EP1543221B1 - Hydraulic valve actuator for reciprocating engine - Google Patents

Hydraulic valve actuator for reciprocating engine Download PDF

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Publication number
EP1543221B1
EP1543221B1 EP03750820A EP03750820A EP1543221B1 EP 1543221 B1 EP1543221 B1 EP 1543221B1 EP 03750820 A EP03750820 A EP 03750820A EP 03750820 A EP03750820 A EP 03750820A EP 1543221 B1 EP1543221 B1 EP 1543221B1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
selector
opening
rotor
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.)
Expired - Lifetime
Application number
EP03750820A
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German (de)
French (fr)
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EP1543221A1 (en
Inventor
Vianney Rabhi
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Individual
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Individual
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Publication of EP1543221A1 publication Critical patent/EP1543221A1/en
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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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • 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
    • 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
    • F01L1/02—Valve drive
    • F01L1/024—Belt drive
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L2001/0535—Single overhead camshafts [SOHC]
    • 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
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/21—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids
    • F01L2009/2125—Shaft and armature construction
    • F01L2009/2126—Arrangements for amplifying the armature stroke
    • 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
    • F01L2013/0052—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 with cams provided on an axially slidable sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement

Definitions

  • the present invention relates to a hydraulic actuator for controlling the lift, the advance to the opening and / or the closing delay of the valves of the piston engines.
  • the opening point of the piston engine valves as a function of the rotation angle of the crankshaft is defined by the angular phasing of the camshaft (s) relative to said crankshaft.
  • the opening time and the lifting of the valves are defined by the cam profile. In general, and in the majority of engines currently produced by the automotive industry, these characteristics are fixed.
  • the control of the Delay Closure Admission allows the adjustment of the charge introduced into the cylinder by "back-flow", that is to say, by returning to the intake manifold of the fresh gases admitted in excess.
  • This technique finds all its interest on engines with variable volumetric ratio because it authorizes the implementation of the cycle of Atkinson which presents a higher yield with partial loads than that of Otto or Beau de Rochas.
  • the "back-flow" obtained by the Closure-Admission Delay control makes it possible to control the effective compression stroke, which makes it possible to provide a higher volumetric ratio with better efficiency at partial loads. and allows a better control of rattling and performance at all regimes.
  • lift control limits the depth of the valve recess in the piston (piston-shaped fingerprints) by allowing the partial-load valves to lower when the volumetric ratio is reached. is high.
  • Certain devices such as the one known under the trade name "VTec” of “Honda” or the “Variocam Plus” of “Porsche” comprise two different cam profiles that make it possible to choose, according to the engine speed, between two different laws of lifting of intake valves.
  • Solenoid solenoid actuators currently have the best level of parameterization, but notable defects make it difficult to industrialize them, including overconsumption of energy, the panic of valves at high speeds, the lack of progressivity when the valves are resting on their seats, overheating of their electrical components, or the need to provide a higher supply voltage than is ordinarily produced on the vehicle. In addition, their manufacturing cost is high and their reliability is difficult to ensure throughout the life of a vehicle.
  • Electrohydraulic devices have also been developed, such as that particularly intended for low-speed engines built by "Sturman” in the United States in collaboration with “Siemens”.
  • the device according to the invention makes it possible to implement most of the strategies for improving the power, the efficiency and the control of emissions by controlling the opening advance, opening time and lifting. of valves.
  • the device according to the invention has a level of reliability and a cost of production compatible with the requirements of the automotive industry.
  • FIGS. 1 to 3 and 22 show a hydraulic actuator 1 comprising at least one hydraulic cylinder 3 which is connected to a high-pressure hydraulic circuit 10 via a conduit in order to open at least one valve 2 a piston engine 12.
  • the hydraulic actuator 1 comprises at least one volumetric hydraulic pump 4 comprising at least one outlet 6 and at least one inlet 7 and whose rotational speed is proportional to that of the crankshaft 5 of the engine 12.
  • the hydraulic actuator 1 comprises at least one pump outlet shutter 8 which makes it possible to prevent the hydraulic fluid expelled at the outlet 6 of the volumetric hydraulic pump 4 from opening into a low-pressure circuit 9 or into a reservoir 58, and compel it to move towards a high pressure circuit 10 communicating with one or more hydraulic cylinder (s) 3 ensuring the opening of one or more valve (s) 2 of the engine 12.
  • the hydraulic actuator 1 comprises at least one valve opening selector 11 which makes it possible to direct, via the high-pressure circuit 10, the hydraulic fluid expelled at the outlet 6 of the volumetric hydraulic pump 4, to the hydraulic cylinder 3 of at least a valve 2 to allow its opening, while preventing said hydraulic fluid to be directed to one or more other valve (s) 2 to remain closed (s).
  • the hydraulic actuator 1 comprises at least one opening non-return valve 24 placed on the high pressure circuit 10 between the pump outlet 6 and the hydraulic cylinder 3 of at least one valve 2 which makes it possible to retain the fluid hydraulic in said hydraulic cylinder 3 of said valve 2 to keep it open.
  • the hydraulic actuator 1 comprises at least one valve closing selector 25 which makes it possible to direct the hydraulic fluid contained in the hydraulic cylinder 3 of at least one valve 2 kept open by the opening non-return valve 24 towards the input or the inputs 7 of the positive displacement hydraulic pump 4 in order to ensure the closure of the at least one valve (s) 2, and to prevent the hydraulic fluid contained in their hydraulic cylinder 3 from being introduced into the hydraulic cylinder 3 d another or other valve (s) 2 to remain in the closed position.
  • the hydraulic actuator 1 comprises at least one pump inlet check valve 26 which allows the hydraulic fluid of the low pressure circuit 9 or the tank 58 to be admitted to the inlet or the inlet (s) 7 of the volumetric hydraulic pump 4 when the pressure of said low pressure circuit 9 or said reservoir 58 is greater than that of said inlet (s) 7 of the positive displacement hydraulic pump 4 ( Figure 8).
  • At least one of the valves 2 is provided with a measurement device emitting an electrical or electromagnetic signal which informs a computer on the lifting height of the valve at a given instant.
  • the low pressure circuit 9 is connected to the pressurized lubricating circuit 15 of the motor 12.
  • the low pressure circuit 9 can also be provided independently of the pressurized lubricating circuit 15 of the motor 12.
  • the low pressure circuit 9 is independent of the pressure lubrication circuit 15 of the engine 12, the latter can be maintained at a pressure greater than atmospheric pressure by means of an additional pump 13.
  • the low pressure circuit 9 which can then comprise a pressure accumulator 14.
  • the pump outlet shutter 8 and the valve opening selector 11 can be combined into a single combined distributor 81 having at least one input connected to the output 6 of the positive displacement hydraulic pump 4, which can be connected either with an output connected to the low pressure circuit 9, or with an output connected to at least one hydraulic cylinder 3 (FIG. 22).
  • FIGS. 4 to 7 show the hydraulic valve actuator for piston engines whose cylinder and the chamber 20 of the hydraulic cylinder 3 ensuring the opening of the valve (s) 2 are arranged in a valve guide 16, said cylinder and said chamber 20 cooperating with a jack piston consisting of a shoulder 19 arranged on the valve stem 18 to open the valve 2.
  • the jack piston constituted by a shoulder 19 arranged on the valve stem 18 participates in guiding the valve 2 in the valve guide 16.
  • the jack piston consisting of the shoulder 19 on the valve stem 18 comprises at least one seal 17.
  • the valve guide 16 comprises at least one drain 22 close to the intake or exhaust duct 21 that includes the cylinder head of the engine 12 to limit the passage of hydraulic fluid to said intake or exhaust duct 21 (FIG. 5).
  • the hydraulic cylinder 3 ensuring the opening of the valve (s) 2 comprises an end-of-stroke damping device for braking the valve (s) 2 before they come into contact with their seat.
  • the hydraulic cylinder 3 arranged in the valve guide 16 comprises an end-of-stroke damping device which consists of a small shoulder 23, arranged on the valve stem 18.
  • the shoulder 23 cooperates with a cylinder portion of low height and diameter substantially greater than said shoulder 23 formed in the upper part of the valve guide 16 to shear the hydraulic fluid when the valve 2 reaches the end of the closing stroke which has for effect of reducing the speed of said valve 2.
  • the hydraulic cylinder 3 ensuring the opening of at least one valve 2 comprises a purge device at its chamber 20 which consists of a shutter which can be opened by means of a control to allow the hydraulic fluid contained in said chamber 20 to escape to a low pressure circuit.
  • the volumetric hydraulic pump 4 may be a finned pump whose stator has an internal profile which defines at least one independent inlet and outlet.
  • a first variant consists in that the volumetric hydraulic pump 4 may be a gear pump comprising at least two gears and at least one independent inlet and outlet.
  • a second variant consists in that the positive displacement hydraulic pump 4 can be a variable displacement pump which makes it possible to vary the lifting speed of the valve (s) 2 of the engine 12 at a given speed of said engine.
  • FIGS. 11 to 13 an exemplary embodiment of the pump outlet shutter 8 is illustrated.
  • the pump output shutter 8 is a solenoid valve controlled by a computer.
  • the pump outlet shutter 8 is a rotary mechanical device contained in a shutter box 65 and rotating at a speed proportional to that of the crankshaft 5 of the engine 12 and comprising a rotor shutter member 27 provided with at least one protuberance 28 which periodically closes one or more pump outlet ports (s) 29 housed in said shutter housing 65 upon rotation of said shutter rotor 27.
  • the seal between the pump outlet orifice (s) 29 and the protrusions 28 of the shutter rotor 27 is reinforced by a holding device in contact with said one or more outlet orifice (s). pump 29 with said protuberances 28 when they are positioned facing said pump outlet port (s) 29.
  • the holding device 30 is constituted by a shutter piston 31 positioned radially in the shutter housing 65 and which comprises a pump outlet port 29 which passes longitudinally through it.
  • the pump outlet port 29 is connected to a pump outlet duct 32 through a radial orifice 33.
  • the shutter piston 31 has a concave cylindrical bearing surface of radius substantially identical to that of the protuberances 28 so as to have a large contact surface with said protuberances 28.
  • the shutter piston 31 has on the side of the shutter housing 65 a surface subjected to the pressure of the hydraulic fluid greater than the contact surface that it has with the protuberances 28, so that it is kept in contact with the said protuberances when the fluid pressure increases in the pump outlet duct 32 to the passage of said protuberances 28 ( Figure 13).
  • the shutter piston 31 comprises at least one seal ensuring the seal between said shutter piston and the bore in which it is housed.
  • FIGS. 11 and 15 to 19 there is shown the shutter rotor 27 which is provided with an angular phase shift device with respect to the crankshaft 5 of the engine 12 so that the opening of the valve (s) 2 can be advanced or delayed.
  • the phase shifter device of the shutter rotor 27 is constituted by at least one helical groove arranged inside said rotor cooperating with at least one helical groove arranged outside the d-shaft. driving said shutter rotor.
  • phase shift is effected by translation of the shutter rotor 27 parallel to its axis of rotation by means of a fork.
  • the shutter rotor 27 has protuberances which are of sufficient width to close off the pump outlet orifice (s) housed in the shutter casing 65 regardless of their longitudinal position with respect to FIG. these latter.
  • the protuberances 28 are wide and of variable section over the length of the shutter rotor 27, so that they have a shutter time which varies according to the longitudinal position of the shutter rotor 27 with respect to the pump outlet orifice (s) 29, which makes it possible to increase or decrease the lift stroke of the valve (s) 2.
  • the control of the longitudinal position of the shutter rotor 27 with respect to the said pump outlet orifice (s) 29 is effected by means of a valve lift fork 62 which makes it possible to print shutter rotor 27 is translated parallel to its axis of rotation
  • the shutter rotor 27 comprises at least one inner right-hand groove 34 cooperating with at least one outer right-hand groove 76 provided on an opening sheath 37 or any other driving element.
  • the angular phase shift device of the shutter rotor 27 consists of the opening sheath 37 comprising at least one inner helical groove 75 cooperating with at least one outer helical groove 60 that its drive shaft 59 or any other means of training.
  • the opening sheath 37 also comprises at least one outer right groove 76 cooperating with at least one inner right spline 34 provided on the shutter rotor 27.
  • the opening sleeve 37 can be operated in translation parallel to its axis of rotation by a valve opening advance fork 61 in order to to advance or to delay the opening of the valve (s) 2 by angular phase shift of the shutter rotor 27 which causes it to rotate.
  • valve lift fork 62 acts on the longitudinal position of the shutter rotor 27 with respect to the pump outlet port (s). .
  • the shutter rotor 27 may comprise at least one inner right groove cooperating with at least one outer right groove provided on its drive shaft or any other drive element.
  • FIGS. 14 to 19 illustrate an example of a valve opening selector 11 which may be a rotary mechanical device contained in a housing and rotating at a speed proportional to that of the crankshaft 5 of the engine 12.
  • valve opening selector 11 may consist of a or more solenoid valve (s) driven by a computer.
  • valve opening selector 11 is a rotary mechanical device contained in a selector casing 66, rotating at a speed proportional to that of the crankshaft 5 of the engine 12, and comprising a rotor opening selector valve 38 provided with a cam 39 which actuates one or more valve opening distributor (s) 40 arranged radially in the selector housing 66.
  • the aperture selector rotor 38 is provided with an angular phase shift device with respect to the crankshaft 5 of the engine 12 so that the valve opening selector 11 can be synchronized with the pump output shutter. 8 and can select the valve (s) 2 at the desired time.
  • the aperture selector rotor 38 has a cam 39 which is integral with the opening sheath 37, allowing the valve opening selector 11 to remain synchronized with the opening of the valve (s) 2 which depends the angular phase shift of the shutter rotor 27 relative to the crankshaft 5 of the engine 12.
  • valve opening advance fork 61 makes it possible to phase shift simultaneously and in the same proportions the opening selector rotor 38 and the shutter rotor 27 with respect to the crankshaft 5.
  • the angular phase shift device of the aperture selector rotor 38 is constituted by at least one helical groove 77 provided inside said aperture selector rotor 38 cooperating with at least one helical groove 60 arranged outside the aperture selector rotor 38. the drive shaft 59 of said aperture selector rotor 38 or any other drive means.
  • phase shift is effected by means of a fork by translation of said opening selector rotor 38 parallel to its axis of rotation.
  • the cam 39 is of sufficient width to actuate the valve opening distributors 40 regardless of its longitudinal position with respect to said distributors.
  • the valve opening distributor (s) 40 consist of a cylindrical piece 78_munie of one or more grooves (s) 41 and taking place in a bore formed in the selector casing 66.
  • the groove (s) 41 are brought by axial translation of the cylindrical piece 78 printed by the cam 39 at the ducts 42 arranged in the selector casing 66 to allow the circulation of the hydraulic fluid in said ducts.
  • the cylindrical pieces 78 are held at the desired distance from the opening selector rotor 38 by the combined action of a shoulder 44 arranged on said cylindrical pieces 78 and bearing on the housing of selectors 66, and a spring 43 maintained compressed by a plug 45 screwed into said housing.
  • the plug 45 screwed into the selector casing 66 defines a chamber 46 which contains the spring 43 and which is connected to the low pressure circuit 9 or the reservoir 58 by a conduit not shown.
  • valve closing selector 25 which consists of a rotary mechanical device contained in a selector casing 66 and rotating at a speed proportional to that of the crankshaft 5 of FIG. motor 12.
  • valve closing selector 25 may consist of one or more solenoid valves (s) driven (s) by a computer.
  • the valve closing selector 25 comprises a closing selector rotor 47 provided with a cam 48 which actuates one or more valve closing valves 49 arranged radially in the selector housing 66.
  • the closing selector rotor 47 is provided with an angular phase shifter with respect to the crankshaft 5 of the motor 12 so that the closure of the valve (s) 2 can be advanced or delayed.
  • the phase shift device of the closing selector rotor 47 consists of at least one helical groove 79 formed inside the closing selector rotor 47 cooperating with at least one helical groove 60 arranged outside the shaft. 59 or any other drive means of said closing selector rotor 47.
  • the phase shift is effected by translating the closing selector rotor 47 parallel to its axis of rotation by means of a valve closing delay range 63.
  • the cam 48 is of sufficient width to actuate the valve closing valves 49 regardless of its longitudinal position with respect thereto.
  • Valve distributor (s) 49 consist of a cylindrical piece 80 provided with one or more grooves 50 and taking place in a bore formed in the selector casing 66.
  • the groove (s) 50 are brought by axial translation of the cylindrical piece 80 printed by the cam 38 at ducts formed in the selector casing 66 to allow the circulation of the hydraulic fluid in said ducts.
  • the cylindrical pieces 80 are held at the desired distance from the closing selector rotor 47 by the combined action of a shoulder 51 provided on said cylindrical pieces 80 and resting on the selector housing 66, and a spring 52 maintained compressed by a plug 53 screwed into said housing.
  • the plug 53 screwed into the selector casing 66 defines a chamber 73 which contains the spring 52 and which is connected to the low pressure circuit 9 or the reservoir 58 by a conduit not shown.
  • the high pressure circuit 10 comprises at least one closure check valve 54 upstream or downstream of the valve closing selector 25 to prevent the hydraulic fluid contained in the hydraulic cylinder 3 from one or more valves (s). ) 2 in the closing phase can not be introduced into the hydraulic cylinder 3 of another or other valve (s) 2 to remain closed (s).
  • the closing check valve 54 positioned upstream or downstream of the valve closing selector 25, consists of a ball held on its seat by a spring.
  • pump inlet check valve 26 consists of a ball held on its seat by a spring.
  • FIGS. 20 and 21 there is illustrated a common casing consisting of one or more pieces in which are contained together or in groups the components that are the volumetric hydraulic pump 4, the pump outlet shutter 8, the selector of FIG. valve opening 11, the non-return valve (s) opening 24, the valve closing selector 25 and the closing non-return valve (s) 54.
  • the volumetric hydraulic pump 4, the shutter rotor 27, the selector rotor 38, and the closing selector rotor 47, or any combination of these four devices are rotated by a common shaft 59 itself driven by rotation by the crankshaft 5 of the engine 12 by means of a transmission device (FIGS. 15 to 19).
  • the transmission device driving the common shaft 59 consists of a pulley 74 driven in rotation by the crankshaft 5 of the engine 12 by means of a toothed belt or chain, or a gear system consisting of at least one pinion.
  • the common shaft 59 is provided with at least one helical groove 60 which rotates the shutter rotor 27, the aperture selector rotor 38, the aperture sheath 37 and the closing selector rotor 47 or any combination of these three devices and cooperates with the internal helical grooves of some of these devices to allow the angular phase shift relative to the crankshaft 5 of the engine 12.
  • the shutter housing 65 is traversed by ducts connecting the outlet (s) 6 of the hydraulic displacement pump 4 with the pump outlet shutter (s) 8 on the one hand and with an opening manifold 68 consisting of a ductwork arranged at the joint plane between the shutter housing 65 and the selector casing 66 on the other hand.
  • the shutter housing 65 is traversed by ducts connecting the inlet (s) 7 of the displacement hydraulic pump 4 with a closure manifold 69 consisting of a ductwork arranged at the joint plane between the selector housing 66 and the closing collector housing 67.
  • the selector casing 66 is traversed longitudinally by conduits 42 which connect the opening manifold 68 and the closure manifold 69 and which can be closed or opened by the valve opening distributor (s) 40 and by the or the valve closing distributor (s) 49.
  • the conduits 42 comprise valve starting conduits 70 located between the valve opening distributor (s) 40 and the valve closing distributor (s) 49 which are connected to the hydraulic cylinder 3 of the valves 2.
  • the selector casing 66 is also traversed longitudinally by one or more ducts which connect the closure manifold 69 with the inlet (s) 7 of the volumetric hydraulic pump 4.
  • the opening manifold 68 makes it possible to connect together the ducts passing longitudinally through the selector casing 66 to be connected to the same pump outlet 6.
  • the pump outlet 6 is connected to the opening manifold 68 by a duct which passes through the shutter housing 65.
  • the closure manifold 69 makes it possible to connect together the ducts passing longitudinally through the selector casing 66 to be connected to the same pump inlet 7.
  • the pump inlet 7 is connected to the closure manifold 69 through the ducts which pass respectively through the selector casing 66 and the shutter casing 65.
  • Assembly screws 71 pass right through the various housings 64, 65, 66 and 67 in order to hold them together, one or more of said assembly screws 71 being able to serve as a slide for the forks 61, 62 and 63 which make it possible to control opening, lifting and closing of the valves 2.
  • valve opening advance range 61, the valve lift range 62 and the valve closure delay range 63 are manipulated in translation by computer driven electric motors which are connected to said forks 61, 62 and 63 by transmission means.
  • a same duct connected to the high pressure hydraulic circuit 10 can simultaneously supply several hydraulic cylinders 3 through a flow divider which ensures a substantially identical lift to the valves 2 actuated by said hydraulic cylinders 3.
  • Figure 1 illustrates the block diagram of the device in a four-valve configuration (e.g., to operate the four intake or exhaust valves of a four-cylinder engine).
  • the hydraulic displacement pump 4 delivers hydraulic fluid from the low pressure circuit 9 - in this case the engine lubrication circuit - via the pump inlet check valve 26 and to the lubricant housing of the motor 58 via the pump outlet shutter 8 then open.
  • valve opening selector 11 places the hydraulic cylinder 3 of said valve in relation with the high pressure circuit 10 coming from the output of the positive displacement hydraulic pump 4.
  • the pump outlet shutter 8 then closes the pump outlet conduit 32 which raises the pressure in the high pressure circuit 10 so that the hydraulic cylinder 3 opens the selected valve.
  • the pump outlet shutter 8 reopens the pump outlet pipe 32 which stops the lifting of the valve because the pressure of the high pressure circuit 10 upstream of the opening non-return valve 24 becomes lower than that prevailing in the chamber of the hydraulic cylinder 3 due to the action of the return spring of the valve.
  • valve closing selector 25 which, at the chosen moment, puts the hydraulic cylinder 3 of said valve in relation with the inlet of the positive displacement hydraulic pump 4 via the high pressure circuit 10.
  • the positive displacement hydraulic pump 4 again delivers hydraulic fluid from the low pressure circuit 9 to the lubricant housing of the engine 58 via the pump inlet check valve 26.
  • FIG. 2 is a schematic representation of a circuit whose operation is identical to the preceding one, but which is intended to actuate the 8 intake or exhaust valves of a four-cylinder engine with two intake or exhaust valves per cylinder.
  • a rotor pump with a single rotor but with an inner cam defining two insulated inputs and two outputs can be used as illustrated in FIG.
  • the pump outlet shutter 8, the valve opening selector 11 and the valve closing selector 25 can be made by means of solenoid valves, but the fragility, the lack of robustness and the lack of regularity of operation of said valves solenoid valves in the context of a heat engine make such achievements difficult.
  • said solenoid valves are advantageously replaced by the mechanical device shown in Figures 15 to 21 which provides the reliability and consistency of operation sought in the automotive engine.
  • the device shown in these figures is particularly intended to actuate the eight intake or exhaust valves of a four-cylinder engine with two intake valves or two exhaust valves per cylinder.
  • the common shaft 59 is rotated by the motor 12 by means of the pulley 74 rotating at the same speed as a conventional camshaft, or at half the speed of the crankshaft 5 of the engine 12, here in the clockwise when the device is seen on the pulley side 74.
  • the entire device can be placed in place of the camshaft it replaces (for example, the intake camshaft) and can be driven, as shown in Figure 9, by the timing belt of the engine with another camshaft (eg, the exhaust camshaft), or further driven by said belt as shown in Figure 10 with another identical device.
  • the volumetric hydraulic pump 4 is of the finned type with an inner cam defining two pump inlets 7 and two pump outputs 6 that are not communicating with each other, the pump inlet check valves 26 are connected to the low pressure circuit 9 In this case, the pressure lubrication circuit of the motor 12, and consist of balls held in abutment on their seat by a spring.
  • the displacement hydraulic pump 4 expels the hydraulic fluid via the pump outlet conduit 32 into the internal cavity of the shutter housing 65, said cavity being connected by a conduit not shown to the oil sump engine lubrication 72.
  • the common shaft 59 is provided with helical splines 60, these splines rotating the shutter rotor 27, the opening selector rotor 38 and the closing selector rotor 47.
  • the shutter rotor 27 and the opening selector rotor 38 remain phased relative to each other because they are integral in rotation with the same sleeve 37, which guarantees a constant duration between the selection of a valve 2 and the start of shutting off the pump outlet 6.
  • the pump outlet shutters 8 are here two in number arranged diametrically opposite in the housing, and each one close one of the two pump outputs 6 of the hydraulic displacement pump 4, each pump outlet 8 being assigned exclusively to the opening is 2-pair valves or odd-order valves 2 of the engine cylinders 12.
  • the two pump inputs 7 are assigned exclusively to the closing of either the 2-pair valves or the odd-order 2 valves of the cylinders of the engine 12.
  • the shutter rotor 27 comprises four protuberances 28 of variable profile placed every ninety degrees.
  • valves 2 open at a constant speed at a given engine speed 12, the longer they are operated for a long time in opening, the higher their lifting height will be important.
  • valve lift range 62 makes it possible to control the lift height of the valves 2, said fork being operated by an electric motor (not shown) controlled by a computer (not shown).
  • the starting point of opening of the valves 2 can be controlled independently of the lifting of the valves 2 by moving in longitudinal translation the opening sheath 37 with respect to the common shaft 59 by means of the advance fork opening of the valve 61.
  • the valve opening advance fork 61 is operated by an electric motor not shown controlled by a computer not shown.
  • valve opening selector 11 and the valve closing selector 25 both fall within the same operating principle.
  • cam 39 of the opening selector actuates opening a valve opening distributor 40 every ninety degrees of rotation of the common shaft 59, ie every one hundred and eighty degrees of rotation. crankshaft 5, in accordance with the requirements of a four-cylinder engine operating on the four-stroke cycle Otto or Beau de Rochas.
  • Each valve opening distributor 40 simultaneously opens or closes the conduits 42 for supplying the hydraulic fluid to the hydraulic cylinders 3 of a pair of valves 2 and an odd valve 2 of the same cylinder.
  • the cylindrical piece 78 is brought back to the desired distance with respect to the cam 39 by its shoulder 44 kept in contact with the selector casing 66 by the spring 43.
  • the starting point of closure of the valves 2 is controlled by moving in longitudinal translation the closing selector rotor 47 with respect to the common shaft 59 by means of the valve closing delay range 63.
  • the common housing may comprise a base in which is housed at least one hydraulic cylinder 3, said base being fixed on the cylinder head of the engine 12 so that each hydraulic cylinder 3 is in contact with the upper end of the tail of the corresponding valve 2 of said motor 12 and can actuate said valve.

