EP0980466A1 - Device for varying a piston engine effective volumetric displacement and/or volumetric ratio of during its operation - Google Patents

Device for varying a piston engine effective volumetric displacement and/or volumetric ratio of during its operation

Info

Publication number
EP0980466A1
EP0980466A1 EP98924396A EP98924396A EP0980466A1 EP 0980466 A1 EP0980466 A1 EP 0980466A1 EP 98924396 A EP98924396 A EP 98924396A EP 98924396 A EP98924396 A EP 98924396A EP 0980466 A1 EP0980466 A1 EP 0980466A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
piston
engine
control
controls
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.)
Granted
Application number
EP98924396A
Other languages
German (de)
French (fr)
Other versions
EP0980466B1 (en
Inventor
Vianney Rabhi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from FR9705943A external-priority patent/FR2763096B1/en
Application filed by Individual filed Critical Individual
Publication of EP0980466A1 publication Critical patent/EP0980466A1/en
Application granted granted Critical
Publication of EP0980466B1 publication Critical patent/EP0980466B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
    • F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/348—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear by means acting on timing belts or chains

Definitions

  • the subject of the present invention is a device making it possible to vary the effective displacement and / or volumetric ratio of a piston engine during its operation.
  • volumetric ratio is also, according to the usual language, a geometric relation existing between the chamber volume and the volume defined by the stroke that multiplies the bore. We will retain here the effective volumetric ratio determined by the effective compression ratio of the fresh gases.
  • the maximum efficiency of internal combustion piston engines is generally recorded at full load, ie throttle valve at full opening, at speed or range of speed where the average effective pressure of the engine cycle is at its maximum value.
  • the main characteristic of the engines which defines their maximum output power and speed is their displacement.
  • large displacement motors consume more energy than large displacement motors, due to a greater distance from their operating conditions generating maximum efficiency.
  • the disadvantages of large displacement engines can become an advantage in conditions of use requiring high power, for example on high speed motorways.
  • the adjustment of the power of the engines is carried out mainly by action on their speed via a gearbox, and on their load through the throttle valve which controls the intake pressure by rolling and modifies the filling rate of the cylinder (s) and the effective average pressure of the engine cycle.
  • Another characteristic of the engines determines their general performance: it is their volumetric ratio. This is defined by the relationship between the volume of the cylinder and the volume of the explosion chamber. This ratio is fixed, it is calculated taking into account the maximum load conditions of the engine and the fuel used, or at partial load or when the cylinder is insufficiently filled at high revs, this ratio could be significantly increased in order to increase the engine efficiency. If the advantage of adapting the engine displacement to the work required of them is obvious, today there is practically no effective device enabling engines, and in particular automobile engines, to obtain this result. However, devices have been tested which in particular provide for disengaging or rendering a certain number of cylinders passive on multi-cylinder engines.
  • the device according to the invention has the following advantages according to a particular embodiment:
  • the engine automatically adapts its displacement to the work requested of it, taking into account the operating conditions which are imposed on it. • Associated with a supercharging device, the engine can be smaller than a conventional engine while retaining a high power and this without penalizing the efficiency at partial load.
  • the engine adapts its volumetric ratio to said filling conditions in order to optimize its performance, ie, it optimizes its effective compression ratio as a function of the diet.
  • the maximum power of the engine is increased, in particular by improving the filling of its cylinder (s) at high speed.
  • the idle speed can be lowered by reducing the residual burnt gas.
  • the engine can operate at degraded efficiency allowing rapid heating of the catalyst used in the exhaust to treat pollutants.
  • the engine cycle exploits a longer expansion stroke than the stroke used to compress the gases, the expansion diagram then being truncated later than on an engine of the same displacement as defined according to the prior art.
  • the time necessary for the compression of the gases is reduced, this limits the time of confinement of the gases which is favorable for triggering undesirable detonation effects.
  • the device according to the invention comprises, according to a first characteristic:
  • a system allowing the volumetric ratio of the engine to be controlled during its operation.
  • the system acts by modifying the origin of the stroke of the piston relative to the cylinder without modifying the length of said stroke.
  • a system for monitoring the effective displacement of the engine operates by pushing back into the intake manifold part of the gases admitted into the engine cylinder thanks to the assistance of an additional intake valve.
  • the closing of the additional intake valve can be significantly delayed so that the piston expels excess inlet gas during its ascent into the cylinder and the start of gas compression takes place later during the upward stroke of the piston.
  • the intake valve as defined according to the prior art can itself be used for this task, this by checking its opening and closing diagrams.
  • This device according to the invention comprises in particular for a displacement:
  • a piston provided with a rack mounted integrally with its lower part, said rack constituting one of the parts of a meshing system, and being held in a guide system which allows it a movement of longitudinal translation.
  • a control rack mounted in a cavity or on a guide arranged in the engine block which allows it a longitudinal translation movement, the position of said control rack being controlled by a control device.
  • a connecting rod mounted freely on the crankshaft of the engine which comprises in its upper part a free mounted gear, said gear constituting the element for transmitting movement between the piston and said connecting rod.
  • a control device which makes it possible to act on the position of the control rack taking account of the result of the processing of the parameters coming from said probes;
  • a servo device which makes it possible to act on the angular offset of the camshaft controlling the opening of the additional intake valve taking into account the result of the processing of the parameters coming from said probes.
  • the device according to the invention comprises:
  • the gear is designed to constitute the member for transmitting the movement between the piston and the connecting rod;
  • a control device which acts on the position of the control rack and which includes:
  • At least one hydraulic cylinder or any other system making it possible to impart a translational movement to the control rack and made integral with said control rack by any mechanical connection;
  • At least one hydraulic cylinder or any other system making it possible to constitute a device which controls the angular offset of the camshaft which controls the opening of the additional intake valve, said hydraulic cylinder being able to act, according to a particular mode of embodiment and by way of nonlimiting example, on the position of an additional pulley thus varying the length of belt or chain located between the pulley of the camshaft of the intake and exhaust valves of the engine such as defined according to the prior art, and the pulley of the camshaft of the additional intake valve; • And a device which controls the angular offset of the camshaft controlling the opening of the additional intake valve and which does not necessarily act on the camshaft controlling the intake and exhaust valves of the motor as defined according to the rules of the prior art.
  • the latter has, according to a particular embodiment, the following advantages:
  • the control system provides in particular that:
  • a control rod positioned parallel to the cylinder axis having a shoulder and being able to move longitudinally, said control rod passing right through the cylinder cover, the cylinder body and the cylinder piston by means of orifices in said cylinder cover, cylinder body and cylinder piston;
  • Valves housed in a duct arranged in the mass of the cylinder piston, allowing the circulation of hydraulic fluid between the upper and lower chambers of the cylinder to be authorized or prohibited as defined by the position of the cylinder piston relative to the body cylinder;
  • a non-return valve housed in a hydraulic fluid inlet duct, the orifice of which opens into the central part of the cylinder body, said non-return valve allowing the entry of hydraulic fluid into the cylinder body, but preventing the outlet ;
  • Sealing devices which can be made, according to a particular embodiment according to the invention, of rubber O-rings. According to a particular embodiment, its operation requires one or more low-power servo means making it possible to act on the longitudinal position of the control rod relative to the jack body, taking account of the operating requirements of the engine.
  • the control device making it possible to act on the position of the control rack comprises:
  • An eccentric longitudinal duct which is arranged in the mass of the cylinder piston and which connects the lower and upper circular surfaces of said cylinder piston.
  • the duct is designed so that it constitutes a housing for the two valves making it possible to authorize or prohibit the circulation of the hydraulic fluid.
  • the conduit is of a diameter greater than that of the valves in order to allow the flow of the fluid through said conduit when said valves are open;
  • An eccentric longitudinal duct which is arranged in the mass of the cylinder piston and which ensures the longitudinal guidance of the control rod; •
  • a cylinder piston which has a cavity on its cylindrical surface opposite the hydraulic fluid inlet orifice opening into the central part of the cylinder body. The cavity has a height at least equivalent to the maximum stroke of the cylinder piston and is connected to the eccentric longitudinal duct arranged in the mass of the cylinder piston;
  • Valves which allow the circulation of hydraulic fluid between the upper and lower chambers of the cylinder to be authorized or prohibited as defined by the position of the cylinder piston relative to the cylinder body.
  • the valves consist of rings which can slide around the control rod. The inside diameter of the valves is less than the diameter of the shoulder of the control rod. When the valves are not kept open by the shoulder of the control rod, they are held in their seats by springs;
  • a shoulder of the control rod which ensures the centering of said control rod in the eccentric longitudinal duct arranged in the mass of the cylinder piston.
  • the shoulder makes it possible to move one or the other of the valves making it possible to authorize or prohibit the circulation of the hydraulic fluid between the upper and lower chambers of the jack.
  • the shoulder is provided with grooves or grooves allowing the circulation of the fluid through the conduit;
  • a non-return valve which is housed in the hydraulic fluid inlet pipe, the orifice of which opens into the central part of the jack body and which may consist, according to a particular embodiment, of a ball held on carried by a spring and closing a hole;
  • a hydraulic fluid inlet conduit whose orifice opens into the central part of the cylinder body and which can be connected, according to a particular embodiment, to the pressurized hydraulic circuit ensuring the lubrication of the variable displacement engine.
