metering flow passage 60 between the first and second pressure passages 44, 46, and the valve body land 50 and the second valve member land 56 cooperate to define a second metering flow passage 62 between the first and second pressure passages 44, 46.
• the valve member 52 may include an annular cavity 64 that cooperates with the valve body 40 to define a flow path (FP) between the first pressure passage 44 and the second pressure passage 46 (see, e.g., FIG. 3).
• the flow path (FP) includes an inlet 66 and an outlet 68-both of which help define the first and second metering flow passages 60, 62 (FIG. 4B-4C), respectively.
• the valve body 40 may also include a second valve body land 70 and a third pressure passage 72
• the valve member 52 may also include a third valve member land 74.
• the second valve member land 56 and the second valve body land 70 cooperate to define a third metering flow passage 76 (FIG. 4B-4C) between the first and third pressure passages 44, 72
• the second valve body land 70 and the third valve member land 74 cooperate to define a fourth metering flow passage 78 between the first and third pressure passages 44, 72.
• valve member 52 When so configured, the valve member 52 may include a second annular cavity 80 (FIG. 4B-4C) that cooperates with the valve body 40 to define a second flow path between the first pressure passage 44 and the third pressure passage 72.
• FIG. 3 demonstrates how hydrodynamic forces can be developed in control valve assembly 24, 26 as the valve member 52 moves relative to the valve body 40.
• the fluid flow changes direction from a path generally perpendicular to an axis (A-A) of the valve member 52 to a path generally parallel to the axis, and then back to a path generally perpendicular to the axis of the valve member.
• FIGS. 4A-4D With the relationship between the hydrodynamic force (F) applied to the valve member by the fluid flow and the valve member displacement ( ⁇ ) being depicted graphically in FIG. 5. Displacement of the valve member 52 at the various positions shown in FIGS. 4A-4D is denoted by the figure number in FIG. 5.
• valve member 52 In FIG. 4A, the valve member 52 is in its closed position with no fluid flow between first pressure passage 44 and second or third pressure passages 46, 72. Accordingly, as shown in FIG. 5, there is little or no hydrodynamic force acting on the valve member 52.
• the net hydrodynamic force (F) increases as the fluid flow path is opened until it reaches a maximum force corresponding to the displacement shown in FIG. 4B.
• the net hydrodynamic force (F) opposing the solenoid force decreases until dimension "X-i" is generally equal to "Yi", and "X 2 " is generally equal to "Y 2 ", at which point there is no hydrodynamic force opposing the solenoid force (see Point 4C in FIG. 5).

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Magnetically Actuated Valves (AREA)
• Valve Device For Special Equipments (AREA)
• Fluid-Pressure Circuits (AREA)
• Lift Valve (AREA)

Applications Claiming Priority (3)

Publications (1)

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Family Applications (1)

Country Status (3)

Family Cites Families (4)

• 2007
  • 2007-10-17 EP EP07825686A patent/EP2076700A2/de not_active Withdrawn
  • 2007-10-17 WO PCT/IB2007/003526 patent/WO2008047233A2/en not_active Ceased
  • 2007-10-17 JP JP2009532910A patent/JP2010507057A/ja active Pending

Non-Patent Citations (1)

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