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

Abstract

A hydraulic valve actuator for reciprocating engine includes at least a hydraulic cylinder ( 3 ) for opening at least one valve ( 2 ) via at least one valve opening selector ( 11 ) with at least one hydraulic positive displacement pump ( 4 ) whereof the hydraulic fluid supplied at the output can be forced into a high pressure circuit ( 10 ) by at least one pump outlet closure ( 8 ), the valve ( 2 ) capable of being maintained opened by an opening non-return valve ( 24 ), then of being reseated by a valve closing selector ( 25 ) which directs the hydraulic fluid contained in the hydraulic cylinder ( 3 ) in the hydraulic positive displacement pump ( 4 ) input by co-operating with a pump input non-return valve ( 26 ).

Description

La présente invention est relative à un actionneur hydraulique permettant le contrôle de la levée, de l'Avance à l'Ouverture et/ou du Retard à la Fermeture des soupapes des moteurs à pistons.The present invention relates to a hydraulic actuator for controlling the lift, the advance to the opening and / or the closing delay of the valves of the piston engines.

Actuellement, le point d'ouverture des soupapes des moteurs à piston en fonction de l'angle de rotation du vilebrequin est défini par le phasage angulaire du ou des arbres à cames par rapport audit vilebrequin. La durée d'ouverture et la levée des soupapes sont définies par le profil de came. En règle générale et dans la majorité des moteurs actuellement produits par l'industrie automobile, ces caractéristiques sont fixes.Currently, the opening point of the piston engine valves as a function of the rotation angle of the crankshaft is defined by the angular phasing of the camshaft (s) relative to said crankshaft. The opening time and the lifting of the valves are defined by the cam profile. In general, and in the majority of engines currently produced by the automotive industry, these characteristics are fixed.

L'expérience a mis en évidence l'intérêt de contrôler les paramètres que sont le point d'ouverture, la durée d'ouverture et la levée des soupapes des moteurs à combustion interne à pistons utilisés en automobile. En effet, ces paramètres ont une forte incidence sur le remplissage du ou des cylindre(s) et sur les conditions de combustion, et les contrôler en marche permet d'optimiser le rendement et la puissance en fonction du régime de rotation du moteur et de la charge recherchée, et de maîtriser les émissions.Experience has shown the importance of controlling the parameters of the opening point, the opening time and the lifting of the valves of internal combustion piston engines used in automobiles. Indeed, these parameters have a strong impact on the filling of the cylinder (s) and the combustion conditions, and control in operation optimizes the efficiency and power depending on the engine rotation speed and the desired load, and control emissions.

Le contrôle de ces paramètres permet notamment :

  • De disposer d'un couple élevé à tous régimes de rotation en provoquant l'ouverture et la fermeture des soupapes d'admission et/ou d'échappement au moment le plus propice au remplissage maximal du cylindre tenant compte notamment de l'inertie des gaz dans les tubulures d'admission et d'échappement.
  • De disposer d'une puissance maximale élevée sans pénaliser le couple et la souplesse du moteur à faibles régimes de rotation.
  • De régler la charge introduite dans le cylindre par vannage directement au niveau de la soupape au lieu d'avoir recours à un papillon en agissant sur la levée et/ou le temps d'ouverture de la ou des soupape(s) d'admission, ceci limitant les pertes par pompage nuisibles au rendement du moteur.
  • De disposer d'une meilleure maîtrise de la turbulence dans la chambre de combustion notamment grâce au contrôle de la hauteur de levée de soupape qui permet de maîtriser la vitesse des gaz introduits dans le cylindre, et de ce fait, de contrôler l'homogénéité du mélange air/carburant et la vitesse de combustion.
  • De régler le taux de gaz brûlés dilués dans la charge introduite dans le ou les cylindre(s) notamment en choisissant un croisement de soupapes (temps où les soupapes d'admission et d'échappement sont ouvertes simultanément dans un même cylindre) plus ou moins important, ce qui permet un meilleur contrôle des émissions et du rendement, et permet une moindre dispersion cyclique (irrégularités de combustion, ratés d'allumage) ce qui autorise un abaissement du régime de ralenti du moteur.
The control of these parameters allows in particular:
  • To have a high torque at all speeds of rotation by causing the opening and closing of the intake and / or exhaust valves at the most favorable moment for the maximum filling of the cylinder taking into account in particular the inertia of the gases in the intake and exhaust manifolds.
  • To have a high maximum power without penalizing the torque and the flexibility of the engine at low speeds of rotation.
  • To regulate the charge introduced into the cylinder by valveing directly at the level of the valve instead of resorting to a throttle by acting on the lifting and / or the opening time of the valve (s) of admission, this limits pumping losses that are detrimental to engine performance.
  • To have a better control of the turbulence in the combustion chamber in particular by controlling the valve lift height which makes it possible to control the speed of the gases introduced into the cylinder, and thus, to control the homogeneity of the air / fuel mixture and the rate of combustion.
  • To regulate the rate of diluted flue gases in the charge introduced into the cylinder (s), in particular by choosing a crossover of valves (time when the intake and exhaust valves are simultaneously open in the same cylinder) more or less important, which allows a better control of the emissions and the yield, and allows a less cyclic dispersion (irregularities of combustion, misfires) which authorizes a lowering of the idling speed of the engine.

En outre, le contrôle du Retard Fermeture Admission autorise le réglage de la charge introduite dans le cylindre par «back-flow», autrement dit, par retour dans la tubulure d'admission des gaz frais admis en excès. Cette technique trouve tout son intérêt sur les moteurs à rapport volumétrique variable car elle autorise la mise en oeuvre du cycle d'Atkinson qui présente un rendement plus élevé à charges partielles que celui d'Otto ou Beau de Rochas.In addition, the control of the Delay Closure Admission allows the adjustment of the charge introduced into the cylinder by "back-flow", that is to say, by returning to the intake manifold of the fresh gases admitted in excess. This technique finds all its interest on engines with variable volumetric ratio because it authorizes the implementation of the cycle of Atkinson which presents a higher yield with partial loads than that of Otto or Beau de Rochas.

Sur moteur atmosphérique ou suralimenté à rapport volumétrique fixe, le «back-flow» obtenu par le contrôle du Retard Fermeture Admission permet de contrôler la course effective de compression, ce qui permet de prévoir un rapport volumétrique plus élevé offrant un meilleur rendement à charges partielles et autorise une meilleure maîtrise du cliquetis et du rendement à tous régimes.On an atmospheric or turbocharged engine with a fixed compression ratio, the "back-flow" obtained by the Closure-Admission Delay control makes it possible to control the effective compression stroke, which makes it possible to provide a higher volumetric ratio with better efficiency at partial loads. and allows a better control of rattling and performance at all regimes.

Sur moteur à taux variable, le contrôle de la levée permet de limiter la profondeur de l'embrèvement des soupapes dans le piston (empreintes ayant la forme des soupapes sur le piston) en autorisant une moindre levée des soupapes à charges partielles lorsque le rapport volumétrique est élevé.On a variable rate engine, lift control limits the depth of the valve recess in the piston (piston-shaped fingerprints) by allowing the partial-load valves to lower when the volumetric ratio is reached. is high.

Diverses technologies existent qui permettent de contrôler tout ou partie de ces paramètres que sont l'avance ouverture, la durée d'ouverture et la levée des soupapes sur les moteurs à combustion interne à pistons voir par exemple document de brevet DE-A-4232573 : depuis de simples déphaseurs d'arbre à cames qui sont industrialisés, jusqu'aux dispositifs électromécaniques ou électro-hydrauliques offrant un contrôle de l'ensemble des dits paramètres mais qui restent au stade expérimental car ils présentent des défauts importants de surcoût, de fiabilité, de contrôlabilité ou de surconsommation énergétique.Various technologies exist which make it possible to control all or part of these parameters which are the opening advance, the duration of opening and the lifting of the valves on piston internal combustion engines, see for example DE-A-4232573: from simple industrialized camshaft phase shifters, up to electromechanical or electro-hydraulic devices offering control of all of these parameters but which remain at the experimental stage because they have significant defects in additional cost, reliability, controllability or energy consumption.

Divers déphaseurs d'arbre à cames et dispositifs de contrôle de levée sont commercialisés en grande série mais ils sont chers et présentent des limites de contrôlabilité : les déphaseurs simples à plusieurs positions prédéfinies ou à variation continue ne permettent pas de contrôler indépendamment l'avance ouverture et le retard fermeture des soupapes et donc, ne permettent pas le contrôle de la durée d'ouverture. En outre, ils ne permettent pas le contrôle de la levée.Various camshaft phase shifters and lift control devices are marketed in large series but they are expensive and have controllability limits: the simple phase shifters with predefined or continuously variable positions do not allow independent control of the opening advance. and the delayed closing of the valves and thus, do not allow the control of the duration of opening. In addition, they do not allow control of the lift.

Certains dispositifs comme celui connu sous l'appellation commerciale «VTec» de «Honda» ou le «Variocam Plus» de «Porsche» comportent deux profils de came différents qui permettent de choisir en fonction du régime du moteur entre deux lois différentes de levée des soupapes d'admission.Certain devices such as the one known under the trade name "VTec" of "Honda" or the "Variocam Plus" of "Porsche" comprise two different cam profiles that make it possible to choose, according to the engine speed, between two different laws of lifting of intake valves.

Le dispositif le plus élaboré qui soit commercialisé actuellement est vraisemblablement celui connu sous l'appellation commerciale «Valvetronic» développé par «BMW» qui autorise le contrôle de la levée des soupapes, et qui, couplé à des «Vanos» de déphasage des arbres à cames, permet de régler la presque totalité des paramètres à l'exception du réglage du retard fermeture qui reste lié à celui de l'avance ouverture ce qui interdit le contrôle du temps d'ouverture des soupapes.The most elaborate device that is currently marketed is probably the one known under the trade name "Valvetronic" developed by "BMW" which allows the control of the lifting of the valves, and which, coupled with "Vanos" of phase shift of the trees to cams, allows to adjust almost all parameters except for the setting of the closing delay which remains linked to that of the opening advance which prohibits the control of the opening time of the valves.