  • the device according to the invention making it possible to vary the effective displacement and / or the volumetric ratio of a piston engine during its operation, comprises:
  • a first device making it possible to control the volumetric ratio of the engine by acting by modifying the origin of the stroke of the piston relative to the cylinder without modifying the length of said stroke;
  • the device according to the present invention comprises a first device making it possible to control the volumetric ratio of the engine constituted by a gear system which comprises: • A rack integral with the lower part of the piston and which is held in a guide system allowing a longitudinal translational movement to said rack;
  • the device according to the present invention comprises a second device for controlling the effective displacement of the engine consisting of an additional intake valve and a device which controls its opening / closing and which makes it possible to modify the angular offset of the closing point. and opening said valve relative to the crankshaft.
  • the device according to the present invention comprises a second device making it possible to control the effective displacement of the engine without an additional intake valve consisting of a device which controls the opening and closing of the intake valve known per se and which makes it possible to modify the angular offset of the point of closure and opening of said valve relative to the crankshaft.
  • the device according to the present invention comprises a device controlling the opening and closing of the additional intake valve which is a camshaft controlled by a device which controls its angular offset relative to the crankshaft of the engine.
  • the device according to the present invention comprises a device controlling the opening and closing of the intake valve known per se which consists of an additional camshaft controlled by a device which controls its angular offset relative to the engine crankshaft , said additional camshaft actuating said valve via a mechanical connection in addition to the movement imparted to said valve by its camshaft.
  • the device according to the present invention comprises a device controlling the angular offset of the camshaft controlling the opening of the additional intake valve which consists of an intermediate pulley whose position defines the length of the timing belt or chain between the camshaft pulley of the engine intake and exhaust valves and the camshaft pulley which controls the opening of the additional intake valve.
  • the device according to the present invention comprises a device controlling the position of the control rack which consists of a hydraulic cylinder which acts on said rack via a mechanical connection.
  • the device according to the present invention comprises a device which controls the position of the intermediate pulley consisting of a hydraulic cylinder.
  • the device according to the present invention comprises a gear having a truncated profile so as to retain only the teeth useful for the transmission of movement between the piston and the connecting rod.
  • the device according to the present invention comprises rolling surfaces which are arranged respectively on the gear and the racks ensuring permanent centering of said gear between said racks, while the point of contact between said rolling surfaces is permanently positioned at the primitive of the gear.
  • the device according to the present invention comprises a piston whose cylindrical part is of a height sufficient to accommodate segments, but does not include a skirt ensuring its longitudinal guidance.
  • the device making it possible to vary the effective displacement and / or the volumetric ratio of a piston engine comprises a device controlling the position of the control rack which comprises:
  • a hydraulic cylinder comprising means for extending its axis making it possible to maintain a volume of fluid displaced as a function of the stroke of the cylinder piston which is identical for each of the upper and lower chambers of said cylinder.
  • Control means which make it possible to move towards a determined position or to maintain in a determined position the axis of the jack with respect to the body of the jack.
  • the device according to the present invention comprises a control device which comprises:
  • An actuator body mounted fixed relative to the engine block parallel to the control rack, an actuator cover mounted fixed relative to the actuator body, an actuator piston, an actuator axis and an actuator axis extension assembly with the control rack, which constitute the upper guide system of said control rack and which can move longitudinally relative to the cylinder body;
  • Control means which consist of a control rod having a shoulder and which can move longitudinally, said control rod being positioned parallel to the cylinder axis and passing right through the cylinder cover, the body of cylinder and the cylinder piston by means of orifices arranged in said cylinder cover, cylinder body and piston cylinder, valves housed in a conduit placed longitudinally and eccentrically arranged in the mass of the cylinder piston, said valves making it possible to authorize or prohibit the circulation of hydraulic fluid between the upper and lower chambers of the cylinder as defined by the position of the jack piston relative to the jack body, said valves being made up of rings which can slide around the control rod, and their internal diameter being less than the diameter of the shoulder of the control rod so that 'it is possible to keep them open thanks to said shoulder of said control rod, when said valves are not kept open by said shoulder of said control rod, they are held in their seat by springs, and a check valve -return housed in a hydraulic fluid inlet conduit whose orifice opens into the central part of the central
  • the device according to the present invention comprises a control device which comprises a jack piston provided with a cavity on its cylindrical surface facing the orifice of the hydraulic fluid inlet pipe opening into the central part of the jack body, said cavity being of a height at least equivalent to the maximum stroke of said cylinder piston and being connected to the conduit placed longitudinally and eccentrically arranged in the mass of said cylinder piston connecting the lower and upper circular surfaces of said cylinder piston a connecting channel.
  • the device according to the present invention comprises a control device which comprises a non-return valve consisting of a ball held on a bearing by a spring and closing an orifice.
  • the device according to the present invention comprises a control device which comprises a hydraulic fluid inlet pipe, one of the orifices of which opens into the central part of the jack body and which is connected to the pressurized hydraulic circuit ensuring the lubrication of the engine. with variable displacement.
  • the device according to the present invention comprises a control device which comprises sealing elements made up of rubber O-rings.
  • the device according to the present invention comprises a control device whose shoulder ensures the centering of the control rod in the conduit placed longitudinally and eccentrically arranged in the mass of said cylinder piston, said shoulder comprising grooves or grooves allowing the circulation of hydraulic fluid through said conduit.
  • Figure 1 is a schematic sectional front view of the device according to the invention.
  • Figure 2 is a schematic sectional right view along line AA of Figure 1 of the device according to the invention.
  • Figure 3 is a schematic sectional view of the opening control device of the intake valve as defined according to the prior art, which, according to a variant of the device according to the invention, can be used to control the displacement of the motor.
  • Figure 4 is a perspective view showing the arrangement of the main elements which constitute the device according to the invention.
  • FIG. 5 is an overall view showing the positioning of the control device according to the invention which makes it possible to act on the position of the control rack relative to the other elements constituting the variable displacement motor, and the representation of an alternative embodiment of the meshing system.
  • Figure 6 is a schematic sectional front view of the control rack control device.
  • Figure 7 is a perspective view showing the arrangement and appearance of the main elements which constitute the device for controlling the position of the control rack according to the invention.
  • the device according to the invention is inserted in an environment well known from the prior art: piston engines.
  • FIGS 1 to 4 there is shown an engine comprising a piston 1, a cylinder 2, valves 3, 4, 15 or 22, an engine block 5, a cylinder head 6, a crankshaft 7, a spark plug 8 and a explosion chamber 9.
  • the device according to the invention essentially comprises a rack 10 integral with the lower part of the piston 1, a control rack 11 mounted in a cavity or on a guide, arranged in the engine block 5, a device 12 which controls the position of said control rack relative to the engine block. It also includes a connecting rod 13 mounted free on the crankshaft 7 of the engine and which comprises in its upper part a gear 14 mounted free.
  • the cylindrical part of the piston 1 is of sufficient height to accommodate the segments, but does not have a skirt ensuring its longitudinal guidance (Figure 5).
  • the gear 14 may have a truncated profile so as to retain only the teeth useful for the transmission of movement between the piston 1 and the connecting rod 13 ( Figure 5).
  • the rolling surfaces are arranged respectively on the gear 14 and the racks 10, 11 ensuring the permanent centering of the said gear between the said racks, while the point of contact between the said rolling surfaces is permanently positioned at the level of the primitive of the gear 14 ( Figure 5).
  • the device according to the invention further comprises an additional intake valve 15 whose camshaft 16 controlling its opening is controlled by a device 17 which controls its angular offset relative to the crankshaft 7 of the engine.
  • the function fulfilled by the additional intake valve 15 can be assumed by the intake valve 22 as defined according to the prior art as shown in FIG. 3.
  • the additional device then makes it possible to modify the angular offset of the point of closure and opening of the valve 22 relative to the crankshaft 7.
  • the additional device may include an additional camshaft 21 slaved to a device not shown which controls its angular offset relative to the engine crankshaft.
  • the additional camshaft 21 actuates the inlet valve 22 via a mechanical connection 23 in addition to the movement imparted to said valve by its camshaft 24 as defined according to the prior art.
  • the device according to the invention may also include various accessories, not shown, such as probes transmitting various operating parameters of the engine, one or more computers or devices processing the information coming from said probes and a system allowing the device to be subjected 12 which controls the position of the control rack 11 with respect to the engine block 5 and the device 17 which controls the angular offset of the additional intake valve 15 as a result of the processing of the information from said probes.
  • various accessories not shown, such as probes transmitting various operating parameters of the engine, one or more computers or devices processing the information coming from said probes and a system allowing the device to be subjected 12 which controls the position of the control rack 11 with respect to the engine block 5 and the device 17 which controls the angular offset of the additional intake valve 15 as a result of the processing of the information from said probes.
  • the operation of the device making it possible to vary the effective displacement and / or the volumetric ratio of a piston engine is as follows:
  • the modification of the effective displacement of the engine while maintaining an adequate volumetric ratio is effected by the combined action of the devices making it possible to control, during its operation, the volumetric ratio of the engine on the one hand and the effective displacement of said engine on the other.
  • the volumetric ratio of the engine is checked by checking the original position of the stroke of the piston 1 relative to the cylinder 2, without modifying the length of said stroke.
  • the effective displacement of the engine is checked as follows:
  • the control device 12 of the rack 11 receives the order to move said control rack 11. This order is materialized, for example, by the introduction into a hydraulic cylinder 25 of a certain volume of pressurized oil from of a pump (not shown).
  • the volume introduced is previously calculated by the device (s) (not shown) processing the information coming from parametric engine probes (not shown).
  • the action of the control device 12 on the control rack 11 by means of a mechanical link 20 has the effect of imparting to said control rack 11 a translational movement parallel to its longitudinal axis.
  • the control rack 11 constitutes a meshing system with the gear 14 mounted freely in the upper part of the connecting rod 13 and the rack 10 secured to the lower part of the piston 1.
  • the displacement of the control rack 11 implies a modification the point of origin of the stroke of the piston 1 relative to the cylinder 2.
  • the modification of the point of origin of the stroke has the effect of modifying the volume of the explosion chamber 9, the length of said stroke being unchanged, the engine's volumetric ratio is changed.
  • the control of the effective displacement of the engine also operates as follows:
  • the device 17 which controls the angular offset of the camshaft 16 which controls the opening of the additional intake valve 15 receives the order to delay or to advance the closing of said additional intake valve 15.
  • This order is materialized according to a particular embodiment of the control device 17 by the introduction into a hydraulic cylinder 26 of a certain volume of pressurized oil from of a pump (not shown).
  • the volume introduced is calculated beforehand by the device (s) not shown performing the processing of information coming from parametric engine probes (not shown).
  • the hydraulic cylinder 26 can act on the position of an intermediate pulley 18 which modifies the length of timing belt 27 or chain between the pulley 28 of the camshaft 24 of the intake 3 and exhaust 4 valves of the engine, and the pulley 29 of the camshaft 16 which controls the opening of the additional intake valve 15.
  • a delay calculated on closing the additional intake valve 15 has the effect of allowing the piston 1 to discharge into the intake manifold 19 a certain quantity of fresh gas admitted in excess on the one hand, and to exploit only part of the length of the stroke of the piston 1 to compress the gases on the other hand.
  • the fresh gases discharged into the intake manifold 19 can be re-aspirated by a neighboring cylinder during the intake phase.
  • the device according to the invention provides that the ratio between the volume of the explosion chamber defined by the system which controls the volumetric ratio and the length of the piston stroke used to compress the fresh gases may not remain constant, in order to to allow the engine to work according to the highest effective volumetric ratio possible authorized by the operating conditions of said engine.
  • FIGS. 5 to 7 show an alternative embodiment of the device 12 which controls the position of the control rack 11 relative to the engine block 5.
  • the control device 12 essentially comprises a jack body 45 mounted fixed relative to the engine block 5 parallel to the control rack 11, a jack cover 46 mounted fixed relative to the jack body 45, a jack piston 47, a cylinder axis 48 and a cylinder axis extension 49 assembled with the control rack 11, which constitute the upper guide system of said control rack 11 and which can move longitudinally relative to the cylinder body 45.
  • control means 42 which consist of a control rod 50 provided with a shoulder 51 and which can move longitudinally.
  • the control rod 50 is positioned parallel to the actuator axis 48 and passes right through the actuator cover 46, the actuator body 45 and the actuator piston 47 by means of conduits arranged in said actuator covers 46, cylinder body 45 and cylinder piston 47.
  • the control means 42 also consist of valves 52, 53 housed in a conduit 54 arranged in the mass of the cylinder piston 47.
  • the valves 52, 53 make it possible to authorize or prohibit the circulation of the hydraulic fluid between the upper 40 and lower 41 chambers of the jack as defined by the position of the jack piston 47 relative to the jack body 45.
  • the valves 52, 53 consist of rings which can slide around the control rod 50. The internal diameter of the rings is provided smaller than the diameter of the shoulder 51 of the control rod 50 so that it is possible to keep them open by said audit the shoulder 51.
  • the control means 42 consist of a non-return valve 43 housed in a hydraulic fluid inlet conduit 57, one of the orifices of which opens into the central part of the jack body 45.
  • the non-return valve 43 authorizes the entry of hydraulic fluid into the cylinder body 45, but prohibits the exit.
  • the valve 43 may consist, according to a particular embodiment, of a ball 58 held on a surface by a spring 59 in order to close an orifice 44.
  • the control means 42 of the device 12 provide that the jack piston 47 has a cavity 30 on its cylindrical surface opposite the inlet duct 57 provided in the central part of the jack body 45.
  • the cavity 30 is of a height at least equivalent to the maximum stroke of the cylinder piston 47.
  • the cavity 30 communicates with the conduit 54 placed longitudinally and eccentrically in order to connect the lower and upper circular surfaces of the cylinder piston 47, by a connecting channel 31.
  • control means 42 also provide that the moving elements 49, 48, 47, 50, 52, 53 are respectively provided with sealing elements which may consist of rubber O-rings 32, 33, 34, 35, 36 , 37, 38, 39.
  • control device 12 shown in Figures 5 to 7 is as follows:
  • the position of the control rack 11 is checked by means of the control rod 50, the position of which determines the position of the jack piston 47 by the action of the two valves 52, 53.
  • valves 52, 53 make it possible to control the volume of oil trapped respectively in the upper 40 and lower 41 chamber of the hydraulic cylinder.
  • the control of the position of the control rack 11 operates as follows
  • the computer not shown which permanently defines the adequate height of the control rack 11 taking into account the operating conditions of the engine acts on the position of the control rod 50 via a servo device which can for example consist of a low power electric stepper motor (not shown).
  • the new position of the control rod 50 relative to the cylinder piston 47 integral with the control rack 11, has the effect of opening the valve 52, 53 located on the side of the direction of movement of said control rod 50, the valve then being lifted by the shoulder 51.
  • valve 52, 53 open, one or more cycles of change of direction of the additional effort may be necessary.
  • the valve 52, 53 remained free relative to the control rod 50 then ensuring a non-return role preventing the hydraulic fluid stored on its side from returning to the side of the valve 52, 53 is kept open by the control rod 50, and this until the desired position of the cylinder piston 47 is obtained relative to the cylinder body 45.
  • Closing and opening the corresponding valves has the effect of filling the chamber opposite to the leaking chamber of hydraulic fluid admitted via the non-return valve 43 housed in the conduit 57.
  • the hydraulic fluid is conveyed to the chamber 40, 41 opposite to the leaking chamber thanks to the cavity 30 provided on the cylindrical surface of the cylinder piston 47 which is opposite on the one hand with the orifice of the conduit 57 opening into the central part of the cylinder body 45 and on the other hand with the connecting channel 31 which connects said cavity 30 to the conduit 54, arranged in the mass of the cylinder piston 47.
  • the position of the control rod 50 therefore permanently conditions the position of the control rack 11 relative to the engine block 5, and therefore the volume of the explosion chamber 9 of the engine. It is thus possible to control the chamber volume of the engine with a very low-power servo device (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Characterised By The Charging Evacuation (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Actuator (AREA)
  • Vehicle Body Suspensions (AREA)
  • Forklifts And Lifting Vehicles (AREA)

Abstract

A device for varying an effective volumetric displacement and/or an effective volumetric ratio of an engine which comprises a piston and a cylinder, the device comprising a first device for controlling the effective volumetric ratio of the engine by modifying a starting point of a stroke of the piston with respect to the cylinder, and a second device for controlling the effective volumetric displacement of the engine by discharging into an inlet pipe excess gases let into the cylinder of the engine.

Description

DISPOSITIF PERMETTANT DE FAIRE VARIER LA DEVICE FOR VARIING THE
CYLINDREE ET/OU LE RAPPORT VOLUMETRIQUECYLINDER AND / OR THE VOLUMETRIC RATIO
EFFECTIFS D'UN MOTEUR A PISTONS PENDANT SONWORKFORCE OF A PISTON ENGINE DURING ITS
FONCTIONNEMENTOPERATION
La présente invention a pour objet un dispositif permettant de faire varier la cylindrée et/ou le rapport volumétrique effectifs d'un moteur à pistons pendant son fonctionnement.The subject of the present invention is a device making it possible to vary the effective displacement and / or volumetric ratio of a piston engine during its operation.
La cylindrée d'un moteur désigne usuellement les caractéristiques géométriques dudit moteur définit par la course et l'alésage. Nous retiendrons ici la notion de cylindrée effective représentée par le volume de gaz à précision atmosphérique effectivement retenue par le moteur pour réaliser chaque cycle.The displacement of an engine usually designates the geometric characteristics of said engine defined by the stroke and the bore. We will retain here the notion of effective cubic capacity represented by the volume of gas with atmospheric precision actually retained by the engine to carry out each cycle.
Le rapport volumétrique est également, selon le langage usuel, une relation géométrique existant entre le volume de chambre et le volume définit par la course que multiplie l'alésage. Nous retiendrons ici le rapport volumétrique effectif déterminé par le taux de compression effectif des gaz frais.The volumetric ratio is also, according to the usual language, a geometric relation existing between the chamber volume and the volume defined by the stroke that multiplies the bore. We will retain here the effective volumetric ratio determined by the effective compression ratio of the fresh gases.
Le rendement maximum des moteurs à combustion interne à pistons est en général enregistré à pleine charge, c'est à dire papillon des gaz à pleine ouverture, au régime ou plage de régime où la pression moyenne effective du cycle moteur est à sa valeur maximum.The maximum efficiency of internal combustion piston engines is generally recorded at full load, ie throttle valve at full opening, at speed or range of speed where the average effective pressure of the engine cycle is at its maximum value.