Les actionneurs électromagnétiques par solénoïdes présentent actuellement le meilleur niveau de paramétrage, mais des défauts notables rendent difficile leur industrialisation parmi lesquels la surconsommation énergétique, l'affolement des soupapes à hauts régimes, le manque de progressivité lors de la repose des soupapes sur leur siège, la surchauffe de leurs composants électriques, ou la nécessité de prévoir une tension électrique d'alimentation plus élevée que celle ordinairement produite sur le véhicule. En outre, leur prix de revient en fabrication est élevé et leur fiabilité est difficile à assurer sur toute la durée de vie d'un véhicule.Solenoid solenoid actuators currently have the best level of parameterization, but notable defects make it difficult to industrialize them, including overconsumption of energy, the panic of valves at high speeds, the lack of progressivity when the valves are resting on their seats, overheating of their electrical components, or the need to provide a higher supply voltage than is ordinarily produced on the vehicle. In addition, their manufacturing cost is high and their reliability is difficult to ensure throughout the life of a vehicle.

Des dispositifs électro-hydrauliques ont été également développés tels que celui particulièrement destiné aux moteurs à faible régime de rotation construit par «Sturman» aux Etat-Unis en collaboration avec «Siemens».Electrohydraulic devices have also been developed, such as that particularly intended for low-speed engines built by "Sturman" in the United States in collaboration with "Siemens".

Qu'il s'agisse des actionneurs électromagnétiques ou électro-hydrauliques, ces dispositifs présentent l'inconvénient de consommer beaucoup d'énergie ce qui réduit leur intérêt en termes d'amélioration de rendement du moteur.Whether electromagnetic or electro-hydraulic actuators, these devices have the disadvantage of consuming a lot of energy which reduces their interest in terms of improving engine efficiency.

Aucune technologie n'existe aujourd'hui qui soit à la fois simple, fiable, économe en énergie, facile à industrialiser, peu onéreuse et qui autorise le contrôle indépendant de l'avance ouverture, du retard fermeture et de la levée des soupapes des moteurs à combustion interne à pistons.No technology exists today that is simple, reliable, energy efficient, easy to industrialize, inexpensive and allows independent control of the opening advance, the closing delay and the lifting of the engine valves. internal combustion piston.

C'est pour répondre à l'indisponibilité d'une telle technologie pour l'industrie du moteur automobile que le dispositif selon l'invention autorise, selon un mode particulier de réalisation :

  • Le contrôle indépendant de l'avance à l'ouverture des soupapes.
  • Le contrôle indépendant du retard à la fermeture des soupapes.
  • Le contrôle indépendant de la levée des soupapes.
  • Un fonctionnement peu bruyant et peu dispendieux en énergie.
It is to respond to the unavailability of such a technology for the automotive engine industry that the device according to the invention allows, according to a particular embodiment:
  • Independent control of the opening advance of the valves.
  • Independent control of valve closing delay.
  • Independent control of the lift of the valves.
  • A quiet operation and inexpensive energy.

De ce fait, le dispositif selon l'invention permet la mise en oeuvre de l'essentiel des stratégies d'amélioration de la puissance, du rendement et du contrôle des émissions par le contrôle de l'avance ouverture, durée d'ouverture et levée de soupapes. En outre, le dispositif selon l'invention présente un niveau de fiabilité et un coût de production compatibles avec les impératifs de l'industrie automobile.As a result, the device according to the invention makes it possible to implement most of the strategies for improving the power, the efficiency and the control of emissions by controlling the opening advance, opening time and lifting. of valves. In addition, the device according to the invention has a level of reliability and a cost of production compatible with the requirements of the automotive industry.

Le dispositif selon l'invention se distingue des dispositifs d'entraînement de soupapes selon l'art antérieur en ce que :

  • a) L'arbre à cames est supprimé, ainsi que les éventuels culbuteurs.
  • b) La culasse est simplifiée notamment grâce à la suppression de la ligne d'arbre à cames ordinairement matérialisée par des paliers et leur dispositif de lubrification, et grâce à la suppression des alésages de poussoirs de soupapes.
  • c) Selon un mode particulier de réalisation, l'encombrement vertical du moteur peut être réduit grâce à la suppression de l'arbre à cames.
  • d) La masse alternative de l'ensemble constitué par les soupapes et leur dispositif d'entraînement est réduite notamment grâce à la suppression des poussoirs et/ou des culbuteurs, ce qui réduit l'effort nécessaire à l'accélération et à la décélération dudit ensemble lors de l'ouverture et de la fermeture des soupapes.
  • e) Les dispositifs de réglage du jeu entre cames et poussoirs tels que pastille de réglage, vis de réglage ou poussoir hydraulique sont supprimés.
  • f) L'orientation des soupapes dans la culasse est facilitée.
The device according to the invention differs from the valve drive devices according to the prior art in that:
  • a) The camshaft is removed, as well as any rocker arm.
  • b) The cylinder head is simplified in particular by the removal of the camshaft line ordinarily materialized by bearings and their lubrication device, and by the removal of the bores of valve lifters.
  • c) According to a particular embodiment, the vertical size of the motor can be reduced by removing the camshaft.
  • d) The alternative mass of the assembly constituted by the valves and their driving device is reduced in particular by the suppression of the pushers and / or rockers, which reduces the effort required for the acceleration and deceleration of said together when opening and closing the valves.
  • e) The adjustment devices of the play between cams and pushers such as setting pad, adjustment screw or hydraulic push button are removed.
  • f) The orientation of the valves in the cylinder head is facilitated.

Ainsi l'actionneur hydraulique de soupapes pour moteurs à pistons suivant la présente invention comprend:

  • Figure imgb0001
    au moins un vérin hydraulique raccordé à un circuit hydraulique haute pression par un conduit, et assurant l'ouverture d'au moins une soupape,
  • Figure imgb0002
    au moins une pompe hydraulique volumétrique comprenant au moins une sortie et au moins une entrée dont la vitesse de rotation est proportionnelle à celle_du vilebrequin du moteur,
  • Figure imgb0003
    au moins un obturateur de sortie de pompe qui permet d'empêcher le fluide hydraulique expulsé à la sortie de la pompe hydraulique volumétrique de déboucher dans un circuit basse pression ou dans un réservoir, et de le contraindre à se diriger vers_un circuit haute pression communiquant avec un ou plusieurs vérin(s) hydraulique(s) assurant l'ouverture d'une ou plusieurs soupape(s),
  • Figure imgb0004
    au moins un sélecteur d'ouverture de soupapes qui permet de diriger via le circuit haute pression le fluide hydraulique expulsé en sortie de la pompe hydraulique volumétrique vers le vérin hydraulique d'au moins une soupape devant être ouverte, tout en interdisant audit fluide hydraulique d'être dirigé vers une ou plusieurs autres soupape(s) devant rester fermée(s),
  • Figure imgb0005
    au moins un clapet anti-retour d'ouverture placé sur le circuit haute pression entre la sortie de pompe et le vérin hydraulique d'au moins une soupape qui permet de retenir le fluide hydraulique dans ledit vérin hydraulique de ladite soupape afin de la maintenir ouverte,
  • Figure imgb0006
    au moins un sélecteur de fermeture de soupapes qui permet de diriger le fluide hydraulique contenu dans le vérin hydraulique d'au moins une soupape maintenue ouverte par le clapet anti-retour d'ouverture vers l'entrée ou les entrées de la pompe hydraulique volumétrique afin d'assurer la fermeture de la ou desdites soupape(s), et d'empêcher le fluide hydraulique contenu dans leur vérin hydraulique d'être introduit dans le vérin hydraulique d'une autre ou d'autres soupape(s) devant rester en position fermée,
  • Figure imgb0007
    et au moins un clapet anti-retour d'entrée de pompe qui permet au fluide hydraulique du circuit basse pression ou du réservoir d'être admis à l'entrée
ou aux entrées de la pompe hydraulique volumétrique lorsque la pression dudit circuit basse pression ou dudit réservoir est supérieure à celle de ladite ou des dites entrée(s) de la pompe hydraulique volumétrique.Thus the hydraulic valve actuator for piston engines according to the present invention comprises:
  • Figure imgb0001
    at least one hydraulic cylinder connected to a high pressure hydraulic circuit by a conduit, and ensuring the opening of at least one valve,
  • Figure imgb0002
    at least one volumetric hydraulic pump comprising at least one outlet and at least one inlet whose rotational speed is proportional to that of the crankshaft of the engine,
  • Figure imgb0003
    at least one pump outlet shutter which makes it possible to prevent the hydraulic fluid expelled at the outlet of the positive displacement hydraulic pump from opening into a low pressure circuit or into a tank, and to force it to move towards a high pressure circuit communicating with one or more hydraulic cylinder (s) ensuring the opening of one or more valves (s),
  • Figure imgb0004
    at least one valve opening selector which makes it possible to direct, via the high-pressure circuit, the hydraulic fluid expelled at the outlet of the positive displacement hydraulic pump towards the hydraulic jack of at least one valve to be opened, while preventing said hydraulic fluid from being be directed to one or more other valve (s) to remain closed (s),
  • Figure imgb0005
    at least one opening check valve placed on the high pressure circuit between the pump outlet and the hydraulic cylinder of at least one valve for retaining the hydraulic fluid in said hydraulic cylinder of said valve to keep it open ,
  • Figure imgb0006
    at least one valve closing selector for directing the hydraulic fluid contained in the hydraulic cylinder of at least one valve held open by the opening check valve to the inlet or inlets of the positive displacement hydraulic pump to to close the valve or valves and to prevent the hydraulic fluid contained in their hydraulic cylinder from being introduced into the hydraulic cylinder of another valve or valves to remain in position; closed
  • Figure imgb0007
    and at least one pump inlet check valve which allows the hydraulic fluid of the low pressure circuit or tank to be admitted to the inlet
or at the inputs of the positive displacement hydraulic pump when the pressure of said low pressure circuit or said tank is greater than that of said inlet (s) of the positive displacement hydraulic pump.

Les autres caractéristiques essentielles de la présente invention ont été décrites dans la description et dans les revendications secondaires dépendantes directement ou indirectement de la revendication principale.The other essential features of the present invention have been described in the description and in the dependent claims directly or indirectly dependent on the main claim.

L'actionneur hydraulique de soupapes pour moteurs à pistons suivant la présente invention comprend :

  • Figure imgb0008
    un vérin hydraulique sur la ou chacune des soupape(s) du moteur qui assure l'ouverture, le maintien en position ouverte, et la fermeture de la ou des dites soupape(s),
  • Figure imgb0009
    une pompe hydraulique volumétrique dont la vitesse de rotation est proportionnelle à celle du vilebrequin,
  • Figure imgb0010
    et un dispositif intégrant un ensemble de vannes et de clapets.
The hydraulic valve actuator for piston engines according to the present invention comprises:
  • Figure imgb0008
    a hydraulic cylinder on the or each valve (s) of the engine which ensures the opening, holding open, and closing the or said valve (s),
  • Figure imgb0009
    a volumetric hydraulic pump whose rotational speed is proportional to that of the crankshaft,
  • Figure imgb0010
    and a device incorporating a set of valves and valves.

Le dispositif intégrant un ensemble de vannes et de clapets à pour fonction :

  • De diriger le fluide hydraulique refoulé en sortie de pompe hydraulique volumétrique vers le vérin hydraulique de la ou des soupape(s) au moment recherché en fonction de la position angulaire du vilebrequin pour assurer la levée de la ou des dite(s) soupape(s).
  • De diriger le fluide hydraulique refoulé en sortie de pompe hydraulique volumétrique vers le vérin hydraulique de la ou des soupape(s) durant le nombre de degrés de rotation de vilebrequin recherché pour assurer la levée de la ou des dite(s) soupape(s) à la hauteur recherchée.
  • De maintenir le fluide hydraulique enfermé dans le vérin hydraulique de la ou des soupape(s) pour maintenir la ou lesdites(s) soupape(s) ouverte(s) durant le nombre de degrés de rotation de vilebrequin recherché.
  • De diriger le fluide hydraulique contenu dans le vérin de la ou des soupape(s) vers l'entrée de la pompe hydraulique volumétrique au moment recherché en fonction de la position angulaire du vilebrequin pour assurer la repose de la ou des dite(s) soupape(s) et récupérer une partie de l'énergie emmagasinée par le ressort de rappel de la ou des soupape(s) lors de l'ouverture de celle(s)-ci.
The device integrating a set of valves and valves to function:
  • Directing the hydraulic fluid discharged at the outlet of the positive displacement hydraulic pump towards the hydraulic cylinder of the valve (s) at the desired moment according to the angular position of the crankshaft to ensure the lifting of the said valve (s) ).
  • Directing the hydraulic fluid discharged at the outlet of the positive displacement hydraulic pump towards the hydraulic cylinder of the valve (s) during the number of degrees of rotation of the crankshaft sought to ensure the lifting of the said valve (s) at the desired height.
  • Maintaining the hydraulic fluid contained in the hydraulic cylinder of the valve (s) to maintain the valve (s) open (s) during the number of degrees of crankshaft rotation sought.
  • Directing the hydraulic fluid contained in the cylinder of the valve (s) to the inlet of the positive displacement hydraulic pump at the desired moment according to the angular position of the crankshaft to ensure the rests of the said valve (s) (s) and recover a portion of the energy stored by the return spring of the valve (s) when opening the one (s) -ci.

Selon un mode particulier de réalisation, le dispositif selon l'invention comporte :

  • Figure imgb0011
    Un ou plusieurs moteur(s) électrique(s) asservi(s) à un ou plusieurs calculateur(s) et qui permettent de contrôler :
    • Le point d'ouverture de la ou des soupape(s) en fonction de la position angulaire du vilebrequin.
    • La hauteur de levée de la ou des soupape(s).
    • Le point de fermeture de la ou des soupape(s) en fonction de la position angulaire du vilebrequin.
  • Figure imgb0012
    Un dispositif de mesure de l'angle du vilebrequin qui, conjugué avec un dispositif de mesure de la levée de soupape, renseigne le ou les calculateur(s) sur le point d'ouverture, la hauteur de la levée et le point de fermeture effectifs de la ou des soupape(s) du moteur. L'ensemble desdits dispositifs de mesure et desdits calculateurs réalisant une boucle de contrôle assurant au mouvement de la ou des soupape(s) du moteur une précision suffisante.
According to a particular embodiment, the device according to the invention comprises:
  • Figure imgb0011
    One or more electric motor (s) servo (s) to one or more computer (s) and which control:
    • The opening point of the valve (s) depending on the angular position of the crankshaft.
    • The lifting height of the valve (s).
    • The closing point of the valve (s) depending on the angular position of the crankshaft.
  • Figure imgb0012
    A crankshaft angle measuring device which, when combined with a valve lift measuring device, informs the computer (s) of the effective opening point, lift height and closing point the valve (s) of the engine. All of said measuring devices and said calculators performing a control loop ensuring the movement of the valve (s) of the engine sufficient accuracy.

La description qui va suivre en regard des dessins annexés, donnés à titre d'exemples non limitatifs, permettra de mieux comprendre l'invention, les caractéristiques qu'elle présente et les avantages qu'elle est susceptible de procurer :

  • Figure 1 illustre le schéma de principe de l'actionneur hydraulique suivant la présente invention selon une configuration à quatre soupapes (par exemple pour actionner les quatre soupapes d'admission d'un moteur à quatre cylindres).
  • Figure 2 est une représentation schématique d'un circuit dont le fonctionnement est identique au précédent, mais qui est destiné, par exemple, à actionner les huit soupapes d'admission d'un moteur quatre cylindres à deux soupapes d'admission par cylindre.
  • Figure 3 est une représentation schématique d'un circuit dont le fonctionnement est identique au précédent, mais qui opère à pression supérieure grâce à une pompe additionnelle, et ceci, afin de limiter les conséquences de la compressibilité du fluide hydraulique et de l'inertie des soupapes sur la précision de fonctionnement du dispositif suivant la présente invention.
  • Figure 4 est une vue en perspective montrant l'actionneur hydraulique suivant la présente invention.
  • Figures 5 à 7 sont des vues illustrant en détail les soupapes d'un moteur pilotées par l'actionneur hydraulique suivant la présente invention.
  • Figure 8 est une vue en coupe montrant les entrées et les sorties de la pompe hydraulique de l'actionneur hydraulique suivant la présente invention.
  • Figures 9 et 10 sont des vues en coupe représentant le positionnement possible de l'actionneur hydraulique suivant la présente invention sur un moteur.
  • Figures 11 à 13 sont des vues illustrant les obturateurs de sortie de pompe de l'actionneur hydraulique suivant la présente invention.
  • Figure 14 est vue en coupe montrant le sélecteur d'ouverture de soupapes de l'actionneur hydraulique suivant la présente invention.
  • Figures 15 à 21 sont des vues représentant l'assemblage des différents éléments constituant l'actionneur hydraulique suivant la présente invention.
  • Figure 22 est une représentation schématique d'un circuit dont le fonctionnement est identique au précédent montré en figure 1 à 3, mais dont l'obturateur de sortie de pompe et le sélecteur d'ouverture de soupapes sont rassemblés en un seul distributeur combiné.
The following description with reference to the accompanying drawings, given by way of non-limiting examples, will provide a better understanding of the invention, the characteristics it has and the advantages that it is likely to provide:
  • Figure 1 illustrates the block diagram of the hydraulic actuator according to the present invention in a four-valve configuration (for example to operate the four intake valves of a four-cylinder engine).
  • Figure 2 is a schematic representation of a circuit whose operation is identical to the previous one, but which is intended, for example, to actuate the eight intake valves of a four-cylinder engine with two intake valves per cylinder.
  • FIG. 3 is a schematic representation of a circuit whose operation is identical to the preceding one, but which operates at higher pressure thanks to an additional pump, and this, in order to limit the consequences of the compressibility of the hydraulic fluid and the inertia of the valves on the operating accuracy of the device according to the present invention.
  • Figure 4 is a perspective view showing the hydraulic actuator according to the present invention.
  • Figures 5 to 7 are views illustrating in detail the valves of a motor driven by the hydraulic actuator according to the present invention.
  • Figure 8 is a sectional view showing the inputs and outputs of the hydraulic pump of the hydraulic actuator according to the present invention.
  • Figures 9 and 10 are sectional views showing the possible positioning of the hydraulic actuator according to the present invention on a motor.
  • Figures 11 to 13 are views illustrating the pump outlet shutters of the hydraulic actuator according to the present invention.
  • Figure 14 is a sectional view showing the valve opening selector of the hydraulic actuator according to the present invention.
  • Figures 15 to 21 are views showing the assembly of the various elements constituting the hydraulic actuator according to the present invention.
  • Figure 22 is a schematic representation of a circuit whose operation is identical to the previous one shown in Figure 1 to 3, but whose pump outlet shutter and the valve opening selector are combined into a single combined distributor.

On a montré en figures 1 à 3 et 22, un actionneur hydraulique 1 comprenant au moins un vérin hydraulique 3 qui est raccordé à un circuit hydraulique haute pression 10 par un conduit afin d'assurer l'ouverture d'au moins une soupape 2 d'un moteur à pistons 12.FIGS. 1 to 3 and 22 show a hydraulic actuator 1 comprising at least one hydraulic cylinder 3 which is connected to a high-pressure hydraulic circuit 10 via a conduit in order to open at least one valve 2 a piston engine 12.

L'actionneur hydraulique 1 comporte au moins une pompe hydraulique volumétrique 4 comprenant au moins une sortie 6 et au moins une entrée 7 et dont la vitesse de rotation est proportionnelle à celle du vilebrequin 5 du moteur 12.The hydraulic actuator 1 comprises at least one volumetric hydraulic pump 4 comprising at least one outlet 6 and at least one inlet 7 and whose rotational speed is proportional to that of the crankshaft 5 of the engine 12.

L'actionneur hydraulique 1 comporte au moins un obturateur de sortie de pompe 8 qui permet d'empêcher le fluide hydraulique expulsé à la sortie 6 de la pompe hydraulique volumétrique 4 de déboucher dans un circuit basse pression 9 ou dans un réservoir 58, et de le contraindre à se diriger vers un circuit haute pression 10 communiquant avec un ou plusieurs vérin(s) hydraulique(s) 3 assurant l'ouverture d'une ou plusieurs soupape(s) 2 du moteur 12.The hydraulic actuator 1 comprises at least one pump outlet shutter 8 which makes it possible to prevent the hydraulic fluid expelled at the outlet 6 of the volumetric hydraulic pump 4 from opening into a low-pressure circuit 9 or into a reservoir 58, and compel it to move towards a high pressure circuit 10 communicating with one or more hydraulic cylinder (s) 3 ensuring the opening of one or more valve (s) 2 of the engine 12.

L'actionneur hydraulique 1 comporte au moins un sélecteur d'ouverture de soupapes 11 qui permet de diriger, via le circuit haute pression 10 le fluide hydraulique expulsé en sortie 6 de la pompe hydraulique volumétrique 4, vers le vérin hydraulique 3 d'au moins une soupape 2 pour permettre son ouverture, tout en interdisant audit fluide hydraulique d'être dirigé vers une ou plusieurs autres soupape(s) 2 devant rester fermée(s).The hydraulic actuator 1 comprises at least one valve opening selector 11 which makes it possible to direct, via the high-pressure circuit 10, the hydraulic fluid expelled at the outlet 6 of the volumetric hydraulic pump 4, to the hydraulic cylinder 3 of at least a valve 2 to allow its opening, while preventing said hydraulic fluid to be directed to one or more other valve (s) 2 to remain closed (s).

L'actionneur hydraulique 1 comporte au moins un clapet anti-retour d'ouverture 24 placé sur le circuit haute pression 10 entre la sortie de pompe 6 et le vérin hydraulique 3 d'au moins une soupape 2 qui permet de retenir le fluide hydraulique dans ledit vérin hydraulique 3 de ladite soupape 2 afin de la maintenir ouverte.The hydraulic actuator 1 comprises at least one opening non-return valve 24 placed on the high pressure circuit 10 between the pump outlet 6 and the hydraulic cylinder 3 of at least one valve 2 which makes it possible to retain the fluid hydraulic in said hydraulic cylinder 3 of said valve 2 to keep it open.

L'actionneur hydraulique 1 comporte au moins un sélecteur de fermeture de soupapes 25 qui permet de diriger le fluide hydraulique contenu dans le vérin hydraulique 3 d'au moins une soupape 2 maintenue ouverte par le clapet anti-retour d'ouverture 24 vers l'entrée ou les entrées 7 de la pompe hydraulique volumétrique 4 afin d'assurer la fermeture de la ou desdites soupape(s) 2, et d'empêcher le fluide hydraulique contenu dans leur vérin hydraulique 3 d'être introduit dans le vérin hydraulique 3 d'une autre ou d'autres soupape(s) 2 devant rester en position fermée.The hydraulic actuator 1 comprises at least one valve closing selector 25 which makes it possible to direct the hydraulic fluid contained in the hydraulic cylinder 3 of at least one valve 2 kept open by the opening non-return valve 24 towards the input or the inputs 7 of the positive displacement hydraulic pump 4 in order to ensure the closure of the at least one valve (s) 2, and to prevent the hydraulic fluid contained in their hydraulic cylinder 3 from being introduced into the hydraulic cylinder 3 d another or other valve (s) 2 to remain in the closed position.

L'actionneur hydraulique 1 comporte au moins un clapet anti-retour d'entrée de pompe 26 qui permet au fluide hydraulique du circuit basse pression 9 ou du réservoir 58 d'être admis à l'entrée ou aux entrée(s) 7 de la pompe hydraulique volumétrique 4 lorsque la pression dudit circuit basse pression 9 ou dudit réservoir 58 est supérieure à celle de ladite ou des dites entrée(s) 7 de la pompe hydraulique volumétrique 4 (figure 8).The hydraulic actuator 1 comprises at least one pump inlet check valve 26 which allows the hydraulic fluid of the low pressure circuit 9 or the tank 58 to be admitted to the inlet or the inlet (s) 7 of the volumetric hydraulic pump 4 when the pressure of said low pressure circuit 9 or said reservoir 58 is greater than that of said inlet (s) 7 of the positive displacement hydraulic pump 4 (Figure 8).

On note que l'une au moins des soupapes 2 est munie d'un dispositif de mesure émettant un signal électrique ou électromagnétique qui renseigne un calculateur sur la hauteur de levée de la soupape à un instant donné.It is noted that at least one of the valves 2 is provided with a measurement device emitting an electrical or electromagnetic signal which informs a computer on the lifting height of the valve at a given instant.

En ce qui concerne le circuit basse pression 9, ce dernier est raccordé au circuit de graissage sous pression 15 du moteur 12. Le circuit basse pression 9 peut être également prévu_indépendant du circuit de graissage sous pression 15 du moteur 12.With regard to the low pressure circuit 9, the latter is connected to the pressurized lubricating circuit 15 of the motor 12. The low pressure circuit 9 can also be provided independently of the pressurized lubricating circuit 15 of the motor 12.

Dans le cas ou le circuit basse pression 9 est indépendant du circuit de graissage sous pression 15 du moteur 12, celui-ci peut être maintenu à une pression supérieure à la pression atmosphérique au moyen d'une pompe additionnelle 13. Le circuit basse pression 9 pouvant alors comporter un accumulateur de pression 14.In the case where the low pressure circuit 9 is independent of the pressure lubrication circuit 15 of the engine 12, the latter can be maintained at a pressure greater than atmospheric pressure by means of an additional pump 13. The low pressure circuit 9 which can then comprise a pressure accumulator 14.

Selon un mode particulier de réalisation, l'obturateur de sortie de pompe 8 et le sélecteur d'ouverture de soupapes 11 peuvent être rassemblés en un seul distributeur combiné 81 comportant au moins une entrée raccordée à la sortie 6 de la pompe hydraulique volumétrique 4, pouvant être mise en relation soit avec une sortie raccordée au circuit basse pression 9, soit avec une sortie raccordée à au moins un vérin hydraulique 3 (figure 22).According to a particular embodiment, the pump outlet shutter 8 and the valve opening selector 11 can be combined into a single combined distributor 81 having at least one input connected to the output 6 of the positive displacement hydraulic pump 4, which can be connected either with an output connected to the low pressure circuit 9, or with an output connected to at least one hydraulic cylinder 3 (FIG. 22).

En figures 4 à 7, on a montré l'actionneur hydraulique de soupapes pour moteurs à pistons dont le cylindre et la chambre 20 du vérin hydraulique 3 assurant l'ouverture de la ou des soupape(s) 2 sont aménagés dans un guide de soupape 16, ledit cylindre et ladite chambre 20 coopérant avec un piston de vérin constitué d'un épaulement 19 aménagé sur la queue de soupape 18 pour ouvrir la soupape 2.FIGS. 4 to 7 show the hydraulic valve actuator for piston engines whose cylinder and the chamber 20 of the hydraulic cylinder 3 ensuring the opening of the valve (s) 2 are arranged in a valve guide 16, said cylinder and said chamber 20 cooperating with a jack piston consisting of a shoulder 19 arranged on the valve stem 18 to open the valve 2.

Le piston de vérin constitué d'un épaulement 19 aménagé sur la queue de soupape 18 participe au guidage de la soupape 2 dans le guide de soupape 16.The jack piston constituted by a shoulder 19 arranged on the valve stem 18 participates in guiding the valve 2 in the valve guide 16.

Le piston de vérin constitué de l'épaulement 19 sur la queue de soupape 18 comporte au moins un joint d'étanchéité 17.The jack piston consisting of the shoulder 19 on the valve stem 18 comprises at least one seal 17.

Le guide de soupape 16 comporte au moins un drain 22 à proximité du conduit d'admission ou d'échappement 21 que comprend la culasse du moteur 12 pour limiter le passage du fluide hydraulique vers ledit conduit d'admission ou d'échappement 21 (figure 5).The valve guide 16 comprises at least one drain 22 close to the intake or exhaust duct 21 that includes the cylinder head of the engine 12 to limit the passage of hydraulic fluid to said intake or exhaust duct 21 (FIG. 5).

Le vérin hydraulique 3 assurant l'ouverture de la ou des soupape(s) 2 comporte un dispositif d'amortissement de fin de course permettant de freiner la ou les soupape(s) 2 avant leur entrée en contact avec leur siège.The hydraulic cylinder 3 ensuring the opening of the valve (s) 2 comprises an end-of-stroke damping device for braking the valve (s) 2 before they come into contact with their seat.

Ainsi, le vérin hydraulique 3 aménagé dans le guide de soupape 16 comporte un dispositif d'amortissement de fin de course qui est constitué d'un petit épaulement 23, aménagé sur la queue de soupape 18.Thus, the hydraulic cylinder 3 arranged in the valve guide 16 comprises an end-of-stroke damping device which consists of a small shoulder 23, arranged on the valve stem 18.

L'épaulement 23 coopère avec une portion de cylindre de faible hauteur et de diamètre sensiblement supérieur audit épaulement 23 aménagée dans la partie supérieure du guide de soupape 16 pour cisailler le fluide hydraulique lorsque la soupape 2 arrive en fin de course de fermeture ce qui a pour effet de réduire la vitesse de ladite soupape 2.The shoulder 23 cooperates with a cylinder portion of low height and diameter substantially greater than said shoulder 23 formed in the upper part of the valve guide 16 to shear the hydraulic fluid when the valve 2 reaches the end of the closing stroke which has for effect of reducing the speed of said valve 2.

Le vérin hydraulique 3 assurant l'ouverture d'au moins une soupape 2 comporte un dispositif de purge au niveau de sa chambre 20 qui est constitué d'un obturateur qui peut être ouvert au moyen d'une commande afin de permettre au fluide hydraulique contenu dans ladite chambre 20 de s'échapper vers un circuit basse pression.The hydraulic cylinder 3 ensuring the opening of at least one valve 2 comprises a purge device at its chamber 20 which consists of a shutter which can be opened by means of a control to allow the hydraulic fluid contained in said chamber 20 to escape to a low pressure circuit.

En figure 8, on a montré la pompe hydraulique volumétrique 4, cette dernière peut être une pompe à ailettes dont le stator présente un profil intérieur qui définit au moins une entrée et une sortie indépendantes.In FIG. 8, the volumetric hydraulic pump 4 has been shown, the latter may be a finned pump whose stator has an internal profile which defines at least one independent inlet and outlet.

Une première variante consiste en ce que la pompe hydraulique volumétrique 4 peut être une pompe à engrenages comportant au moins deux pignons et au moins une entrée et une sortie indépendantes.A first variant consists in that the volumetric hydraulic pump 4 may be a gear pump comprising at least two gears and at least one independent inlet and outlet.

Une seconde variante consiste en ce que la pompe hydraulique volumétrique 4 peut être une pompe à cylindrée variable qui permet de faire varier la vitesse de levée de la ou des soupape(s) 2 du moteur 12 à un régime donné dudit moteur.A second variant consists in that the positive displacement hydraulic pump 4 can be a variable displacement pump which makes it possible to vary the lifting speed of the valve (s) 2 of the engine 12 at a given speed of said engine.

En figures 11 à 13, on a illustré un exemple de réalisation de l'obturateur de sortie de pompe 8.In FIGS. 11 to 13, an exemplary embodiment of the pump outlet shutter 8 is illustrated.

Un autre exemple consisterait en ce que l'obturateur de sortie de pompe 8 soit une électrovanne pilotée par un calculateur.Another example would be that the pump output shutter 8 is a solenoid valve controlled by a computer.

Dans l'exemple montré en figures 11 à 13, l'obturateur de sortie de pompe 8 est un dispositif mécanique rotatif contenu dans un carter d'obturateurs 65 et tournant à une vitesse proportionnelle à celle du vilebrequin 5 du moteur 12 et comportant un rotor d'obturateur 27 muni d'au moins une protubérance 28 venant obturer périodiquement un ou des orifice(s) de sortie de pompe 29 logés dans ledit carter d'obturateurs 65 lors de la rotation dudit rotor d'obturateur 27.In the example shown in FIGS. 11 to 13, the pump outlet shutter 8 is a rotary mechanical device contained in a shutter box 65 and rotating at a speed proportional to that of the crankshaft 5 of the engine 12 and comprising a rotor shutter member 27 provided with at least one protuberance 28 which periodically closes one or more pump outlet ports (s) 29 housed in said shutter housing 65 upon rotation of said shutter rotor 27.

On note que l'étanchéité entre le ou les orifice(s) de sortie de pompe 29 et les protubérances 28 du rotor d'obturateur 27 est renforcée par un dispositif de maintient en contact 30 dudit ou des dits orifice(s) de sortie de pompe 29 avec lesdites protubérances 28 lorsque celles-ci sont positionnées en face dudit ou des dits orifice(s) de sortie de pompe 29.It should be noted that the seal between the pump outlet orifice (s) 29 and the protrusions 28 of the shutter rotor 27 is reinforced by a holding device in contact with said one or more outlet orifice (s). pump 29 with said protuberances 28 when they are positioned facing said pump outlet port (s) 29.

Le dispositif de maintien en contact 30 est constitué d'un piston d'obturateur 31 positionné radialement dans le carter d'obturateurs 65 et qui comprend un orifice de sortie de pompe 29 qui le traverse longitudinalement de part en part.The holding device 30 is constituted by a shutter piston 31 positioned radially in the shutter housing 65 and which comprises a pump outlet port 29 which passes longitudinally through it.

L'orifice de sortie de pompe 29 est relié à un conduit de sortie de pompe 32 par un orifice radial 33. Le piston d'obturateur 31 comporte une face d'appui cylindrique concave de rayon sensiblement identique à celui des protubérances 28 de façon à présenter une large surface de contact avec lesdites protubérances 28.The pump outlet port 29 is connected to a pump outlet duct 32 through a radial orifice 33. The shutter piston 31 has a concave cylindrical bearing surface of radius substantially identical to that of the protuberances 28 so as to have a large contact surface with said protuberances 28.

Le piston d'obturateur 31 présente du coté du carter d'obturateurs 65 une surface soumise à la pression du fluide hydraulique supérieure à la surface de contact qu'il présente avec les protubérances 28, de sorte qu'il est maintenu en contact avec lesdites protubérances lorsque la pression du fluide augmente dans le conduit de sortie de pompe 32 au passage des dites protubérances 28 (figure 13).The shutter piston 31 has on the side of the shutter housing 65 a surface subjected to the pressure of the hydraulic fluid greater than the contact surface that it has with the protuberances 28, so that it is kept in contact with the said protuberances when the fluid pressure increases in the pump outlet duct 32 to the passage of said protuberances 28 (Figure 13).

Lorsque aucune protubérance ne vient obturer l'orifice de sortie de pompe 29 du piston d'obturateur 31, ce dernier est maintenu en appui sur le carter d'obturateurs 65 par un ressort 56 (figure 12).When no protrusion closes the pump outlet port 29 of the shutter piston 31, the latter is held in abutment on the shutter housing 65 by a spring 56 (Figure 12).

Le piston d'obturateur 31 comporte au moins un joint assurant l'étanchéité entre ledit piston d'obturateur et l'alésage dans lequel il est logé.The shutter piston 31 comprises at least one seal ensuring the seal between said shutter piston and the bore in which it is housed.

En figures 11 et 15 à 19, on a représenté le rotor d'obturateur 27 qui est muni d'un dispositif de déphasage angulaire par rapport au vilebrequin 5 du moteur 12 de sorte que l'ouverture de la ou des soupape(s) 2 puisse être avancée ou retardée.In FIGS. 11 and 15 to 19, there is shown the shutter rotor 27 which is provided with an angular phase shift device with respect to the crankshaft 5 of the engine 12 so that the opening of the valve (s) 2 can be advanced or delayed.

Dans une variante, non représentée, le dispositif de déphasage du rotor d'obturateur 27 est constitué d'au moins une cannelure hélicoïdale aménagée à l'intérieur dudit rotor coopérant avec au moins une cannelure hélicoïdale aménagée à l'extérieur de l'arbre d'entraînement dudit rotor d'obturateur.In a variant, not shown, the phase shifter device of the shutter rotor 27 is constituted by at least one helical groove arranged inside said rotor cooperating with at least one helical groove arranged outside the d-shaft. driving said shutter rotor.

Dans cette variante, le déphasage s'opère par translation du rotor d'obturateur 27 parallèlement à son axe de rotation au moyen d'une fourchette.In this variant, the phase shift is effected by translation of the shutter rotor 27 parallel to its axis of rotation by means of a fork.

Selon cette variante, le rotor d'obturateur 27_comporte des protubérances qui sont de largeur suffisante pour obturer le ou les orifice(s) de sortie de pompe logé(s) dans le carter d'obturateurs 65 quelle que soit leur position longitudinale par rapport à ces derniers.According to this variant, the shutter rotor 27 has protuberances which are of sufficient width to close off the pump outlet orifice (s) housed in the shutter casing 65 regardless of their longitudinal position with respect to FIG. these latter.