A ces conditions de fonctionnement correspondent, pour chaque moteur, une puissance et un régime définis. Ceci revient à dire que dès lors que le travail demandé à un moteur ne correspond pas à ces conditions de puissance et de régime, son rendement décroît.These operating conditions correspond, for each engine, to a defined power and speed. This amounts to saying that as soon as the work required of an engine does not correspond to these conditions of power and speed, its output decreases.
La principale caractéristique des moteurs qui définit leur puissance et régime de rendement maximum, est leur cylindrée.The main characteristic of the engines which defines their maximum output power and speed is their displacement.
En utilisation courante, notamment dans le domaine de l'automobile, les conditions de fonctionnement des moteurs génératrices d'un rendement optimal sont rarement réunies. En effet, la cylindrée des moteurs est constante et la puissance qui leur est demandée par le conducteur varie de façon considérable.In current use, especially in the automotive field, the operating conditions of engines generating optimum performance are rarely met. In fact, the engine displacement is constant and the power demanded by the driver varies considerably.
En pratique générale, plus les conditions de travail imposées au moteur par le conducteur sont éloignées de ses conditions de rendement maximal, plus son rendement est bas.In general, the more the working conditions imposed on the engine by the driver are far from its conditions of maximum efficiency, the lower its efficiency.
En utilisation à faible puissance, par exemple lors de déplacements urbains, à travail égal, les moteurs de grosse cylindrée consomment plus d'énergie que les moteurs de grosse cylindrée, du fait d'un éloignement plus important de leurs conditions de fonctionnement génératrices d'un rendement maximal. Les inconvénients des moteurs de grosse cylindrée peuvent devenir un avantage lors de conditions d'utilisation nécessitant une forte puissance, par exemple sur autoroute à vitesse élevée.In use at low power, for example during urban journeys, for the same work, large displacement motors consume more energy than large displacement motors, due to a greater distance from their operating conditions generating maximum efficiency. The disadvantages of large displacement engines can become an advantage in conditions of use requiring high power, for example on high speed motorways.
Dans tous les cas, le réglage de la puissance des moteurs s'opère principalement par action sur leur régime par l'intermédiaire d'une boîte de vitesses, et sur leur charge par le biais du papillon des gaz qui contrôle la pression d'admission par laminage et modifie le taux de remplissage du(des) cylindre(s) et la pression moyenne effective du cycle moteur.In all cases, the adjustment of the power of the engines is carried out mainly by action on their speed via a gearbox, and on their load through the throttle valve which controls the intake pressure by rolling and modifies the filling rate of the cylinder (s) and the effective average pressure of the engine cycle.
Une autre caractéristique des moteurs détermine leur rendement général : c'est leur rapport volumétrique. Celui-ci est défini par la relation existant entre le volume du cylindre et le volume de la chambre d'explosion. Ce rapport est fixe, il est calculé en tenant compte des conditions de charge maximales du moteur et du carburant utilisé, or, à charge partielle ou lorsque le cylindre est insuffisamment rempli à hauts régimes, ce rapport pourrait être sensiblement augmenté afin d'accroître le rendement du moteur. Si l'avantage d'adapter la cylindrée des moteurs au travail qui leur est demandé est évident, il n'existe aujourd'hui pratiquement aucun dispositif performant permettant aux moteurs, et en particulier aux moteurs d'automobiles, d'obtenir ce résultat. Des dispositifs ont toutefois été expérimentés qui prévoient notamment de débrayer ou de rendre passifs un certain nombre de cylindres sur des moteurs multi-cylindres.Another characteristic of the engines determines their general performance: it is their volumetric ratio. This is defined by the relationship between the volume of the cylinder and the volume of the explosion chamber. This ratio is fixed, it is calculated taking into account the maximum load conditions of the engine and the fuel used, or at partial load or when the cylinder is insufficiently filled at high revs, this ratio could be significantly increased in order to increase the engine efficiency. If the advantage of adapting the engine displacement to the work required of them is obvious, today there is practically no effective device enabling engines, and in particular automobile engines, to obtain this result. However, devices have been tested which in particular provide for disengaging or rendering a certain number of cylinders passive on multi-cylinder engines.
Aucun de ces dispositifs, en raison de leur lourdeur de mise en œuvre et de leur efficacité relative, n'a pu être considéré comme digne d'être reproduit en grand nombre.None of these devices, because of their cumbersome implementation and their relative effectiveness, could not be considered worthy of being reproduced in large numbers.
S'il est avantageux, pour conserver un rendement optimal, d'adapter le rapport volumétrique des moteurs aux conditions de remplissage de leur(s) cylindre(s), notamment à hauts régimes, aucun dispositif n'apporte aujourd'hui de solution pertinente qui permette d'obtenir un tel résultat.If it is advantageous, in order to maintain optimal efficiency, to adapt the volumetric ratio of the engines to the conditions of filling of their cylinder (s), in particular at high revs, no device today provides any relevant solution. which allows to obtain such a result.
C'est pour améliorer de façon significative le rendement global des moteurs à combustion interne à pistons, tenant compte de leur contexte d'utilisation variable, que le dispositif selon l'invention prévoit que tout moteur qui en est doté présente des particularités qui le distinguent d'un moteur tel que défini selon les règles de l'art antérieur.It is in order to significantly improve the overall efficiency of internal combustion piston engines, taking into account their context of variable use, that the device according to the invention provides that any engine which is provided with it has characteristics which distinguish it. an engine as defined according to the rules of the prior art.
Ainsi le dispositif suivant l'invention présente selon un mode particulier de réalisation les avantages suivants :Thus, the device according to the invention has the following advantages according to a particular embodiment:
• Afin de rester à l'optimum de son rendement, le moteur adapte automatiquement sa cylindrée au travail qui lui est demandé, tenant compte des conditions de régime qui lui sont imposées. • Associé à un dispositif de suralimentation le moteur peut être de plus petites dimensions qu'un moteur conventionnel en conservant une puissance élevée et ceci sans pénaliser le rendement à charge partielle.• In order to remain at optimum performance, the engine automatically adapts its displacement to the work requested of it, taking into account the operating conditions which are imposed on it. • Associated with a supercharging device, the engine can be smaller than a conventional engine while retaining a high power and this without penalizing the efficiency at partial load.
• Lors de mauvaises conditions de remplissage de son(ses) cylindre(s), notamment à régime élevé, le moteur adapte son rapport volumétrique auxdites conditions de remplissage afin d'optimiser son rendement soit, il optimise son taux de compression effectif en fonction du régime.• During poor filling conditions of its cylinder (s), in particular at high speed, the engine adapts its volumetric ratio to said filling conditions in order to optimize its performance, ie, it optimizes its effective compression ratio as a function of the diet.
« La puissance maximale du moteur est accrue notamment par amélioration du remplissage de son(ses) cylindre(s) à régime élevé.“The maximum power of the engine is increased, in particular by improving the filling of its cylinder (s) at high speed.
• Le rendement du moteur est accru de façon importante sur l'essentiel de sa plage de puissance.• The efficiency of the engine is significantly increased over most of its power range.
• Le rendement maximal du moteur peut être obtenu sur une plage de régime élargie.• Maximum engine performance can be obtained over a wider speed range.
• Les pertes en pompage sont réduites sur l'essentiel de la plage de puissance du moteur.• Pumping losses are reduced over most of the engine's power range.
• Le régime de ralenti peut être abaissé grâce à la réduction des gaz brûlés résiduels.• The idle speed can be lowered by reducing the residual burnt gas.
• Le moteur peut fonctionner à rendement dégradé permettant un réchauffement rapide du catalyseur utilisé à l'échappement pour traiter les polluants.• The engine can operate at degraded efficiency allowing rapid heating of the catalyst used in the exhaust to treat pollutants.
• Les frottements pistons/cylindres sont réduits grâce au mode de guidage longitudinal du piston.• Piston / cylinder friction is reduced thanks to the piston's longitudinal guide mode.
• Le régime à une moindre incidence sur le frottement.• The regime has a lesser impact on friction.
• Les pièces mécaniques sont particulièrement ramassées et leur vitesse à l'exception du piston est réduite.• The mechanical parts are particularly picked up and their speed except for the piston is reduced.
• L'ovalisation du(des) cylindre(s) par usure est réduite grâce à l'absence de poussée latérale sur le piston dû à l'obliquité de la bielle. En outre, le dispositif selon l'invention prévoit notamment que :• The ovalization of the cylinder (s) by wear is reduced thanks to the absence of lateral thrust on the piston due to the obliquity of the connecting rod. In addition, the device according to the invention provides in particular that:
A basse cylindrée, le cycle moteur exploite une course de détente plus longue que la course utilisée pour compresser les gaz, le diagramme de détente étant alors tronqué plus tard que sur un moteur de même cylindrée tel que défini selon l'art antérieur. A basse cylindrée, le temps nécessaire à la compression des gaz est réduit, ceci limite le temps de confinement des gaz propice au déclenchement d'effets indésirables de détonation.At low displacement, the engine cycle exploits a longer expansion stroke than the stroke used to compress the gases, the expansion diagram then being truncated later than on an engine of the same displacement as defined according to the prior art. At low displacement, the time necessary for the compression of the gases is reduced, this limits the time of confinement of the gases which is favorable for triggering undesirable detonation effects.