Dans notre exemple de réalisation selon les figures 11 et 15 à 19, les protubérances 28 sont prévues larges et de section variable sur la longueur du rotor d'obturateur 27, de sorte qu'elles présentent un temps d'obturation qui varie en fonction de la position longitudinale du rotor d'obturateur 27 par rapport au ou aux orifice(s) de sortie de pompe 29 ce qui permet d'augmenter ou de diminuer la course de levée de la ou des soupape(s) 2.In our exemplary embodiment according to FIGS. 11 and 15 to 19, the protuberances 28 are wide and of variable section over the length of the shutter rotor 27, so that they have a shutter time which varies according to the longitudinal position of the shutter rotor 27 with respect to the pump outlet orifice (s) 29, which makes it possible to increase or decrease the lift stroke of the valve (s) 2.

Le contrôle de la position longitudinale du rotor d'obturateur 27 par rapport au(x) dit(s) orifice(s) de sortie de pompe 29 s'opère au moyen d'une fourchette de levée de soupape 62 qui permet d'imprimer audit rotor d'obturateur 27 une translation parallèlement à son axe de rotationThe control of the longitudinal position of the shutter rotor 27 with respect to the said pump outlet orifice (s) 29 is effected by means of a valve lift fork 62 which makes it possible to print shutter rotor 27 is translated parallel to its axis of rotation

On constate que le rotor d'obturateur 27 comprend au moins une cannelure droite intérieure 34 coopérant avec au moins une cannelure droite extérieure 76 prévue sur un fourreau d'ouverture 37 ou tout autre élément d'entraînement.It is found that the shutter rotor 27 comprises at least one inner right-hand groove 34 cooperating with at least one outer right-hand groove 76 provided on an opening sheath 37 or any other driving element.

Le dispositif de déphasage angulaire du rotor d'obturateur 27 est constitué du fourreau d'ouverture 37 comprenant au moins une cannelure hélicoïdale intérieure 75 coopérant avec au moins une cannelure hélicoïdale extérieure 60 que comporte son arbre d'entraînement 59 ou tout autre moyen d'entraînement.The angular phase shift device of the shutter rotor 27 consists of the opening sheath 37 comprising at least one inner helical groove 75 cooperating with at least one outer helical groove 60 that its drive shaft 59 or any other means of training.

Le fourreau d'ouverture 37 comporte également au moins une cannelure droite extérieure 76 coopérant avec au moins une cannelure droite intérieure 34 prévue sur le rotor d'obturateur 27.The opening sheath 37 also comprises at least one outer right groove 76 cooperating with at least one inner right spline 34 provided on the shutter rotor 27.

Le fourreau d'ouverture 37 peut être manoeuvré en translation parallèlement à son axe de rotation par une fourchette d'avance ouverture de soupape 61 afin d'avancer ou de retarder l'ouverture de la ou des soupape(s) 2 par déphasage angulaire du rotor d'obturateur 27 qu'il entraîne en rotation.The opening sleeve 37 can be operated in translation parallel to its axis of rotation by a valve opening advance fork 61 in order to to advance or to delay the opening of the valve (s) 2 by angular phase shift of the shutter rotor 27 which causes it to rotate.

La levée de la ou des soupape(s) 2 est contrôlée indépendamment au moyen de la fourchette de levée de soupape 62 qui agit sur la position longitudinale du rotor d'obturateur 27 par rapport au ou aux orifice(s) de sortie de pompe 29.The lifting of the valve (s) 2 is controlled independently by means of the valve lift fork 62 which acts on the longitudinal position of the shutter rotor 27 with respect to the pump outlet port (s). .

On constate dans une variante d'exécution, non représentée, que le rotor d'obturateur 27 peut comprendre au moins une cannelure droite intérieure coopérant avec au moins une cannelure droite extérieure prévue sur son arbre d'entraînement ou tout autre élément d'entraînement.It is noted in an alternative embodiment, not shown, that the shutter rotor 27 may comprise at least one inner right groove cooperating with at least one outer right groove provided on its drive shaft or any other drive element.

En figures 14 à 19, on a illustré un exemple de sélecteur d'ouverture de soupapes 11 qui peut être un dispositif mécanique rotatif contenu dans un carter et tournant à une vitesse proportionnelle à celle du vilebrequin 5 du moteur 12.FIGS. 14 to 19 illustrate an example of a valve opening selector 11 which may be a rotary mechanical device contained in a housing and rotating at a speed proportional to that of the crankshaft 5 of the engine 12.

En variante, le sélecteur d'ouverture de soupapes 11 peut être constitué d'une
ou plusieurs électrovanne(s) pilotée(s) par un calculateur.In a variant, the valve opening selector 11 may consist of a
or more solenoid valve (s) driven by a computer.

Selon l'exemple représenté en figures 14 à 19, le sélecteur d'ouverture de soupapes 11 est un dispositif mécanique rotatif contenu dans un carter de sélecteurs 66, tournant à une vitesse proportionnelle à celle du vilebrequin 5 du moteur 12, et comportant un rotor de sélecteur d'ouverture 38 muni d'une came 39 qui actionne un ou plusieurs distributeur(s) d'ouverture de soupape 40 disposé(s) radialement dans le carter de sélecteurs 66.According to the example shown in FIGS. 14 to 19, the valve opening selector 11 is a rotary mechanical device contained in a selector casing 66, rotating at a speed proportional to that of the crankshaft 5 of the engine 12, and comprising a rotor opening selector valve 38 provided with a cam 39 which actuates one or more valve opening distributor (s) 40 arranged radially in the selector housing 66.

Le rotor de sélecteur d'ouverture 38 est muni d'un dispositif de déphasage angulaire d'ouverture par rapport au vilebrequin 5 du moteur 12 de sorte que le sélecteur d'ouverture de soupapes 11 puisse être synchronisé avec l'obturateur de sortie de pompe 8 et puisse sélectionner la ou les soupape(s) 2 au moment recherché.The aperture selector rotor 38 is provided with an angular phase shift device with respect to the crankshaft 5 of the engine 12 so that the valve opening selector 11 can be synchronized with the pump output shutter. 8 and can select the valve (s) 2 at the desired time.

Le rotor de sélecteur d'ouverture 38 comporte une came 39 qui est solidaire du fourreau d'ouverture 37, permettant au sélecteur d'ouverture de soupapes 11 de rester synchronisé avec l'ouverture de la ou des soupape(s) 2 qui dépend du déphasage angulaire du rotor d'obturateur 27 par rapport au vilebrequin 5 du moteur 12.The aperture selector rotor 38 has a cam 39 which is integral with the opening sheath 37, allowing the valve opening selector 11 to remain synchronized with the opening of the valve (s) 2 which depends the angular phase shift of the shutter rotor 27 relative to the crankshaft 5 of the engine 12.

La fourchette d'avance ouverture de soupape 61 permet de déphaser simultanément et dans les mêmes proportions le rotor de sélecteur d'ouverture 38 et le rotor d'obturateur 27 par rapport au vilebrequin 5.The valve opening advance fork 61 makes it possible to phase shift simultaneously and in the same proportions the opening selector rotor 38 and the shutter rotor 27 with respect to the crankshaft 5.

Le dispositif de déphasage angulaire du rotor de sélecteur d'ouverture 38 est constitué d'au moins une cannelure hélicoïdale 77 aménagée à l'intérieur dudit rotor de sélecteur d'ouverture 38 coopérant avec au moins une cannelure hélicoïdale 60 aménagée à l'extérieur de l'arbre d'entraînement 59 dudit rotor de sélecteur d'ouverture 38 ou de tout autre moyen d'entraînement.The angular phase shift device of the aperture selector rotor 38 is constituted by at least one helical groove 77 provided inside said aperture selector rotor 38 cooperating with at least one helical groove 60 arranged outside the aperture selector rotor 38. the drive shaft 59 of said aperture selector rotor 38 or any other drive means.

Le déphasage s'opère au moyen d'une fourchette par translation dudit rotor de sélecteur d'ouverture 38 parallèlement à son axe de rotation.The phase shift is effected by means of a fork by translation of said opening selector rotor 38 parallel to its axis of rotation.

La came 39 est prévue de largeur suffisante pour actionner les distributeurs d'ouverture de soupape 40 quelle que soit sa position longitudinale par rapport aux dits distributeurs.The cam 39 is of sufficient width to actuate the valve opening distributors 40 regardless of its longitudinal position with respect to said distributors.

Le ou les distributeur(s) d'ouverture de soupape 40 sont constitués d'une pièce cylindrique 78_munie d'une ou plusieurs gorge(s) 41 et prenant place dans un alésage aménagé dans le carter de sélecteurs 66.The valve opening distributor (s) 40 consist of a cylindrical piece 78_munie of one or more grooves (s) 41 and taking place in a bore formed in the selector casing 66.

Les gorge(s) 41 sont amenées par translation axiale de la pièce cylindrique 78 imprimée par la came 39 au niveau de conduits 42 aménagés dans le carter de sélecteurs 66 afin de permettre la circulation du fluide hydraulique dans lesdits conduits.The groove (s) 41 are brought by axial translation of the cylindrical piece 78 printed by the cam 39 at the ducts 42 arranged in the selector casing 66 to allow the circulation of the hydraulic fluid in said ducts.

Lorsque la came 39 ne les actionne pas, les pièces cylindriques 78 sont maintenues à la distance recherchée du rotor de sélecteur d'ouverture 38 par l'action conjuguée d'un épaulement 44 aménagé sur lesdites pièces cylindriques 78 et prenant appui sur le carter de sélecteurs 66, et d'un ressort 43 maintenu comprimé par un bouchon 45 vissé dans ledit carter.When the cam 39 does not actuate them, the cylindrical pieces 78 are held at the desired distance from the opening selector rotor 38 by the combined action of a shoulder 44 arranged on said cylindrical pieces 78 and bearing on the housing of selectors 66, and a spring 43 maintained compressed by a plug 45 screwed into said housing.

Le bouchon 45 vissé dans le carter de sélecteurs 66 définit une chambre 46 qui contient le ressort 43 et qui est reliée au circuit basse pression 9 ou au réservoir 58 par un conduit non représenté.The plug 45 screwed into the selector casing 66 defines a chamber 46 which contains the spring 43 and which is connected to the low pressure circuit 9 or the reservoir 58 by a conduit not shown.

En figures 15 à 21, on a montré un exemple de réalisation d'un sélecteur de fermeture de soupapes 25 qui est constitué d'un dispositif mécanique rotatif contenu dans un carter de sélecteur 66 et tournant à une vitesse proportionnelle à celle du vilebrequin 5 du moteur 12.In FIGS. 15 to 21, an embodiment of a valve closing selector 25 has been shown which consists of a rotary mechanical device contained in a selector casing 66 and rotating at a speed proportional to that of the crankshaft 5 of FIG. motor 12.

En variante, le sélecteur de fermeture de soupapes 25 peut être constitué d'une ou plusieurs électrovanne(s) pilotée(s) par un calculateur.Alternatively, the valve closing selector 25 may consist of one or more solenoid valves (s) driven (s) by a computer.

Le sélecteur de fermeture de soupapes 25 comporte un rotor de sélecteur de fermeture 47 muni d'une came 48 qui actionne un ou plusieurs distributeur(s) de fermeture de soupape 49 disposé(s) radialement dans le carter de sélecteurs 66.The valve closing selector 25 comprises a closing selector rotor 47 provided with a cam 48 which actuates one or more valve closing valves 49 arranged radially in the selector housing 66.

Le rotor de sélecteur de fermeture 47 est muni d'un dispositif de déphasage angulaire par rapport au vilebrequin 5 du moteur 12 de sorte que la fermeture de la ou des soupape(s) 2 puisse être avancée ou retardée.The closing selector rotor 47 is provided with an angular phase shifter with respect to the crankshaft 5 of the motor 12 so that the closure of the valve (s) 2 can be advanced or delayed.

Le dispositif de déphasage du rotor de sélecteur de fermeture 47 est constitué d'au moins une cannelure hélicoïdale 79 aménagée à l'intérieur du rotor de sélecteur de fermeture 47 coopérant avec au moins une cannelure hélicoïdale 60 aménagée à l'extérieur de l'arbre d'entraînement 59 ou de tout autre moyen d'entraînement dudit rotor de sélecteur de fermeture 47.The phase shift device of the closing selector rotor 47 consists of at least one helical groove 79 formed inside the closing selector rotor 47 cooperating with at least one helical groove 60 arranged outside the shaft. 59 or any other drive means of said closing selector rotor 47.

Le déphasage s'opère par translation du rotor de sélecteur de fermeture 47 parallèlement à son axe de rotation au moyen d'une fourchette de retard fermeture de soupape 63.The phase shift is effected by translating the closing selector rotor 47 parallel to its axis of rotation by means of a valve closing delay range 63.

La came 48 est de largeur suffisante pour actionner les distributeurs de fermeture de soupape 49 quelle que soit sa position longitudinale par rapport à ces derniers.The cam 48 is of sufficient width to actuate the valve closing valves 49 regardless of its longitudinal position with respect thereto.

Le ou les distributeur(s) de fermeture de soupape 49 sont constitués d'une pièce cylindrique 80 munie d'une ou plusieurs gorge(s) 50 et prenant place dans un alésage aménagé dans le carter de sélecteurs 66.Valve distributor (s) 49 consist of a cylindrical piece 80 provided with one or more grooves 50 and taking place in a bore formed in the selector casing 66.

Les gorge(s) 50 sont amenées par translation axiale de la pièce cylindrique 80 imprimée par la came 38 au niveau de conduits aménagés dans le carter de sélecteurs 66 afin de permettre la circulation du fluide hydraulique dans lesdits conduits.The groove (s) 50 are brought by axial translation of the cylindrical piece 80 printed by the cam 38 at ducts formed in the selector casing 66 to allow the circulation of the hydraulic fluid in said ducts.

Lorsque la came 48 ne les actionne pas, les pièces cylindriques 80 sont maintenues à la distance recherchée du rotor de sélecteur de fermeture 47 par l'action conjuguée d'un épaulement 51 aménagé sur lesdites pièces cylindriques 80 et prenant appui sur le carter de sélecteurs 66, et d'un ressort 52 maintenu comprimé par un bouchon 53 vissé dans ledit carter.When the cam 48 does not actuate them, the cylindrical pieces 80 are held at the desired distance from the closing selector rotor 47 by the combined action of a shoulder 51 provided on said cylindrical pieces 80 and resting on the selector housing 66, and a spring 52 maintained compressed by a plug 53 screwed into said housing.

Le bouchon 53 vissé dans le carter de sélecteurs 66 définit une chambre 73 qui contient le ressort 52 et qui est reliée au circuit basse pression 9 ou au réservoir 58 par un conduit non représenté.The plug 53 screwed into the selector casing 66 defines a chamber 73 which contains the spring 52 and which is connected to the low pressure circuit 9 or the reservoir 58 by a conduit not shown.

Le circuit haute pression 10 comporte au moins un clapet anti-retour de fermeture 54 en amont ou en aval du sélecteur de fermeture de soupape 25 afin d'empêcher que le fluide hydraulique contenu dans le vérin hydraulique 3 d'une ou plusieurs soupape(s) 2 en phase de fermeture ne puisse être introduit dans le vérin hydraulique 3 d'une autre ou d'autres soupape(s) 2 devant rester fermée(s).The high pressure circuit 10 comprises at least one closure check valve 54 upstream or downstream of the valve closing selector 25 to prevent the hydraulic fluid contained in the hydraulic cylinder 3 from one or more valves (s). ) 2 in the closing phase can not be introduced into the hydraulic cylinder 3 of another or other valve (s) 2 to remain closed (s).

Le clapet anti-retour de fermeture 54, positionné en amont ou en aval du sélecteur de fermeture de soupape 25, est constitué d'une bille maintenue sur son siège par un ressort.The closing check valve 54, positioned upstream or downstream of the valve closing selector 25, consists of a ball held on its seat by a spring.

On note également que le clapet anti-retour d'entrée de pompe 26 est constitué d'une bille maintenue sur son siège par un ressort.It is also noted that the pump inlet check valve 26 consists of a ball held on its seat by a spring.

En figures 20 et 21, on a illustré un carter commun constitué d'une ou plusieurs pièces dans lequel sont contenus ensemble ou par groupe les composants que sont la pompe hydraulique volumétrique 4, l'obturateur de sortie de pompe 8, le sélecteur d'ouverture de soupapes 11, le ou les clapet(s) anti-retour d'ouverture 24, le sélecteur de fermeture de soupapes 25 et le ou les clapet(s) anti-retour de fermeture 54.In FIGS. 20 and 21, there is illustrated a common casing consisting of one or more pieces in which are contained together or in groups the components that are the volumetric hydraulic pump 4, the pump outlet shutter 8, the selector of FIG. valve opening 11, the non-return valve (s) opening 24, the valve closing selector 25 and the closing non-return valve (s) 54.

La pompe hydraulique volumétrique 4, le rotor d'obturateur 27, le rotor de sélecteur 38, et le rotor de sélecteur de fermeture 47, ou une combinaison quelconque de ces quatre dispositifs sont entraînés en rotation par un arbre commun 59 lui-même entraîné en rotation par le vilebrequin 5 du moteur 12 au moyen d'un dispositif de transmission (figures 15 à 19).The volumetric hydraulic pump 4, the shutter rotor 27, the selector rotor 38, and the closing selector rotor 47, or any combination of these four devices are rotated by a common shaft 59 itself driven by rotation by the crankshaft 5 of the engine 12 by means of a transmission device (FIGS. 15 to 19).

Le dispositif de transmission entraînant l'arbre commun 59 est constitué d'une poulie 74 entraînée en rotation par le vilebrequin 5 du moteur 12 au moyen d'une courroie crantée ou d'une chaîne, ou d'un système d'engrenages constitué d'au moins un pignon.The transmission device driving the common shaft 59 consists of a pulley 74 driven in rotation by the crankshaft 5 of the engine 12 by means of a toothed belt or chain, or a gear system consisting of at least one pinion.

L'arbre commun 59 est muni d'au moins une cannelure hélicoïdale 60 qui entraîne en rotation le rotor d'obturateur 27, le rotor de sélecteur d'ouverture 38, le fourreau d'ouverture 37 et le rotor de sélecteur de fermeture 47 ou une combinaison quelconque de ces trois dispositifs et coopère avec les cannelures hélicoïdales intérieures de certains de ces dispositifs pour en permettre le déphasage angulaire par rapport au vilebrequin 5 du moteur 12.The common shaft 59 is provided with at least one helical groove 60 which rotates the shutter rotor 27, the aperture selector rotor 38, the aperture sheath 37 and the closing selector rotor 47 or any combination of these three devices and cooperates with the internal helical grooves of some of these devices to allow the angular phase shift relative to the crankshaft 5 of the engine 12.

Le carter commun est constitué de quatre carters principaux qui contiennent l'arbre commun 59 et qui sont assemblés bout à bout avec respectivement :

  • Figure imgb0013
    un carter de pompe 64 comprenant la pompe hydraulique volumétrique 4 et le ou les clapet(s) anti-retour d'entrée de pompe 26,
  • Figure imgb0012
    un carter d'obturateurs 65 contenant le rotor d'obturateur 27 et le ou les orifice(s) de sortie de pompe 29,
  • Figure imgb0007
    un carter de sélecteurs 66 contenant la fourchette de levée de soupape 62, le rotor de sélecteur d'ouverture 38, le ou les distributeur(s) d'ouverture de soupape 40, la fourchette d'avance ouverture de soupape 61, le rotor de sélecteur de fermeture 47, le ou les distributeur(s) de fermeture de soupape 49, la fourchette de retard fermeture de soupape 63, le ou les clapet(s) anti-retour d'ouverture 24, et pouvant comporter le ou les clapet(s) anti-retour de fermeture 54,
  • Figure imgb0012
    et un carter de collecteur de fermeture 67.
The common housing consists of four main housings which contain the common shaft 59 and which are assembled end to end with respectively:
  • Figure imgb0013
    a pump casing 64 comprising the volumetric hydraulic pump 4 and the pump inlet check valve (s) 26,
  • Figure imgb0012
    a shutter housing 65 containing the shutter rotor 27 and the pump outlet port (s) 29,
  • Figure imgb0007
    a selector housing 66 containing the valve lift fork 62, the opening selector rotor 38, the valve opening distributor (s) 40, the valve opening advance fork 61, the rotor closing selector 47, the valve closing distributor (s) 49, the valve closing delay range 63, the opening non-return valve (s) 24, and possibly including the valve (s) ( s) closing anti-return 54,
  • Figure imgb0012
    and a closing collector housing 67.

Le carter d'obturateurs 65 est traversé de conduits reliant la ou les sortie(s) 6 de la pompe hydraulique volumétrique 4 avec le ou les obturateur(s) de sortie de pompe 8 d'une part et avec un collecteur d'ouverture 68 constitué d'un réseau de conduits aménagé au plan de joint entre le carter d'obturateurs 65 et le carter de sélecteurs 66 d'autre part.The shutter housing 65 is traversed by ducts connecting the outlet (s) 6 of the hydraulic displacement pump 4 with the pump outlet shutter (s) 8 on the one hand and with an opening manifold 68 consisting of a ductwork arranged at the joint plane between the shutter housing 65 and the selector casing 66 on the other hand.

Le carter d'obturateurs 65 est traversé de conduits reliant la ou les entrée(s) 7 de la pompe hydraulique volumétrique 4 avec un collecteur de fermeture 69 constitué d'un réseau de conduits aménagé au plan de joint entre le carter de sélecteurs 66 et le carter de collecteur de fermeture 67.The shutter housing 65 is traversed by ducts connecting the inlet (s) 7 of the displacement hydraulic pump 4 with a closure manifold 69 consisting of a ductwork arranged at the joint plane between the selector housing 66 and the closing collector housing 67.

Le carter de sélecteurs 66 est traversé longitudinalement par des conduits 42 qui relient le collecteur d'ouverture 68 et le collecteur de fermeture 69 et qui peuvent être obturés ou ouverts par le ou les distributeur(s) d'ouverture de soupape 40 et par le ou les distributeur(s) de fermeture de soupape 49.The selector casing 66 is traversed longitudinally by conduits 42 which connect the opening manifold 68 and the closure manifold 69 and which can be closed or opened by the valve opening distributor (s) 40 and by the or the valve closing distributor (s) 49.

Les conduits 42 comportent des conduits de départ de soupape 70 situés entre le ou les distributeur(s) d'ouverture de soupape 40 et le ou les distributeur(s) de fermeture de soupape 49 qui sont connectés au vérin hydraulique 3 de la ou des soupapes 2.The conduits 42 comprise valve starting conduits 70 located between the valve opening distributor (s) 40 and the valve closing distributor (s) 49 which are connected to the hydraulic cylinder 3 of the valves 2.

Le carter de sélecteurs 66 est également traversé longitudinalement par un ou plusieurs conduits qui relient le collecteur de fermeture 69 avec la ou les entrée(s) 7 de la pompe hydraulique volumétrique 4.The selector casing 66 is also traversed longitudinally by one or more ducts which connect the closure manifold 69 with the inlet (s) 7 of the volumetric hydraulic pump 4.

Le collecteur d'ouverture 68 permet de relier entre eux les conduits traversant longitudinalement le carter de sélecteurs 66 devant être reliés à une même sortie de pompe 6.The opening manifold 68 makes it possible to connect together the ducts passing longitudinally through the selector casing 66 to be connected to the same pump outlet 6.

La sortie de pompe 6 est connectée au collecteur d'ouverture 68 par un conduit qui traverse le carter d'obturateurs 65.The pump outlet 6 is connected to the opening manifold 68 by a duct which passes through the shutter housing 65.

Le collecteur de fermeture 69 permet de relier entre eux les conduits traversant longitudinalement le carter de sélecteurs 66 devant être reliés à une même entrée de pompe 7.The closure manifold 69 makes it possible to connect together the ducts passing longitudinally through the selector casing 66 to be connected to the same pump inlet 7.

L'entrée de pompe 7 est connectée au collecteur de fermeture 69 par les conduits qui traversent respectivement le carter de sélecteurs 66 et le carter d'obturateurs 65.The pump inlet 7 is connected to the closure manifold 69 through the ducts which pass respectively through the selector casing 66 and the shutter casing 65.

Des vis d'assemblage 71 traversent de part en part les différents carters 64, 65, 66 et 67 afin de les maintenir assemblés, l'une ou plusieurs des dites vis d'assemblage 71 pouvant servir de glissière aux fourchettes 61, 62 et 63 qui permettent de commander l'ouverture, la levée et la fermeture des soupapes 2.Assembly screws 71 pass right through the various housings 64, 65, 66 and 67 in order to hold them together, one or more of said assembly screws 71 being able to serve as a slide for the forks 61, 62 and 63 which make it possible to control opening, lifting and closing of the valves 2.

La fourchette d'avance ouverture de soupape 61, la fourchette de levée de soupape 62 et la fourchette de retard fermeture de soupape 63 sont manoeuvrées en translation par des moteurs électriques pilotés par un calculateur qui sont reliés aux dites fourchettes 61, 62 et 63 par des moyens de transmission.The valve opening advance range 61, the valve lift range 62 and the valve closure delay range 63 are manipulated in translation by computer driven electric motors which are connected to said forks 61, 62 and 63 by transmission means.

Le ou les orifice(s) de sortie de pompe 29 que viennent obturer les protubérances 28 du rotor d'obturateur 27 débouchent à l'intérieur du carter commun qui comprend notamment l'arbre commun 59, ledit carter commun constituant une chambre fermée raccordée :

  • Figure imgb0012
    au carter d'huile de graissage du moteur 72 au moyen d'un conduit,
  • Figure imgb0005
    ou au circuit de graissage sous pression 15 du moteur 12,
  • Figure imgb0005
    ou à un carter de fluide hydraulique indépendant du carter d'huile de graissage du moteur 72,
  • Figure imgb0005
    ou maintenu sous pression par la pompe additionnelle 13.
The pump outlet port (s) 29 closed by the protuberances 28 of the shutter rotor 27 open into the housing which includes in particular the common shaft 59, said housing forming a connected closed chamber:
  • Figure imgb0012
    to the engine lubricating oil sump 72 by means of a conduit,
  • Figure imgb0005
    or the pressure lubrication circuit 15 of the engine 12,
  • Figure imgb0005
    or a hydraulic fluid sump independent of the engine oil sump 72,
  • Figure imgb0005
    or maintained under pressure by the additional pump 13.

On note que selon un mode particulier de réalisation un même conduit raccordé au circuit hydraulique haute pression 10 peut alimenter simultanément plusieurs vérins hydrauliques 3 au travers d'un diviseur de débit qui assure une levée sensiblement identique aux soupapes 2 actionnées par lesdits vérins hydrauliques 3.Note that according to a particular embodiment a same duct connected to the high pressure hydraulic circuit 10 can simultaneously supply several hydraulic cylinders 3 through a flow divider which ensures a substantially identical lift to the valves 2 actuated by said hydraulic cylinders 3.

On comprend de la description qui précède le fonctionnement du dispositif selon la présente invention.It is understood from the description which precedes the operation of the device according to the present invention.

La figure 1, illustre le schéma de principe du dispositif selon une configuration à quatre soupapes (par exemple pour actionner les quatre soupapes d'admission ou d'échappement d'un moteur à quatre cylindres).Figure 1 illustrates the block diagram of the device in a four-valve configuration (e.g., to operate the four intake or exhaust valves of a four-cylinder engine).

On y voit que lorsque aucune soupape ne doit être ouverte par l'un ou l'autre des vérins hydrauliques 3, la pompe hydraulique volumétrique 4 débite du fluide hydraulique en provenance du circuit basse pression 9 - ici le circuit de graissage du moteur - via le clapet anti-retour d'entrée de pompe 26 et vers le carter de lubrifiant du moteur 58 via l'obturateur de sortie de pompe 8 alors ouvert.It can be seen that when no valve is to be opened by one or the other of the hydraulic cylinders 3, the hydraulic displacement pump 4 delivers hydraulic fluid from the low pressure circuit 9 - in this case the engine lubrication circuit - via the pump inlet check valve 26 and to the lubricant housing of the motor 58 via the pump outlet shutter 8 then open.

Lorsqu'une soupape doit être ouverte, le sélecteur d'ouverture de soupapes 11 met le vérin hydraulique 3 de ladite soupape en relation avec le circuit haute pression 10 en provenance de la sortie de la pompe hydraulique volumétrique 4.When a valve must be opened, the valve opening selector 11 places the hydraulic cylinder 3 of said valve in relation with the high pressure circuit 10 coming from the output of the positive displacement hydraulic pump 4.

L'obturateur de sortie de pompe 8 ferme alors le conduit de sortie de pompe 32 ce qui élève la pression dans le circuit haute pression 10 de sorte que le vérin hydraulique 3 ouvre la soupape sélectionnée.The pump outlet shutter 8 then closes the pump outlet conduit 32 which raises the pressure in the high pressure circuit 10 so that the hydraulic cylinder 3 opens the selected valve.

Lorsque la soupape est suffisamment levée, l'obturateur de sortie de pompe 8 réouvre le conduit de sortie de pompe 32 ce qui stoppe la levée de la soupape car la pression du circuit haute pression 10 en amont du clapet anti-retour d'ouverture 24 devient inférieure à celle régnant dans la chambre du vérin hydraulique 3 du fait de l'action du ressort de rappel de la soupape.When the valve is sufficiently raised, the pump outlet shutter 8 reopens the pump outlet pipe 32 which stops the lifting of the valve because the pressure of the high pressure circuit 10 upstream of the opening non-return valve 24 becomes lower than that prevailing in the chamber of the hydraulic cylinder 3 due to the action of the return spring of the valve.

Grâce à l'action du clapet anti-retour d'ouverture 24, ladite soupape reste ouverte.Thanks to the action of the opening non-return valve 24, said valve remains open.

La fermeture de la soupape est commandée par le sélecteur de fermeture de soupapes 25 qui, au moment choisi, met le vérin hydraulique 3 de ladite soupape en relation avec l'entrée de la pompe hydraulique volumétrique 4 via le circuit haute pression 10.The closing of the valve is controlled by the valve closing selector 25 which, at the chosen moment, puts the hydraulic cylinder 3 of said valve in relation with the inlet of the positive displacement hydraulic pump 4 via the high pressure circuit 10.

La rapide montée en pression dudit circuit haute pression 10 ayant pour conséquence de fermer l'arrivée du fluide hydraulique en provenance du circuit de graissage du moteur par l'action du clapet anti-retour d'entrée de pompe 26 et de forcer le fluide hydraulique à l'entrée de ladite pompe hydraulique volumétrique 4 ce qui permet de récupérer en majeure partie le travail mécanique absorbé par la compression du ressort de la soupape, et de maîtriser la vitesse de fermeture de ladite soupape.The rapid rise in pressure of said high pressure circuit 10 having the consequence of closing the arrival of the hydraulic fluid from the engine lubricating circuit by the action of the pump inlet check valve 26 and forcing the hydraulic fluid at the inlet of said volumetric hydraulic pump 4 which allows to recover most of the work mechanical absorbed by the compression of the spring of the valve, and to control the closing speed of said valve.

Lorsque la soupape est reposée sur son siège, la pompe hydraulique volumétrique 4 débite à nouveau du fluide hydraulique en provenance du circuit basse pression 9 vers le carter de lubrifiant du moteur 58 via le clapet anti-retour d'entrée de pompe 26.When the valve is rested on its seat, the positive displacement hydraulic pump 4 again delivers hydraulic fluid from the low pressure circuit 9 to the lubricant housing of the engine 58 via the pump inlet check valve 26.

On peut remarquer que l'ouverture et la fermeture simultanée de deux soupapes différentes sont possible, auquel cas, l'entrée de la pompe hydraulique volumétrique 4 est alimentée par le vérin hydraulique 3 d'une soupape en manoeuvre de fermeture, tandis que le fluide hydraulique sortant de ladite pompe hydraulique volumétrique 4 est forcé par l'obturateur de sortie de pompe 8 à alimenter le vérin hydraulique 3 d'une autre soupape en manoeuvre d'ouverture.It may be noted that the simultaneous opening and closing of two different valves is possible, in which case the inlet of the positive displacement hydraulic pump 4 is supplied by the hydraulic cylinder 3 of a valve during closing operation, while the fluid hydraulic output of said positive displacement hydraulic pump 4 is forced by the pump outlet shutter 8 to supply the hydraulic cylinder 3 of another valve in opening operation.

La figure 2 est une représentation schématique d'un circuit dont le fonctionnement est identique au précédent, mais qui est destiné à actionner les 8 soupapes d'admission ou d'échappement_d'un moteur quatre cylindres à deux soupapes d'admission ou d'échappement par cylindre.FIG. 2 is a schematic representation of a circuit whose operation is identical to the preceding one, but which is intended to actuate the 8 intake or exhaust valves of a four-cylinder engine with two intake or exhaust valves per cylinder.

Selon cette configuration, une pompe à ailettes à un seul rotor mais dotée d'une came intérieure définissant deux entrées et deux sorties isolées peut être utilisée comme illustré figure 8.According to this configuration, a rotor pump with a single rotor but with an inner cam defining two insulated inputs and two outputs can be used as illustrated in FIG.

L'obturateur de sortie de pompe 8, le sélecteur d'ouverture de soupapes 11 et le sélecteur de fermeture de soupapes 25 peuvent être réalisés au moyen d'électrovannes, mais la fragilité, le manque de robustesse et le manque de régularité de fonctionnement desdites électrovannes dans le contexte d'un moteur thermique rendent difficile de telles réalisations.The pump outlet shutter 8, the valve opening selector 11 and the valve closing selector 25 can be made by means of solenoid valves, but the fragility, the lack of robustness and the lack of regularity of operation of said valves solenoid valves in the context of a heat engine make such achievements difficult.

Pour cette raison, lesdites électrovannes sont avantageusement remplacées par le dispositif mécanique montré sur les figures 15 à 21 qui apporte la fiabilité et la constance de fonctionnement recherchée dans la motorisation automobile. Le dispositif représenté sur ces figures est particulièrement destiné à actionner les huit soupapes d'admission ou d'échappement d'un moteur quatre cylindres à deux soupapes d'admission ou deux soupapes d'échappement par cylindre.For this reason, said solenoid valves are advantageously replaced by the mechanical device shown in Figures 15 to 21 which provides the reliability and consistency of operation sought in the automotive engine. The device shown in these figures is particularly intended to actuate the eight intake or exhaust valves of a four-cylinder engine with two intake valves or two exhaust valves per cylinder.

Les variantes d'un tel dispositif pour d'autres configurations de moteur apparaîtront aisément à l'homme de l'art.Variants of such a device for other engine configurations will be readily apparent to those skilled in the art.

L'arbre commun 59 est entraîné en rotation par le moteur 12 au moyen de la poulie 74 tournant à la même vitesse qu'un arbre à cames conventionnel, soit à la moitié de la vitesse du vilebrequin 5 du moteur 12, ici, dans le sens des aiguilles d'une montre lorsque l'appareil est vu coté poulie 74.The common shaft 59 is rotated by the motor 12 by means of the pulley 74 rotating at the same speed as a conventional camshaft, or at half the speed of the crankshaft 5 of the engine 12, here in the clockwise when the device is seen on the pulley side 74.

De ce fait, et selon un mode particulier de réalisation, l'ensemble du dispositif peut être placé en lieu et place de l'arbre à cames qu'il remplace (par exemple, l'arbre à cames d'admission) et peut être entraîné, comme montré sur la figure 9, par la courroie de distribution du moteur avec un autre arbre à cames (par exemple, l'arbre à cames d'échappement), ou encore être entraîné par ladite courroie comme montré sur la figure 10 avec un autre dispositif identique.Therefore, and according to a particular embodiment, the entire device can be placed in place of the camshaft it replaces (for example, the intake camshaft) and can be driven, as shown in Figure 9, by the timing belt of the engine with another camshaft (eg, the exhaust camshaft), or further driven by said belt as shown in Figure 10 with another identical device.

La pompe hydraulique volumétrique 4 est de type à ailettes avec une came intérieure définissant deux entrées de pompe 7 et deux sorties de pompe 6 non communicantes entre elles, les clapets anti-retour d'entrée de pompe 26 sont connectés au circuit basse pression 9 en l'occurrence, le circuit de graissage sous pression du moteur 12, et sont constitués de billes maintenues en appui sur leur siège par un ressort.The volumetric hydraulic pump 4 is of the finned type with an inner cam defining two pump inlets 7 and two pump outputs 6 that are not communicating with each other, the pump inlet check valves 26 are connected to the low pressure circuit 9 In this case, the pressure lubrication circuit of the motor 12, and consist of balls held in abutment on their seat by a spring.

Lorsque aucune soupape ne doit être ouverte, la pompe hydraulique volumétrique 4 expulse le fluide hydraulique via le conduit de sortie de pompe 32 dans la cavité interne du carter d'obturateurs 65, ladite cavité étant reliée par un conduit non représenté au carter d'huile de graissage du moteur 72.When no valve is to be opened, the displacement hydraulic pump 4 expels the hydraulic fluid via the pump outlet conduit 32 into the internal cavity of the shutter housing 65, said cavity being connected by a conduit not shown to the oil sump engine lubrication 72.