Pour atteindre ces résultats, le dispositif selon l'invention comporte selon une première caractéristique :To achieve these results, the device according to the invention comprises, according to a first characteristic:
• Un système permettant de contrôler durant son fonctionnement le rapport volumétrique du moteur. Le système agit par modification de l'origine de la course du piston par rapport au cylindre sans modifier la longueur de ladite course.• A system allowing the volumetric ratio of the engine to be controlled during its operation. The system acts by modifying the origin of the stroke of the piston relative to the cylinder without modifying the length of said stroke.
• Un système de contrôle de la cylindrée effective du moteur. Le système opère par refoulement dans la tubulure d'admission d'une partie des gaz admis dans le cylindre du moteur grâce au concours d'une soupape d'admission additionnelle. En fonctionnement à cylindrée réduite, la fermeture de la soupape d'admission additionnelle peut être retardée de façon significative afin que le piston refoule durant son ascension dans le cylindre les gaz admis en excès et que le début de compression des gaz ait lieu plus tard durant la course ascensionnelle du piston. Selon une variante du dispositif selon l'invention, la soupape d'admission telle que définie selon l'art antérieur peut elle-même être utilisée à cette tâche, ceci en contrôlant ses diagrammes d'ouverture et de fermeture.• A system for monitoring the effective displacement of the engine. The system operates by pushing back into the intake manifold part of the gases admitted into the engine cylinder thanks to the assistance of an additional intake valve. In reduced cylinder operation, the closing of the additional intake valve can be significantly delayed so that the piston expels excess inlet gas during its ascent into the cylinder and the start of gas compression takes place later during the upward stroke of the piston. According to a variant of the device according to the invention, the intake valve as defined according to the prior art can itself be used for this task, this by checking its opening and closing diagrams.
Ce dispositif selon l'invention comporte notamment pour une cylindrée :This device according to the invention comprises in particular for a displacement:
• Un piston muni d'une crémaillère montée solidairement de sa partie inférieure, ladite crémaillère constituant l'une des parties d'un système d'engrènement, et étant maintenue dans un système de guidage qui lui autorise un mouvement de translation longitudinale.• A piston provided with a rack mounted integrally with its lower part, said rack constituting one of the parts of a meshing system, and being held in a guide system which allows it a movement of longitudinal translation.
• Une crémaillère de commande montée dans une cavité ou sur un guide aménagés dans le bloc moteur qui lui autorisent un mouvement de translation longitudinale, la position de ladite crémaillère de commande étant contrôlée par un dispositif de contrôle.• A control rack mounted in a cavity or on a guide arranged in the engine block which allows it a longitudinal translation movement, the position of said control rack being controlled by a control device.
• Une bielle montée libre sur le vilebrequin du moteur qui comporte en sa partie supérieure un engrenage monté libre, ledit engrenage constituant l'élément de transmission du mouvement entre le piston et ladite bielle.• A connecting rod mounted freely on the crankshaft of the engine which comprises in its upper part a free mounted gear, said gear constituting the element for transmitting movement between the piston and said connecting rod.
• Une soupape d'admission additionnelle dont l'arbre à cames qui commande son ouverture/fermeture est asservie à un dispositif qui contrôle son décalage angulaire par rapport au vilebrequin du moteur, ceci permettant de modifier le décalage angulaire du point de fermeture et d'ouverture de ladite soupape par rapport au vilebrequin.• An additional intake valve whose camshaft which controls its opening / closing is slaved to a device which controls its angular offset relative to the engine crankshaft, this making it possible to modify the angular offset of the closing point and opening of said valve relative to the crankshaft.
Selon un mode particulier de réalisation, son fonctionnement nécessite :According to a particular embodiment, its operation requires:
• Des sondes transmettant divers paramètres de fonctionnement du moteur ; • Un ou plusieurs calculateurs ou dispositifs effectuant le traitement desdits paramètres ;• Probes transmitting various engine operating parameters; • One or more computers or devices processing these parameters;
• Un dispositif de contrôle qui permet d'agir sur la position de la crémaillère de commande tenant compte du résultat du traitement des paramètres en provenance desdites sondes ;• A control device which makes it possible to act on the position of the control rack taking account of the result of the processing of the parameters coming from said probes;
• Un dispositif d'asservissement qui permet d'agir sur le décalage angulaire de l'arbre à cames commandant l'ouverture de la soupape d'admission additionnelle tenant compte du résultat du traitement des paramètres en provenance desdites sondes.• A servo device which makes it possible to act on the angular offset of the camshaft controlling the opening of the additional intake valve taking into account the result of the processing of the parameters coming from said probes.
Enfin, le dispositif suivant l'invention comprend :Finally, the device according to the invention comprises:
« Un piston solidaire dans sa partie inférieure d'une crémaillère et qui assure la même fonction que le piston de tout moteur tel que défini selon les règles de l'art antérieur. Seul diffère son mode de transmission mécanique du mouvement au vilebrequin ;"A piston integral in its lower part with a rack and which performs the same function as the piston of any engine as defined according to the rules of the prior art. The only difference is its mode of mechanical transmission of the movement to the crankshaft;
• Une bielle montée libre sur le vilebrequin qui assure la même fonction que la bielle de tout moteur tel que défini selon les règles de l'art antérieur. Seul diffère son mode de liaison mécanique avec le piston ;• A connecting rod mounted freely on the crankshaft which performs the same function as the connecting rod of any engine as defined according to the rules of the prior art. The only difference is its mode of mechanical connection with the piston;
• Un engrenage monté libre en la partie supérieure de la bielle et qui est assujetti au déplacement du piston par l'intermédiaire du système d'engrènement qu'il constitue avec la crémaillère solidaire de la partie inférieure dudit piston d'une part, et la crémaillère de commande montée dans une cavité ou sur un guide, aménagés dans le bloc moteur et maintenue en position par son dispositif de contrôle d'autre part. L'engrenage est prévu pour constituer l'organe de transmission du mouvement entre le piston et la bielle ;• A gear mounted freely in the upper part of the connecting rod and which is subject to the displacement of the piston by means of the meshing system which it constitutes with the rack integral with the lower part of said piston on the one hand, and the control rack mounted in a cavity or on a guide, arranged in the engine block and held in position by its control device on the other hand. The gear is designed to constitute the member for transmitting the movement between the piston and the connecting rod;
• Un dispositif de contrôle qui permet d'agir sur la position de la crémaillère de commande et qui comprend :• A control device which acts on the position of the control rack and which includes:
* Au moins un vérin hydraulique ou tout autre système permettant d'imprimer un mouvement de translation à la crémaillère de commande et rendu solidaire de ladite crémaillère de commande par une quelconque liaison mécanique ;* At least one hydraulic cylinder or any other system making it possible to impart a translational movement to the control rack and made integral with said control rack by any mechanical connection;
* Au moins un vérin hydraulique ou tout autre système permettant de constituer un dispositif qui contrôle le décalage angulaire de l'arbre à cames qui commande l'ouverture de la soupape d'admission additionnelle, ledit vérin hydraulique pouvant agir, selon un mode particulier de réalisation et à titre d'exemple non limitatif, sur la position d'une poulie additionnelle faisant ainsi varier la longueur de courroie ou de chaîne située entre la poulie de l'arbre à cames des soupapes d'admission et d'échappement du moteur tel que défini selon l'art antérieur, et la poulie de l'arbre à cames de la soupape d'admission additionnelle ; • Et un dispositif qui contrôle le décalage angulaire de l'arbre à cames commandant l'ouverture de la soupape d'admission additionnelle et qui n'agit pas nécessairement sur l'arbre à cames commandant les soupapes d'admission et d'échappement du moteur tel que défini selon les règles de l'art antérieur.* At least one hydraulic cylinder or any other system making it possible to constitute a device which controls the angular offset of the camshaft which controls the opening of the additional intake valve, said hydraulic cylinder being able to act, according to a particular mode of embodiment and by way of nonlimiting example, on the position of an additional pulley thus varying the length of belt or chain located between the pulley of the camshaft of the intake and exhaust valves of the engine such as defined according to the prior art, and the pulley of the camshaft of the additional intake valve; • And a device which controls the angular offset of the camshaft controlling the opening of the additional intake valve and which does not necessarily act on the camshaft controlling the intake and exhaust valves of the motor as defined according to the rules of the prior art.
Afin de limiter le coût de production du moteur à cylindrée variable et de minimiser la consommation de puissance du dispositif de contrôle permettant d'agir sur la position de la crémaillère de commande, ce dernier présente selon un mode particulier de réalisation les avantages suivants :In order to limit the production cost of the variable displacement engine and to minimize the power consumption of the control device making it possible to act on the position of the control rack, the latter has, according to a particular embodiment, the following advantages:
• Le déplacement et le maintien permanent à la position souhaitée de la crémaillère de commande sont assurés sans pompe hydraulique ;• The displacement and permanent maintenance of the control rack in the desired position is ensured without hydraulic pump;
• Le contrôle de la position de la crémaillère de commande et donc du volume de chambre d'explosion du moteur peut être obtenu avec un dispositif d'asservissement de très faible puissance ;• Control of the position of the control rack and therefore of the volume of the engine's explosion chamber can be obtained with a very low-power servo device;
• Tout transfert de fluide hydraulique nécessaire à tout changement de position de la crémaillère de commande est assuré sans pompe hydraulique auxiliaire. Selon l'invention, le vérin hydraulique utilisé pour effectuer tout changement de position de ladite crémaillère de commande opère lui-même lesdits transferts en utilisant pour cela les changements permanents du sens de l'effort auquel il est soumis ;• Any transfer of hydraulic fluid required for any change of position of the control rack is ensured without an auxiliary hydraulic pump. According to the invention, the hydraulic cylinder used to effect any change in position of said control rack itself operates said transfers, using for this permanent changes in the direction of the force to which it is subjected;
• La correction de la position de la crémaillère de commande s'effectue automatiquement et de façon permanente durant le fonctionnement du moteur• The position of the control rack is corrected automatically and permanently during engine operation
• Le dispositif est particulièrement robuste et simple à réaliser, il ne fait en outre appel qu'à des techniques de réalisation bien connues de l'art antérieur ;• The device is particularly robust and simple to produce, it also only uses production techniques well known in the prior art;
Le dispositif de contrôle prévoit notamment que :The control system provides in particular that:
• Le contrôle de la position de la crémaillère de commande est suffisamment précis pour permettre un contrôle précis du rapport volumétrique du moteur ;• The control of the control rack position is precise enough to allow precise control of the engine's volumetric ratio;
• La précision de contrôle de la position de la crémaillère de commande est peu altérée durant toute la durée de vie du moteur, et toute fuite de liquide hydraulique est automatiquement compensée de façon permanente.• The precision of controlling the position of the control rack remains little altered throughout the life of the engine, and any leakage of hydraulic fluid is automatically compensated for permanently.
Pour atteindre ces résultats, le dispositif de contrôle qui permet d'agir sur la position de la crémaillère de commande comporte :To achieve these results, the control device which acts on the position of the control rack comprises:
• Un corps de vérin monté fixe par rapport au bloc moteur parallèlement à la crémaillère de commande ; • Un couvercle de vérin monté fixe par rapport au corps de vérin ;• A cylinder body mounted fixed relative to the engine block parallel to the control rack; • A cylinder cover mounted fixed relative to the cylinder body;
• Un piston de vérin, un axe de vérin et un prolongateur d'axe de vérin assemblés avec la crémaillère de commande, qui constituent le système de guidage supérieur de ladite crémaillère de commande du moteur et qui peuvent se déplacer longitudinalement par rapport au corps de vérin ;• A cylinder piston, a cylinder axis and a cylinder axis extender assembled with the control rack, which constitute the upper guide system of said engine control rack and which can move longitudinally relative to the body of the cylinder;
• Une tige de contrôle positionnée parallèlement à l'axe de vérin comportant un épaulement et pouvant se déplacer longitudinalement, ladite tige de contrôle traversant de part en part le couvercle de vérin, le corps de vérin et le piston de vérin grâce à des orifices aménagés dans lesdits couvercle de vérin, corps de vérin et piston de vérin ;• A control rod positioned parallel to the cylinder axis having a shoulder and being able to move longitudinally, said control rod passing right through the cylinder cover, the cylinder body and the cylinder piston by means of orifices in said cylinder cover, cylinder body and cylinder piston;
• Des valves logées dans un conduit aménagé dans la masse du piston de vérin, permettant d'autoriser ou d'interdire la circulation du fluide hydraulique entre les chambres supérieure et inférieure du vérin telles que définies par la position du piston de vérin relative au corps de vérin ;• Valves housed in a duct arranged in the mass of the cylinder piston, allowing the circulation of hydraulic fluid between the upper and lower chambers of the cylinder to be authorized or prohibited as defined by the position of the cylinder piston relative to the body cylinder;
• Un clapet anti-retour logé dans un conduit d'arrivée de fluide hydraulique dont l'orifice débouche dans la partie centrale du corps de vérin ledit clapet antiretour autorisant l'entrée du fluide hydraulique dans le corps de vérin, mais en interdisant la sortie ;• A non-return valve housed in a hydraulic fluid inlet duct, the orifice of which opens into the central part of the cylinder body, said non-return valve allowing the entry of hydraulic fluid into the cylinder body, but preventing the outlet ;
• Des ressorts assurant le maintien en contact sur leur siège des valves et clapets ;• Springs ensuring the maintenance in contact on their seat of the valves and valves;
• Des dispositifs d'étanchéité pouvant être constitués, selon un mode particulier de réalisation selon l'invention, de joints toriques en caoutchouc. Selon un mode particulier de réalisation, son fonctionnement nécessite un ou des moyens d'asservissement de faible puissance permettant d'agir sur la position longitudinale de la tige de contrôle par rapport au corps de vérin, tenant compte des impératifs de fonctionnement du moteur. Le dispositif de contrôle permettant d'agir sur la position de la crémaillère de commande comprend :• Sealing devices which can be made, according to a particular embodiment according to the invention, of rubber O-rings. According to a particular embodiment, its operation requires one or more low-power servo means making it possible to act on the longitudinal position of the control rod relative to the jack body, taking account of the operating requirements of the engine. The control device making it possible to act on the position of the control rack comprises:
• Un conduit longitudinal excentré qui est aménagé dans la masse du piston de vérin et qui relie les surfaces circulaires inférieure et supérieure dudit piston de vérin. Le conduit est réalisé de telle sorte qu'il constitue un logement pour les deux valves permettant d'autoriser ou d'interdire la circulation du fluide hydraulique. Le conduit est d'un diamètre supérieur à celui des valves afin de permettre l'écoulement du fluide au travers dudit conduit lorsque lesdites valves sont ouvertes ;• An eccentric longitudinal duct which is arranged in the mass of the cylinder piston and which connects the lower and upper circular surfaces of said cylinder piston. The duct is designed so that it constitutes a housing for the two valves making it possible to authorize or prohibit the circulation of the hydraulic fluid. The conduit is of a diameter greater than that of the valves in order to allow the flow of the fluid through said conduit when said valves are open;
Un conduit longitudinal excentré qui est aménagé dans la masse du piston de vérin et qui assure le guidage longitudinal de la tige de contrôle ; • Un piston de vérin qui comporte une cavité sur sa surface cylindrique en regard avec l'orifice d'arrivée de fluide hydraulique débouchant dans la partie centrale du corps de vérin. La cavité est d'une hauteur au moins équivalente à la course maximale du piston de vérin et est reliée au conduit longitudinal excentré aménagé dans la masse du piston de vérin ;An eccentric longitudinal duct which is arranged in the mass of the cylinder piston and which ensures the longitudinal guidance of the control rod; • A cylinder piston which has a cavity on its cylindrical surface opposite the hydraulic fluid inlet orifice opening into the central part of the cylinder body. The cavity has a height at least equivalent to the maximum stroke of the cylinder piston and is connected to the eccentric longitudinal duct arranged in the mass of the cylinder piston;
• Des valves qui permettent d'autoriser ou d'interdire la circulation du fluide hydraulique entre les chambres supérieure et inférieure du vérin telles que définies par la position du piston de vérin relative au corps de vérin. Les valves sont constituées de bagues pouvant coulisser autour de la tige de contrôle. Le diamètre intérieur des valves est inférieur au diamètre de l'épaulement de la tige de contrôle. Lorsque les valves ne sont pas maintenues ouvertes par l'épaulement de la tige de contrôle, elles sont maintenues sur leur siège par des ressorts ;• Valves which allow the circulation of hydraulic fluid between the upper and lower chambers of the cylinder to be authorized or prohibited as defined by the position of the cylinder piston relative to the cylinder body. The valves consist of rings which can slide around the control rod. The inside diameter of the valves is less than the diameter of the shoulder of the control rod. When the valves are not kept open by the shoulder of the control rod, they are held in their seats by springs;
• Un épaulement de la tige de contrôle qui assure le centrage de ladite tige de contrôle dans le conduit longitudinal excentré aménagé dans la masse du piston de vérin. L'épaulement permet de déplacer l'une ou l'autre des valves permettant d'autoriser ou d'interdire la circulation du fluide hydraulique entre les chambres supérieure et inférieure du vérin. L'épaulement est pourvu de rainures ou de gorges autorisant la circulation du fluide au travers du conduit ;• A shoulder of the control rod which ensures the centering of said control rod in the eccentric longitudinal duct arranged in the mass of the cylinder piston. The shoulder makes it possible to move one or the other of the valves making it possible to authorize or prohibit the circulation of the hydraulic fluid between the upper and lower chambers of the jack. The shoulder is provided with grooves or grooves allowing the circulation of the fluid through the conduit;
• Un clapet anti-retour qui est logé dans le conduit d'arrivée de fluide hydraulique dont l'orifice débouche dans la partie centrale du corps de vérin et qui peut être constitué, selon un mode particulier de réalisation, d'une bille maintenue sur une portée par un ressort et obturant un orifice ;• A non-return valve which is housed in the hydraulic fluid inlet pipe, the orifice of which opens into the central part of the jack body and which may consist, according to a particular embodiment, of a ball held on carried by a spring and closing a hole;
• Un conduit d'arrivée de fluide hydraulique dont l'orifice débouche dans la partie centrale du corps de vérin et qui peut être connecté, selon un mode particulier de réalisation, au circuit hydraulique sous pression assurant la lubrification du moteur à cylindrée variable.• A hydraulic fluid inlet conduit whose orifice opens into the central part of the cylinder body and which can be connected, according to a particular embodiment, to the pressurized hydraulic circuit ensuring the lubrication of the variable displacement engine.