Comme on peut le voir sur les figures, l'arbre commun 59 est muni de cannelures hélicoïdales 60, ces cannelures entraînant en rotation le rotor d'obturateur 27, le rotor de sélecteur d'ouverture 38 et le rotor de sélecteur de fermeture 47.As can be seen in the figures, the common shaft 59 is provided with helical splines 60, these splines rotating the shutter rotor 27, the opening selector rotor 38 and the closing selector rotor 47.

Ici, le rotor d'obturateur 27 et le rotor de sélecteur d'ouverture 38 restent phasés l'un par rapport à l'autre car ils sont solidaires en rotation du même fourreau 37 ce qui garantit une durée constante entre la sélection d'une soupape 2 et le début d'obturation de la sortie de pompe 6.Here, the shutter rotor 27 and the opening selector rotor 38 remain phased relative to each other because they are integral in rotation with the same sleeve 37, which guarantees a constant duration between the selection of a valve 2 and the start of shutting off the pump outlet 6.

On peut constater que le fonctionnement des obturateurs de pompe 8, du sélecteur d'ouverture de soupapes 11, et du sélecteur de fermeture de soupapes 25 est forcément synchronisé du fait qu'ils sont tous entraînés par l'arbre commun 59.It can be seen that the operation of the pump shutters 8, the valve opening selector 11, and the valve closing selector 25 is necessarily synchronized because they are all driven by the common shaft 59.

Les obturateurs de sortie de pompe 8 sont ici au nombre de deux placés de façon diamétralement opposée dans le carter, et obturent chacun l'une des deux sorties de pompe 6 de la pompe hydraulique volumétrique 4, chaque sortie de pompe 8 étant affectée exclusivement à l'ouverture soit des soupapes 2 paires soit des soupapes 2 impaires des cylindres du moteur 12.The pump outlet shutters 8 are here two in number arranged diametrically opposite in the housing, and each one close one of the two pump outputs 6 of the hydraulic displacement pump 4, each pump outlet 8 being assigned exclusively to the opening is 2-pair valves or odd-order valves 2 of the engine cylinders 12.

Les soupapes 2 paires et impaires d'un même cylindre ayant la même cinématique au même instant sont donc couplées dans leur fonctionnement.The 2 odd and even valves of the same cylinder having the same kinematics at the same time are therefore coupled in their operation.

De la même façon, les deux entrées de pompe 7 sont affectées exclusivement à la fermeture soit des soupapes 2 paires soit des soupapes 2 impaires des cylindres du moteur 12.In the same way, the two pump inputs 7 are assigned exclusively to the closing of either the 2-pair valves or the odd-order 2 valves of the cylinders of the engine 12.

Le rotor d'obturateur 27 comprend quatre protubérances 28 de profil variable placées tous les quatre-vingt-dix degrés.The shutter rotor 27 comprises four protuberances 28 of variable profile placed every ninety degrees.

Puisque les orifices de sortie de pompe 29 sont installés de manière fixe dans le carter d'obturateurs 65, une translation du rotor d'obturateur 27 sur le fourreau d'ouverture 37 modifie la longueur active des protubérances 28 faisant face aux orifices de sortie de pompe 29 et de ce fait permet d'augmenter ou de diminuer le nombre de degrés de vilebrequin 5 durant lesquels va s'opérer l'ouverture des soupapes 2.Since the pump outlets 29 are fixedly installed in the shutter housing 65, a translation of the shutter rotor 27 on the aperture sheath 37 changes the active length of the protuberances 28 facing the exit apertures. pump 29 and thereby increases or decreases the number of degrees of crankshaft 5 during which will occur the opening of the valves 2.

Comme les soupapes 2 s'ouvrent à vitesse constante à un régime du moteur 12 donné, plus elles seront actionnées longtemps en ouverture, plus leur hauteur de levée sera importante.As the valves 2 open at a constant speed at a given engine speed 12, the longer they are operated for a long time in opening, the higher their lifting height will be important.

Pour cette raison, la fourchette de levée de soupape 62 permet de contrôler la hauteur de levée des soupapes 2, ladite fourchette étant manoeuvrée par un moteur électrique non représenté piloté par un calculateur non représenté.For this reason, the valve lift range 62 makes it possible to control the lift height of the valves 2, said fork being operated by an electric motor (not shown) controlled by a computer (not shown).

Le point de début d'ouverture des soupapes 2 peut être contrôlé indépendamment de la levée des soupapes 2 en déplaçant en translation longitudinale le fourreau d'ouverture 37 par rapport à l'arbre commun 59 au moyen de la fourchette d'avance ouverture de soupape 61.The starting point of opening of the valves 2 can be controlled independently of the lifting of the valves 2 by moving in longitudinal translation the opening sheath 37 with respect to the common shaft 59 by means of the advance fork opening of the valve 61.

Cette action permet de déphaser angulairement le rotor d'obturateur 27 par rapport au vilebrequin 5 du moteur 12, les cannelures hélicoïdales intérieures 75 du fourreau d'ouverture 37 coopérant avec les cannelures hélicoïdales 60 extérieures le l'arbre commun 59 ceci ayant pour conséquence que les protubérances 28 du rotor d'obturateur 27 obturent plus ou moins tôt les orifices de sortie de pompe 29 sans modifier leur longueur active qui reste sous le contrôle de la fourchette de levée de soupape 62.This action makes it possible to angularly phase out the shutter rotor 27 with respect to the crankshaft 5 of the engine 12, the inner helical splines 75 of the opening sheath 37 cooperating with the external helical splines 60 the common shaft 59 with the consequence that the protrusions 28 of the shutter rotor 27 more or less close the pump outlet ports 29 without modifying their active length which remains under the control of the valve lift fork 62.

La fourchette d'avance ouverture de soupape 61 est manoeuvrée par un moteur électrique non représenté piloté par un calculateur non représenté.The valve opening advance fork 61 is operated by an electric motor not shown controlled by a computer not shown.

Le sélecteur d'ouverture de soupapes 11 et le sélecteur de fermeture de soupapes 25 relèvent tous les deux du même principe de fonctionnement.The valve opening selector 11 and the valve closing selector 25 both fall within the same operating principle.

On notera que la came 39 du sélecteur d'ouverture actionne en ouverture un distributeur d'ouverture de soupape 40 tous les quatre-vingt-dix degrés de rotation de l'arbre commun 59, soit tous les cent-quatre-vingt degrés de rotation du vilebrequin 5, conformément aux nécessités d'un moteur à quatre cylindres fonctionnant selon le cycle quatre temps d'Otto ou Beau de Rochas.It should be noted that the cam 39 of the opening selector actuates opening a valve opening distributor 40 every ninety degrees of rotation of the common shaft 59, ie every one hundred and eighty degrees of rotation. crankshaft 5, in accordance with the requirements of a four-cylinder engine operating on the four-stroke cycle Otto or Beau de Rochas.

Chaque distributeur d'ouverture de soupape 40 permet d'ouvrir ou de fermer simultanément les conduits 42 d'amenée du fluide hydraulique aux vérins hydrauliques 3 d'une soupape 2 paire et d'une soupape 2 impaire d'un même cylindre.Each valve opening distributor 40 simultaneously opens or closes the conduits 42 for supplying the hydraulic fluid to the hydraulic cylinders 3 of a pair of valves 2 and an odd valve 2 of the same cylinder.

Ce résultat est obtenu grâce aux gorges 41 aménagées sur la pièce cylindrique 78 du distributeur d'ouverture de soupape 40 qui sont soit en regard desdits conduits 42 lorsque la came 39 actionne le distributeur d'ouverture de soupape 40, soit obturent les dits conduits 42 lorsque la came 39 ne les actionne pas.This result is obtained thanks to the grooves 41 arranged on the cylindrical part 78 of the valve opening distributor 40 which are either facing said ducts 42 when the cam 39 actuates the valve opening distributor 40, or block said ducts 42 when the cam 39 does not operate them.

La pièce cylindrique 78 est ramenée à la distance recherchée par rapport à la came 39 par son épaulement 44 maintenu au contact du carter de sélecteurs 66 par le ressort 43.The cylindrical piece 78 is brought back to the desired distance with respect to the cam 39 by its shoulder 44 kept in contact with the selector casing 66 by the spring 43.

Le point de début de fermeture des soupapes 2 est contrôlé en déplaçant en translation longitudinale le rotor de sélecteur de fermeture 47 par rapport à l'arbre commun 59 au moyen de la fourchette de retard de fermeture de soupape 63.The starting point of closure of the valves 2 is controlled by moving in longitudinal translation the closing selector rotor 47 with respect to the common shaft 59 by means of the valve closing delay range 63.

Cette action permet de déphaser angulairement le rotor de sélecteur de fermeture 47 par rapport au vilebrequin 5 du moteur 12, les cannelures hélicoïdales intérieures 79 dudit rotor de sélecteur de fermeture 47 coopérant avec les cannelures hélicoïdales 60 extérieures de l'arbre commun 59, ceci ayant pour conséquence que les distributeurs de fermeture de soupapes 49 sont actionnés plus ou moins tôt afin de fermer les soupapes 2 plus ou moins tôt.This action makes it possible to angularly phase out the closing selector rotor 47 relative to the crankshaft 5 of the engine 12, the inner helical splines 79 of said closing selector rotor 47 cooperating with the external helical splines 60 of the common shaft 59, this having As a consequence, the valve closing valves 49 are actuated more or less early in order to close the valves 2 more or less early.

On note que le carter commun peut comprendre un socle dans lequel est logé au moins un vérin hydraulique 3, ledit socle étant fixé sur la culasse du moteur 12 afin que chaque vérin hydraulique 3 soit en contact avec l'extrémité supérieure de la queue de la soupape 2 correspondante dudit moteur 12 et puisse actionner ladite soupape.Note that the common housing may comprise a base in which is housed at least one hydraulic cylinder 3, said base being fixed on the cylinder head of the engine 12 so that each hydraulic cylinder 3 is in contact with the upper end of the tail of the corresponding valve 2 of said motor 12 and can actuate said valve.

Il doit d'ailleurs être entendu que la description qui précède n'a été donnée qu'à titre d'exemple et quelle ne limite nullement le domaine de l'invention dont on ne sortirait pas en remplaçant les détails d'exécution décrits par tout autre équivalent.It must also be understood that the foregoing description has been given only by way of example and which in no way limits the scope of the invention which would not be overcome by replacing the details of execution described by any other equivalent.

Claims (57)