Le dispositif suivant l'invention permettant de faire varier la cylindrée et/ou le rapport volumétrique effectifs d'un moteur à pistons pendant son fonctionnement, comprend:The device according to the invention making it possible to vary the effective displacement and / or the volumetric ratio of a piston engine during its operation, comprises:
• Un premier dispositif permettant de contrôler le rapport volumétrique du moteur en agissant par modification de l'origine de la course du piston par rapport au cylindre sans modifier la longueur de ladite course ;• A first device making it possible to control the volumetric ratio of the engine by acting by modifying the origin of the stroke of the piston relative to the cylinder without modifying the length of said stroke;
• Et un second dispositif permettant de contrôler la cylindrée effective du moteur en opérant par refoulement des gaz admis en excès dans le cylindre du moteur dans la tubulure d'admission et par ajustement de la longueur de la course ascensionnelle du piston utilisée pour compresser les gaz.• And a second device making it possible to control the effective displacement of the engine by operating by repressing the gases admitted in excess into the cylinder of the engine in the intake manifold and by adjusting the length of the upward stroke of the piston used to compress the gases .
Le dispositif suivant la présente invention comprend un premier dispositif permettant de contrôler le rapport volumétrique du moteur constitué d'un système d'engrènement qui comprend : • Une crémaillère solidaire de la partie inférieure du piston et qui est maintenue dans un système de guidage autorisant un mouvement de translation longitudinale à ladite crémaillère ;The device according to the present invention comprises a first device making it possible to control the volumetric ratio of the engine constituted by a gear system which comprises: • A rack integral with the lower part of the piston and which is held in a guide system allowing a longitudinal translational movement to said rack;
• Une crémaillère de commande guidée en translation longitudinale dans le bloc moteur ;• A control rack guided in longitudinal translation in the engine block;
• Un dispositif permettant de contrôler la position de la crémaillère de commande ;• A device for controlling the position of the control rack;
• Et un engrenage monté libre sur une bielle également libre sur un vilebrequin de manière que l'engrenage soit disposé entre les deux crémaillères pour constituer l'élément de transmission du mouvement entre le piston et la bielle.• And a gear mounted freely on a connecting rod also free on a crankshaft so that the gear is disposed between the two racks to constitute the element for transmitting movement between the piston and the connecting rod.
Le dispositif suivant la présente invention comprend un second dispositif permettant de contrôler la cylindrée effective du moteur constitué d'une soupape d'admission additionnelle et d'un dispositif qui contrôle son ouverture/fermeture et qui permet de modifier le décalage angulaire du point de fermeture et d'ouverture de ladite soupape par rapport au vilebrequin.The device according to the present invention comprises a second device for controlling the effective displacement of the engine consisting of an additional intake valve and a device which controls its opening / closing and which makes it possible to modify the angular offset of the closing point. and opening said valve relative to the crankshaft.
Le dispositif suivant la présente invention comprend un second dispositif permettant de contrôler la cylindrée effective du moteur sans soupape d'admission additionnelle constitué d'un dispositif qui contrôle l'ouverture et la fermeture de la soupape d'admission connue en soi et qui permet de modifier le décalage angulaire du point de fermeture et d'ouverture de ladite soupape par rapport au vilebrequin. Le dispositif suivant la présente invention comprend un dispositif contrôlant l'ouverture et la fermeture de la soupape d'admission additionnelle qui est un arbre à cames asservi à un dispositif qui contrôle son décalage angulaire par rapport au vilebrequin du moteur. Le dispositif suivant la présente invention comprend un dispositif contrôlant l'ouverture et la fermeture de la soupape d'admission connue en soi qui est constitué d'un arbre à cames additionnel asservi à un dispositif qui contrôle son décalage angulaire par rapport au vilebrequin du moteur, ledit arbre à cames additionnel actionnant ladite soupape par l'intermédiaire d'une liaison mécanique en complément du mouvement imprimé à ladite soupape par son arbre à cames.The device according to the present invention comprises a second device making it possible to control the effective displacement of the engine without an additional intake valve consisting of a device which controls the opening and closing of the intake valve known per se and which makes it possible to modify the angular offset of the point of closure and opening of said valve relative to the crankshaft. The device according to the present invention comprises a device controlling the opening and closing of the additional intake valve which is a camshaft controlled by a device which controls its angular offset relative to the crankshaft of the engine. The device according to the present invention comprises a device controlling the opening and closing of the intake valve known per se which consists of an additional camshaft controlled by a device which controls its angular offset relative to the engine crankshaft , said additional camshaft actuating said valve via a mechanical connection in addition to the movement imparted to said valve by its camshaft.
Le dispositif suivant la présente invention comprend un dispositif contrôlant le décalage angulaire de l'arbre à cames commandant l'ouverture de la soupape d'admission additionnelle qui est constitué d'une poulie intermédiaire dont la position définit la longueur de courroie de distribution ou de chaîne comprise entre la poulie de l'arbre à cames des soupapes d'admission et d'échappement du moteur et la poulie de l'arbre à cames qui commande l'ouverture de la soupape d'admission additionnelle. Le dispositif suivant la présente invention comprend un dispositif contrôlant la position de la crémaillère de commande qui est constitué d'un vérin hydraulique qui agit sur ladite crémaillère par l'intermédiaire d'une liaison mécanique. Le dispositif suivant la présente invention comprend un dispositif qui contrôle la position de la poulie intermédiaire constitué d'un vérin hydraulique.The device according to the present invention comprises a device controlling the angular offset of the camshaft controlling the opening of the additional intake valve which consists of an intermediate pulley whose position defines the length of the timing belt or chain between the camshaft pulley of the engine intake and exhaust valves and the camshaft pulley which controls the opening of the additional intake valve. The device according to the present invention comprises a device controlling the position of the control rack which consists of a hydraulic cylinder which acts on said rack via a mechanical connection. The device according to the present invention comprises a device which controls the position of the intermediate pulley consisting of a hydraulic cylinder.
Le dispositif suivant la présente invention comprend un engrenage présentant un profil tronqué de manière à conserver uniquement les dentures utiles à la transmission du mouvement entre le piston et la bielle.The device according to the present invention comprises a gear having a truncated profile so as to retain only the teeth useful for the transmission of movement between the piston and the connecting rod.
Le dispositif suivant la présente invention comprend des surfaces de roulement qui sont aménagées respectivement sur l'engrenage et les crémaillères assurant le centrage permanent dudit engrenage entre lesdites crémaillères, tandis que le point de contact entre lesdites surfaces de roulement est en permanence positionné au niveau de la primitive de l'engrenage.The device according to the present invention comprises rolling surfaces which are arranged respectively on the gear and the racks ensuring permanent centering of said gear between said racks, while the point of contact between said rolling surfaces is permanently positioned at the primitive of the gear.
Le dispositif suivant la présente invention comprend un piston dont la partie cylindrique est d'une hauteur suffisante pour loger des segments, mais ne comporte pas de jupe assurant son guidage longitudinal.The device according to the present invention comprises a piston whose cylindrical part is of a height sufficient to accommodate segments, but does not include a skirt ensuring its longitudinal guidance.
Le dispositif permettant de faire varier la cylindrée et/ou le rapport volumétrique effectifs d'un moteur à pistons comprend un dispositif contrôlant la position de la crémaillère de commande qui comporte :The device making it possible to vary the effective displacement and / or the volumetric ratio of a piston engine comprises a device controlling the position of the control rack which comprises:
• Un vérin hydraulique comportant des moyens pour le prolongement de son axe permettant de conserver un volume de fluide déplacé en fonction de la course du piston de vérin qui est identique pour chacune des chambres supérieure et inférieure dudit vérin.• A hydraulic cylinder comprising means for extending its axis making it possible to maintain a volume of fluid displaced as a function of the stroke of the cylinder piston which is identical for each of the upper and lower chambers of said cylinder.
• Des moyens de contrôle qui permettent de déplacer vers une position déterminée ou de maintenir dans une position déterminée l'axe du vérin par rapport au corps du vérin. Le dispositif suivant la présente invention comprend un dispositif de contrôle qui comporte :• Control means which make it possible to move towards a determined position or to maintain in a determined position the axis of the jack with respect to the body of the jack. The device according to the present invention comprises a control device which comprises:
• Un corps de vérin monté fixe par rapport au bloc moteur parallèlement à la crémaillère de commande, un couvercle de vérin monté fixe par rapport au corps de vérin, un piston de vérin, un axe de vérin et un prolongateur d'axe de vérin assemblés avec la crémaillère de commande, qui constituent le système de guidage supérieur de ladite crémaillère de commande et qui peuvent se déplacer longitudinalement par rapport au corps de vérin ;• An actuator body mounted fixed relative to the engine block parallel to the control rack, an actuator cover mounted fixed relative to the actuator body, an actuator piston, an actuator axis and an actuator axis extension assembly with the control rack, which constitute the upper guide system of said control rack and which can move longitudinally relative to the cylinder body;
• Des moyens de contrôle qui sont constitués d'une tige de contrôle comportant un épaulement et pouvant se déplacer longitudinalement, ladite tige de contrôle étant positionnée parallèlement à l'axe de vérin et traversant de part en part le couvercle de vérin, le corps de vérin et le piston de vérin grâce à des orifices aménagés dans lesdits couvercle de vérin, corps de vérin et piston de vérin, de valves logées dans un conduit placé longitudinalement et de façon excentrée aménagé dans la masse du piston de vérin, lesdites valves permettant d'autoriser ou d'interdire la circulation du fluide hydraulique entre les chambres supérieure et inférieure du vérin telles que définies par la position du piston de vérin relative au corps de vérin, lesdites valves étant constituées de bagues qui peuvent coulisser autour de la tige de contrôle, et leur diamètre intérieur étant inférieur au diamètre de l'épaulement de la tige de contrôle de telle sorte qu'il soit possible de les maintenir ouvertes grâce audit épaulement de ladite tige de contrôle, lorsque lesdites valves ne sont pas maintenues ouvertes par ledit épaulement de ladite tige de contrôle, elles sont maintenues sur leur siège par des ressorts, et d'un clapet anti-retour logé dans un conduit d'arrivée de fluide hydraulique dont l'orifice débouche dans la partie centrale du corps de vérin, ledit clapet anti-retour autorisant l'entrée du fluide hydraulique dans le corps de vérin, mais en interdisant la sortie.• Control means which consist of a control rod having a shoulder and which can move longitudinally, said control rod being positioned parallel to the cylinder axis and passing right through the cylinder cover, the body of cylinder and the cylinder piston by means of orifices arranged in said cylinder cover, cylinder body and piston cylinder, valves housed in a conduit placed longitudinally and eccentrically arranged in the mass of the cylinder piston, said valves making it possible to authorize or prohibit the circulation of hydraulic fluid between the upper and lower chambers of the cylinder as defined by the position of the jack piston relative to the jack body, said valves being made up of rings which can slide around the control rod, and their internal diameter being less than the diameter of the shoulder of the control rod so that 'it is possible to keep them open thanks to said shoulder of said control rod, when said valves are not kept open by said shoulder of said control rod, they are held in their seat by springs, and a check valve -return housed in a hydraulic fluid inlet conduit whose orifice opens into the central part of the cylinder body , said non-return valve allowing the entry of hydraulic fluid into the cylinder body, but preventing the outlet.