  1. Hydraulic valve actuator for reciprocating engines, comprising:
    Figure imgb0036
    at least one hydraulic jack (3) connected to a high-pressure hydraulic circuit (10) by means of a duct and ensuring the opening of at least one valve (2),
    Figure imgb0036
    at least one hydraulic positive displacement pump (4) comprising at least one outlet and at least one inlet, and rotating at a speed proportional to that of the engine crankshaft,
    Figure imgb0036
    at least one pump outlet plug (8) which makes it possible to prevent the hydraulic fluid expelled at the outlet of the hydraulic positive displacement pump (4) from issuing into a low-pressure circuit (9) or into a reservoir (58) and to force it into a high-pressure circuit (10) communicating with one or more hydraulic jacks (3) ensuring the opening of one or more valves (2),
    Figure imgb0036
    at least one valve opening selector (11) which makes it possible to direct, via the high-pressure circuit (10), the hydraulic fluid expelled at the outlet of the hydraulic positive displacement pump (4) towards the hydraulic jack (3) of at least one valve (2) to be opened, while at the same time preventing said hydraulic fluid from being directed towards one or more other valves (2) to remain closed,
    Figure imgb0036
    at least one opening nonreturn valve (24) which is located on the high-pressure circuit (10) between the outlet or outlets of the hydraulic positive displacement pump (4) and the hydraulic jack (3) of at least one valve (2) and which makes it possible to retain the hydraulic fluid in said hydraulic jack (3) of said valve (2) in order to keep it open,
    Figure imgb0036
    at least one valve closing selector (25) which makes it possible to direct the hydraulic fluid contained in the hydraulic jack (3) of at least one valve (2) kept open by the opening nonreturn valve (24) towards the inlet or inlets of the hydraulic positive displacement pump (4), in order to ensure the closing of said valve or valves (2) and to prevent the hydraulic fluid contained in their hydraulic jack (3) from being introduced into the hydraulic jack (3) of another valve or other valves (2) which is or are to remain in a closed position,
    Figure imgb0036
    characterized in that at least one pump inlet nonreturn valve (26) which is located at the inlet or inlets of the hydraulic positive displacement pump (4) and which makes it possible for the hydraulic fluid of the low-pressure circuit (9) or of the reservoir (58) to be admitted at the inlet or inlets of the hydraulic positive displacement pump (4) when the pressure of said low-pressure circuit (9) or of said reservoir (58) is higher than that of said inlet or inlets of the hydraulic positive displacement pump (4).
  2. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the cylinder and the chamber (20) of the hydraulic jack (3) ensuring the opening of the valve or valves (2) are arranged in a valve guide (16), said cylinder and said chamber (20) cooperating with a jack piston consisting of a shoulder (19) arranged on the valve stem (18) in order to open the valve (2).
  3. Hydraulic valve actuator for reciprocating engines according to Claim 2, characterized in that the jack piston consisting of a shoulder (19) arranged on the valve stem (18) participates in guiding the valve (2) in the valve guide (16).
  4. Hydraulic valve actuator for reciprocating engines according to Claim 2, characterized in that the jack piston consisting of a shoulder (19) on the valve stem (18) comprises at least one seal (17).
  5. Hydraulic valve actuator for reciprocating engines according to Claim 2, characterized in that the valve guide (16) comprises at least one drain (22) in the vicinity of the intake or exhaust duct (21), which the cylinder head of the engine (12) comprises in order to limit the passage of the hydraulic fluid towards said intake or exhaust duct (21).
  6. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the hydraulic jack (3) ensuring the opening of the valve or valves (2) comprises a limit-stop damping device making it possible to brake the valve or valves (2) before said valves come into contact with their seat.
  7. Hydraulic valve actuator for reciprocating engines according to Claim 6, characterized in that the hydraulic jack (3) arranged in the valve guide (16) comprises a limit-stop damping device consisting of a small shoulder (23) which is arranged on the valve stem (18) and which cooperates with cylinder portion of small height and of a diameter substantially larger than said small shoulder (23), said cylinder portion being arranged in the upper part of the valve guide (16) in order to shear the hydraulic fluid when the valve (2) reaches the end of the closing stroke, the effect of which is to reduce the speed of said valve (2).
  8. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the hydraulic jack (3) ensuring the opening of at least one valve (2) comprises, in the region of its chamber (20), a bleeding device consisting of a plug which can be opened by means of a command in order to make it possible for the hydraulic fluid contained in said chamber (20) to escape towards a low-pressure circuit.
  9. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that at least one valve (2) is equipped with a measuring device emitting an electrical or electromagnetic signal which informs a computer of the lift height of the valve at a given moment.
  10. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the low-pressure circuit (9) is connected to the pressurized lubrication circuit (15) of the engine (12).
  11. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the low-pressure circuit (9) is independent of the pressurized lubrication circuit (15) of the engine (12).
  12. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the low-pressure circuit (9) is independent of the pressurized lubrication circuit (15) of the engine (12) and is kept at a pressure higher than the atmospheric pressure by means of an additional pump (13).
  13. Hydraulic valve actuator for reciprocating engines according to Claim 12, characterized in that the low-pressure circuit (9) comprises a pressure accumulator (14) .
  14. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the hydraulic positive displacement pump (4) is a vane pump, the stator of which has an inner profile which defines at least one inlet and one outlet which are independent.
  15. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the hydraulic positive displacement pump (4) is a gear pump comprising at least two pinions and at least one inlet and one outlet which are independent.
  16. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the hydraulic positive displacement pump (4) is a variable displacement pump which makes it possible to vary the lifting speed of the valve or valves (2) of the engine (12) under given operating conditions of said engine.
  17. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the pump outlet plug (8) is a solenoid valve controlled by a computer.
  18. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the pump outlet plug (8) is a rotary mechanical device contained in a plug housing (65) and rotating at a speed proportional to that of the crankshaft (5) of the engine (12), and comprising a plug rotor (27) equipped with at least one protuberance (28) periodically plugging one or more pump outlet ports (29) accommodated in said plug housing (65) during the rotation of said plug rotor (27).
  19. Hydraulic valve actuator for reciprocating engines according to Claim 18, characterized in that the leaktightness between the pump outlet port or ports (29) and the protuberances (28) of the plug rotor (27) is reinforced by a device (30) for keeping said pump outlet port or ports (29) in contact with said protuberances (28) when the latter are positioned opposite said pump outlet port or ports (29).
  20. Hydraulic valve actuator for reciprocating engines according to Claim 19, characterized in that the device (30) for keeping in contact consists of a plug piston (31) which is positioned radially in the plug housing (65) and which comprises a pump outlet port (29) which passes right through it longitudinally, said pump outlet port (29) being connected to a pump outlet duct (32) by means of a radial port (33), said plug piston (31) comprises a concave cylindrical bearing face having a radius substantially identical to that of the protuberances (28), so as to have a wide contact surface with said protuberances (28), the plug piston (31) has, on the side of the plug housing (65), a surface subjected to the pressure of the hydraulic fluid which is greater than the contact surface which it has with the protuberances (28), so that said plug piston is kept in contact with said protuberances when the pressure of the fluid increases in the pump outlet duct (32) during the passage of said protuberances (28), and, when there is no protuberance plugging the pump outlet port (29) of the plug piston (31), the latter is kept in bearing contact on the plug housing (65) by means of a spring (56).
  21. Hydraulic valve actuator for reciprocating engines according to Claim 20, characterized in that the plug piston (31) comprises at least one seal ensuring leaktightness between said plug piston (31) and the bore in which it is accommodated.
  22. Hydraulic valve actuator for reciprocating engines according to Claim 18, characterized in that the plug rotor (27) is equipped with a device for angular phase shift with respect to the crankshaft (5) of the engine (12), so that the opening of the valve or valves (2) can be advanced or retarded.
  23. Hydraulic valve actuator for reciprocating engines according to Claim 22, characterized in that the angular phase-shifting device of the plug rotor (27) consists of at least one helical spline arranged on the inside of said plug rotor (27) and cooperating with at least one helical spline arranged on the outside of the driveshaft of said plug rotor (27), the phase shift taking place by means of the translation of said plug rotor (27) parallel to its axis of rotation by means of a fork, and the protuberances being of sufficient width to plug the pump outlet port or ports (29) accommodated in said plug housing (65), whatever their position with respect to the latter.
  24. Hydraulic valve actuator for reciprocating engines according to Claim 18, characterized in that the protuberances (28) of the plug rotor (27) are wide and of variable cross section over the length of the plug rotor (27), so that they have a plugging time which varies as a function of the longitudinal position of the plug rotor (27) with respect to the pump outlet port or ports (29), thus making it possible to increase or reduce the lift stroke of the valve or valves (2), and the longitudinal position of the plug rotor (27) with respect to said pump outlet port or ports (29) is controlled by means of a valve lift fork (62) which makes it possible to impart to said plug rotor (27) a translation parallel to its axis of rotation, said plug rotor (27) comprising at least one straight inner spline cooperating with at least one straight outer spline which a driveshaft comprises.
  25. Hydraulic valve actuator for reciprocating engines according to any one of Claims 18, 23 and 24, characterized in that the angular phase-shifting device of the plug rotor (27), which makes it possible to advance or retard the opening of the valve or valves (2), consists of an opening sleeve (37) comprising, on the one hand, at least one inner helical spline (75) cooperating with at least one outer helical spline (60) which the driveshaft of said opening sleeve (37) comprises and, on the other hand, at least one straight outer spline (76) cooperating with at least one straight inner spline (34) which the plug rotor (27) comprises, said opening sleeve (37) being capable of being actuated in terms of translation parallel to its axis of rotation by means of a valve opening advance fork (61), in order to advance or retard the opening of the valve or valves (2) by means of the angular phase shift of the plug rotor (27) which it drives in rotation, while the lift of the valve or valves (2) is controlled independently by means of the valve lift fork (62) which acts on the longitudinal position of the plug rotor (27) with respect to the pump outlet port or ports (29), said plug rotor (27) comprising the protuberances (28) of variable cross section which ensure a variable plugging time.
  26. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the valve opening selector (11) consists of one or more solenoid valves controlled by a computer.
  27. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the valve opening selector (11) is a rotary mechanical device contained in a housing and rotating at a speed proportional to that of the crankshaft (5) of the engine (12).
  28. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the valve opening selector (11) is a rotary mechanical device contained in a selector housing (66), rotating at a speed proportional to that of the crankshaft (5) of the engine (12) and comprising an opening selector rotor (38) equipped with a cam (39) which actuates one or more valve opening distributors arranged radially in the selector housing (66).
  29. Hydraulic valve actuator for reciprocating engines according to Claim 27, characterized in that the opening selector rotor (38) is equipped with a device for angular phase shift with respect to the crankshaft (5) of the engine (12), so that the valve opening selector (11) can be synchronized with the pump outlet plug (8) and can select the valve or valves (2) at the desired moment.
  30. Hydraulic valve actuator for reciprocating engines according to Claim 28, characterized in that the opening selector rotor (38) comprising a cam (39) is integral with the opening sleeve (37), thus making it possible for the valve opening selector (11) to remain synchronized with the opening moment of the valve or valves (2) which depends on the angular phase shift of the plug rotor (27) with respect to the crankshaft (5) of the engine (12), the valve opening advance fork (61) then making it possible, simultaneously and in the same proportions, to shift the phase of the opening selector rotor (38) and the plug rotor (27) with respect to the crankshaft (5).
  31. Hydraulic valve actuator for reciprocating engines according to Claim 29, characterized in that the angular phase-shifting device of the opening selector rotor (38) consists of at least one helical spline (77) arranged on the inside of said opening selector rotor (38) and cooperating with at least one helical spline arranged on the outside of the driveshaft of said opening selector rotor (38), the phase shift taking place by means of a fork as a result of the translation of said opening selector rotor (38) parallel to its axis of rotation, and the cam (39) being of sufficient width to actuate the valve opening distributors, whatever its longitudinal position with respect to the latter.
  32. Hydraulic valve actuator for reciprocating engines according to Claim 28, characterized in that each valve opening distributor (40) consists of a cylindrical piece (78) equipped with at least one groove (41) and accommodated in a bore arranged in the selector housing (66), each groove (41) being brought, by means of the axial translation of the cylindrical piece (78) imparted by the cam (39), level with at least one duct (42) arranged in the selector housing (66), in order to make it possible for the hydraulic fluid to circulate in each duct (42), said cylindrical piece (78) being kept at a desired distance from the opening selector rotor (38) by the twin action of a shoulder (44) arranged on said cylindrical piece (78) and bearing on the selector housing (66) and of a spring (43) kept compressed by a cap (45) screwed into the selector housing (66).
  33. Hydraulic valve actuator for reciprocating engines according to Claim 32, characterized in that the cap (45) screwed in the selector housing (66) defines a chamber (46) which contains the spring (43) and which is connected to the low-pressure circuit (9) or to the reservoir (58) by means of a duct.
  34. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the valve closing selector (25) consists of one or more solenoid valves controlled by a computer.
  35. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the valve closing selector (25) is a rotary mechanical device contained in a housing and rotating at a speed proportional to that of the crankshaft (5) of the engine (12).
  36. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the valve closing selector (25) is a rotary mechanical device contained in a housing and rotating at a speed proportional to that of the crankshaft (5) of the engine (12) and comprising a closing selector rotor (47) equipped with a cam (48) which actuates one or more valve closing distributors arranged radially in said housing.
  37. Hydraulic valve actuator for reciprocating engines according to Claim 36, characterized in that the closing selector rotor (47) is equipped with a device for angular phase shift with respect to the crankshaft (5) of the engine (12), so that the closing of the valve or valves (2) can be advanced or retarded.
  38. Hydraulic valve actuator for reciprocating engines according to Claim 37, characterized in that the phase-shifting device of the closing selector rotor (47) consists of at least one helical spline (79) arranged on the inside of said closing selector rotor (47) and cooperating with at least one helical spline arranged on the outside of the driveshaft of said closing selector rotor (47), the phase shift taking place by means of a valve closing retard fork (63) by means of the translation of said closing selector rotor (47) parallel to its axis of rotation, and the cam (48) being of sufficient width to actuate the valve closing distributors (49), whatever its longitudinal position with respect to the latter.
  39. Hydraulic valve actuator for reciprocating engines according to Claim 36, characterized in that each valve closing distributor (49) consists of a cylindrical piece (80) equipped with at least one groove (50) and accommodated in a bore arranged in the selector housing (66), each groove (50) being brought, by means of the axial translation of the cylindrical piece (80) imparted by the cam (48), level with at least one duct (42) arranged in the selector housing (66), in order to make it possible for the hydraulic fluid to circulate in each duct (42), said cylindrical piece (80) being kept at a desired distance from the closing selector rotor (47) by the twin action of a shoulder (51) arranged on said cylindrical piece (80) and bearing on the selector housing (66) and of a spring (52) kept compressed by a cap (53) screwed into the selector housing (66).
  40. Hydraulic valve actuator for reciprocating engines according to Claim 39, characterized in that the cap (53) screwed in the selector housing (66) defines a chamber (73) which contains the spring (52) and which is connected to the low-pressure circuit (9) or to the reservoir (58) by means of a duct.
  41. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the high-pressure circuit (10) comprises at least one closing nonreturn valve (54) upstream or downstream of the valve closing selector (25), in order to prevent the hydraulic fluid contained in the hydraulic jack (3) of one or more valves (2) in the closing phase from being capable of being introduced into the hydraulic jack (3) of another valve or other valves (2) which are to remain closed.
  42. Hydraulic valve actuator for reciprocating engines according to Claim 41, characterized in that the closing nonreturn valve (54) positioned upstream or downstream of the valve closing selector (25) consists of a ball kept on its seat by means of a spring.
  43. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the pump inlet nonreturn valve (26) consists of a ball kept on its seat by means of a spring.
  44. Hydraulic valve actuator for reciprocating engines according to Claim 41, characterized in that the hydraulic positive displacement pump (4), the pump outlet plug (8), the valve opening selector (11), the opening nonreturn valve or valves (24), the valve closing selector (25) and the closing nonreturn valve or valves (54), as components, are contained together or in groups in a common housing consisting of one or more parts.
  45. Hydraulic valve actuator for reciprocating engines according to either of Claims 28 and 36, characterized in that the hydraulic positive displacement pump (4), the plug rotor (27), the opening selector rotor (38) and the closing selector rotor (47) or any combination of these four devices are driven in rotation by means of a common shaft (59), itself driven in rotation by the crankshaft (5) of the engine (12) by means of a transmission device.
  46. Hydraulic valve actuator for reciprocating engines according to Claim 45, characterized in that the transmission device driving the common shaft (59) consists of a pulley (74) driven in rotation by the crankshaft (5) of the engine (12) by means of a notched belt or a chain or a gear system consisting of at least one pinion.
  47. Hydraulic valve actuator for reciprocating engines according to Claim 45, characterized in that the common shaft (59) is equipped with at least one helical spline (60) which drives in rotation the plug rotor (27), the opening selector rotor (38), the opening sleeve (37) and the closing selector rotor (47) or any combination of these three devices and cooperates with the helical splines of some of its devices in order to allow their angular phase shift with respect to the crankshaft (5) of the engine (12).
  48. Hydraulic valve actuator for reciprocating engines according to Claim 45, characterized in that the common housing consists of four main housings which contain the common shaft (59) and which are assembled end to end, with respectively:
    Figure imgb0036
    a pump housing (64) comprising the hydraulic positive displacement pump (4) and the pump inlet nonreturn valve or valves (26),
    Figure imgb0044
    a plug housing (65) containing the plug rotor (27) and the pump outlet port or ports (29),
    Figure imgb0044
    a selector housing (66) containing the valve lift fork (62), the opening selector rotor (38), the valve opening distributor or distributors (40), the valve opening advance fork (61), the closing selector rotor (47), the valve closing distributor or distributors (49), the valve closing retard fork (63) and the opening nonreturn valve or valves (24) and capable of comprising the closing nonreturn valve or valves (54),
    Figure imgb0044
    and a closing collector housing (67).
  49. Hydraulic valve actuator for reciprocating engines according to Claim 48, characterized in that the plug housing (65) has passing through it ducts connecting the outlet or outlets (6) of the hydraulic positive displacement pump (4) to the pump outlet plug or plugs (8), on the one hand, and to an opening collector (68) consisting of a network of ducts which is arranged at the parting plane between the plug housing (65) and the selector housing (66), on the other hand, and connecting the inlet or inlets (7) of the hydraulic positive displacement pump (4) to a closing collector (69) consisting of a network of ducts which is arranged at the parting plane between the selector housing (66) and the closing collector housing (67).
  50. Hydraulic valve actuator for reciprocating engines according to Claim 49, characterized in that the selector housing (66) has passing through it longitudinally ducts (42) which connect the opening collector (68) and the closing collector (69) and which can be shut off or opened by means of the valve opening distributor or distributors (40) and by means of the valve closing distributor or distributors (49), said ducts (42) comprising valve outgoing ducts (70) which are located between the valve opening distributor or distributors (40) and the valve closing distributor or distributors (49) and which are connected to the hydraulic jack (3) of the valve or valves (2), said selector housing (66) likewise having passing through it longitudinally one or more ducts which connect the closing connector (69) to the inlet or inlets (7) of the hydraulic positive displacement pump (4).
  51. Hydraulic valve actuator for reciprocating engines according to Claim 50, characterized in that the opening collector (68) makes it possible to connect to one another the ducts (42) which pass longitudinally through the selector housing (66) and which are to be connected to the same pump outlet (6), said pump outlet (6) being connected to said opening collector (68) by means of the duct which passes through the plug housing (65), while the closing collector (69) makes it possible to connect to one another the ducts (42) which pass longitudinally through the selector housing (66) and which are to be connected to the same pump inlet (7), said pump inlet (7) being connected to said closing collector (69) by means of the ducts (42) which pass respectively through the selector housing (66) and the plug housing (65).
  52. Hydraulic valve actuator for reciprocating engines according to Claim 48, characterized in that assembly screws (71) pass right through the various housings (64, 65, 66 and 67) in order to keep them assembled, one or more of said assembly screws (71) being capable of serving as slideway for the forks (61, 62 and 63) which make it possible to control the opening, lift and closing of the valves (2).
  53. Hydraulic valve actuator for reciprocating engines according to Claim 48, characterized in that the valve opening advance fork (61), the valve lift fork (62) and the valve closing retard fork (63) are actuated in terms of translation by means of electric motors controlled by a computer and connected to said forks (61, 62 and 63) by transmission means.
  54. Hydraulic valve actuator for reciprocating engines according to Claim 44, characterized in that the pump outlet port or ports (29) which the protuberances (28) of the plug rotor (27) shut off issue on the inside of the common housing which comprises, in particular, the common shaft (59), said common housing forming a closed chamber connected:
    Figure imgb0044
    to the engine lubricating oil housing (72) by means of a duct,
    Figure imgb0044
    or to the pressurized lubrication circuit (15) of the engine (12),
    Figure imgb0044
    or to a hydraulic fluid housing independent of the engine lubricating oil housing (72),
    Figure imgb0044
    or kept under pressure by the additional pump (13) .
  55. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the same duct connected to the high-pressure hydraulic circuit (10) simultaneously feeds a plurality of hydraulic jacks (3) via a flow divider which ensures that the valves (2) actuated by said hydraulic jacks (3) have a substantially identical lift.
  56. Hydraulic valve actuator for reciprocating engines according to Claim 1, characterized in that the pump outlet plug (8) and the valve opening selector (11) are gathered together in a single combined distributor (81) comprising at least one inlet connected to the outlet (6) of the hydraulic positive displacement pump (4) and capable of being put in relation either with an outlet connected to the low-pressure circuit (9) or with an outlet connected to at least one hydraulic jack (3).
  57. Hydraulic valve actuator for reciprocating engines according to Claim 44, characterized in that the common housing comprises a plinth in which at least one hydraulic jack (3) is accommodated, said plinth being fastened to the cylinder head of the engine (12), so that each hydraulic jack (3) is in contact with the upper end of the stem of the corresponding valve (2) of said engine (12) and can actuate said valve.
EP03750820A 2002-07-23 2003-07-18 Hydraulic valve actuator for reciprocating engine Expired - Lifetime EP1543221B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0209323A FR2842867B1 (en) 2002-07-23 2002-07-23 HYDRAULIC VALVE ACTUATOR FOR PISTON ENGINES
FR0209323 2002-07-23
PCT/FR2003/002271 WO2004011780A1 (en) 2002-07-23 2003-07-18 Hydraulic valve actuator for reciprocating engine

Publications (2)

Publication Number Publication Date
EP1543221A1 EP1543221A1 (en) 2005-06-22
EP1543221B1 true EP1543221B1 (en) 2006-04-12

Family

ID=30011407

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03750820A Expired - Lifetime EP1543221B1 (en) 2002-07-23 2003-07-18 Hydraulic valve actuator for reciprocating engine

Country Status (10)

Country Link
US (1) US7162982B2 (en)
EP (1) EP1543221B1 (en)
JP (1) JP4260743B2 (en)
AT (1) ATE323217T1 (en)
AU (1) AU2003269033B2 (en)
CA (1) CA2492844C (en)
DE (1) DE60304589T2 (en)
ES (1) ES2261965T3 (en)
FR (1) FR2842867B1 (en)
WO (1) WO2004011780A1 (en)

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Publication number Priority date Publication date Assignee Title
DE102006058691A1 (en) * 2006-12-13 2008-06-19 Schaeffler Kg Device for the hydraulic control of gas exchange valves of a reciprocating internal combustion engine
FR2980515B1 (en) * 2011-09-26 2016-03-11 Vianney Rabhi ELECTRO-HYDRAULIC VALVE ACTUATOR WITH ALTERNATIVE CAM
CA2845080A1 (en) * 2012-05-16 2013-04-04 Vianney Rabhi Electro-hydraulic valve actuator having an alternating cam
CN106460593A (en) * 2014-05-12 2017-02-22 博格华纳公司 Crankshaft driven valve actuation
WO2016010732A1 (en) * 2014-07-16 2016-01-21 Borgwarner Inc. Crankshaft driven valve actuation using a connecting rod
FR3071869B1 (en) 2017-10-02 2019-10-11 Vianney Rabhi HYDRAULIC REGENERATION VALVE ACTUATOR
US10704431B2 (en) 2017-10-03 2020-07-07 Vianney Rabhi Regenerative valve hydraulic actuator
KR102371063B1 (en) 2017-11-20 2022-03-07 현대자동차주식회사 Control system for variable valve apparatus and oil control valve
EP3728904B1 (en) * 2017-12-21 2022-01-05 Volvo Truck Corporation An auxiliary transmission brake arrangement
EP4065821B1 (en) * 2019-11-27 2023-10-04 Piaggio & C. SpA Camshaft with phasing device for multicylinder internal combustion engine with poppet valves

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DE2940112A1 (en) * 1979-10-03 1981-04-16 Daimler-Benz Ag, 7000 Stuttgart PRESSURE CONTROLLER
US5255641A (en) * 1991-06-24 1993-10-26 Ford Motor Company Variable engine valve control system
DE4232573A1 (en) * 1991-10-12 1993-04-15 Volkswagen Ag Valve for IC engine combustion chamber - has second pressure chamber, connected to first chamber, and limited by pressure piston, subject to combustion chamber pressure
US5713331A (en) * 1994-12-21 1998-02-03 Mannesmann Rexroth Gmbh Injection and exhaust-brake system for an internal combustion engine having several cylinders
DE10143959A1 (en) * 2001-09-07 2003-03-27 Bosch Gmbh Robert Hydraulically controled actuator for valve, especially gas replacement valve in combustion engine, has control piston with area of working surface(s) changing along piston displacement path

Also Published As

Publication number Publication date
US20060102117A1 (en) 2006-05-18
FR2842867B1 (en) 2004-10-08
CA2492844A1 (en) 2004-02-05
ATE323217T1 (en) 2006-04-15
DE60304589D1 (en) 2006-05-24
AU2003269033A1 (en) 2004-02-16
JP4260743B2 (en) 2009-04-30
JP2005533962A (en) 2005-11-10
EP1543221A1 (en) 2005-06-22
CA2492844C (en) 2010-10-19
AU2003269033B2 (en) 2008-11-27
ES2261965T3 (en) 2006-11-16
FR2842867A1 (en) 2004-01-30
US7162982B2 (en) 2007-01-16
DE60304589T2 (en) 2007-02-08
WO2004011780A1 (en) 2004-02-05

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