Le dispositif suivant la présente invention comprend un dispositif de contrôle qui comporte un piston de vérin pourvu d'une cavité sur sa surface cylindrique en regard avec l'orifice du conduit d'arrivée de fluide hydraulique débouchant dans la partie centrale du corps de vérin, ladite cavité étant d'une hauteur au moins équivalente à la course maximale dudit piston de vérin et étant reliée au conduit placé longitudinalement et de façon excentrée aménagé dans la masse dudit piston de vérin reliant les surfaces circulaires inférieure et supérieure dudit piston de vérin, par un canal de liaison. Le dispositif suivant la présente invention comprend un dispositif de contrôle qui comprend un clapet anti-retour constitué d'une bille maintenue sur une portée par un ressort et obturant un orifice.The device according to the present invention comprises a control device which comprises a jack piston provided with a cavity on its cylindrical surface facing the orifice of the hydraulic fluid inlet pipe opening into the central part of the jack body, said cavity being of a height at least equivalent to the maximum stroke of said cylinder piston and being connected to the conduit placed longitudinally and eccentrically arranged in the mass of said cylinder piston connecting the lower and upper circular surfaces of said cylinder piston a connecting channel. The device according to the present invention comprises a control device which comprises a non-return valve consisting of a ball held on a bearing by a spring and closing an orifice.
Le dispositif suivant la présente invention comprend un dispositif de contrôle qui comprend un conduit d'arrivée de fluide hydraulique dont l'un des orifices débouche dans la partie centrale du corps de vérin et qui est connecté au circuit hydraulique sous pression assurant la lubrification du moteur à cylindrée variable. Le dispositif suivant la présente invention comprend un dispositif de contrôle qui comporte des éléments d'étanchéité constitués de joints toriques en caoutchouc.The device according to the present invention comprises a control device which comprises a hydraulic fluid inlet pipe, one of the orifices of which opens into the central part of the jack body and which is connected to the pressurized hydraulic circuit ensuring the lubrication of the engine. with variable displacement. The device according to the present invention comprises a control device which comprises sealing elements made up of rubber O-rings.
Le dispositif suivant la présente invention comprend un dispositif de contrôle dont l'épaulement assure le centrage de la tige de contrôle dans le conduit placé longitudinalement et de façon excentrée aménagé dans la masse dudit piston de vérin, ledit épaulement comportant des rainures ou des gorges autorisant la circulation du fluide hydraulique au travers dudit conduit.The device according to the present invention comprises a control device whose shoulder ensures the centering of the control rod in the conduit placed longitudinally and eccentrically arranged in the mass of said cylinder piston, said shoulder comprising grooves or grooves allowing the circulation of hydraulic fluid through said conduit.
D'autres caractéristiques et avantages de la présente invention apparaîtront mieux à la lecture de la description qui va suivre, faite en relation avec les dessins annexés sur lesquels :Other characteristics and advantages of the present invention will appear better on reading the description which follows, made in relation to the appended drawings in which:
La figure 1 est une vue de face en coupe schématique du dispositif selon l'invention. La figure 2 est une vue de droite en coupe schématique selon la ligne A-A de la figure 1 du dispositif selon l'invention. La figure 3 est une vue en coupe schématique du dispositif de commande d'ouverture de la soupape d'admission telle que définie selon l'art antérieur, qui, selon une variante du dispositif selon l'invention, peut être utilisée pour contrôler la cylindrée du moteur. La figure 4 est une vue en perspective mettant en évidence la disposition des principaux éléments qui constituent le dispositif selon l'invention.Figure 1 is a schematic sectional front view of the device according to the invention. Figure 2 is a schematic sectional right view along line AA of Figure 1 of the device according to the invention. Figure 3 is a schematic sectional view of the opening control device of the intake valve as defined according to the prior art, which, according to a variant of the device according to the invention, can be used to control the displacement of the motor. Figure 4 is a perspective view showing the arrangement of the main elements which constitute the device according to the invention.
La figure 5 est une vue d'ensemble mettant en évidence le positionnement du dispositif de contrôle selon l'invention qui permet d'agir sur la position de la crémaillère de commande par rapport aux autres éléments constituants le moteur à cylindrée variable, et la représentation d'une variante de réalisation du système d'engrènement.FIG. 5 is an overall view showing the positioning of the control device according to the invention which makes it possible to act on the position of the control rack relative to the other elements constituting the variable displacement motor, and the representation of an alternative embodiment of the meshing system.
La figure 6 est une vue de face en coupe schématique du dispositif de contrôle de la crémaillère de commande.Figure 6 is a schematic sectional front view of the control rack control device.
La figure 7 est une vue en perspective mettant en évidence la disposition et l'apparence des principaux éléments qui constituent le dispositif de contrôle de la position de la crémaillère de commande selon l'invention.Figure 7 is a perspective view showing the arrangement and appearance of the main elements which constitute the device for controlling the position of the control rack according to the invention.
Comme on peut le voir sur les figures, le dispositif selon l'invention vient s'insérer dans un environnement bien connu de l'art antérieur : les moteurs à pistons.As can be seen in the figures, the device according to the invention is inserted in an environment well known from the prior art: piston engines.
En figures 1 à 4 on a montré un moteur comprenant un piston 1 , un cylindre 2, des soupapes 3, 4, 15 ou 22, un bloc moteur 5, une culasse 6, un vilebrequin 7, une bougie d'allumage 8 et une chambre d'explosion 9.In Figures 1 to 4 there is shown an engine comprising a piston 1, a cylinder 2, valves 3, 4, 15 or 22, an engine block 5, a cylinder head 6, a crankshaft 7, a spark plug 8 and a explosion chamber 9.
La fonction de ces organes est, selon l'invention, inchangée eut égard à l'état antérieur de la technique.The function of these organs is, according to the invention, unchanged having regard to the prior art.
Le dispositif selon l'invention comporte essentiellement une crémaillère 10 solidaire de la partie inférieure du piston 1 , une crémaillère de commande 11 montée dans une cavité ou sur un guide, aménagés dans le bloc moteur 5, un dispositif 12 qui contrôle la position de ladite crémaillère de commande par rapport au bloc moteur. Il comporte également une bielle 13 montée libre sur le vilebrequin 7 du moteur et qui comprend dans sa partie supérieure un engrenage 14 monté libre.The device according to the invention essentially comprises a rack 10 integral with the lower part of the piston 1, a control rack 11 mounted in a cavity or on a guide, arranged in the engine block 5, a device 12 which controls the position of said control rack relative to the engine block. It also includes a connecting rod 13 mounted free on the crankshaft 7 of the engine and which comprises in its upper part a gear 14 mounted free.
On remarque que la partie cylindrique du piston 1 est d'une hauteur suffisante pour loger des segments, mais ne comporte pas de jupe assurant son guidage longitudinal (figure 5). On note que suivant un mode particulier de réalisation, l'engrenage 14 peut présenter un profil tronqué de manière à conserver uniquement les dentures utiles à la transmission du mouvement entre le piston 1 et la bielle 13 (figure 5). On constate que des surfaces de roulement sont aménagées respectivement sur l'engrenage 14 et les crémaillères 10, 11 assurant le centrage permanent dudit engrenage entre lesdites crémaillères, tandis que le point de contact entre lesdites surfaces de roulement est en permanence positionné au niveau de la primitive de l'engrenage 14 (figure 5). Le dispositif selon l'invention comporte en outre une soupape d'admission additionnelle 15 dont l'arbre à cames 16 commandant son ouverture est asservie à un dispositif 17 qui contrôle son décalage angulaire par rapport au vilebrequin 7 du moteur. Selon une variante, la fonction remplie par la soupape d'admission additionnelle 15 peut être assumée par la soupape d'admission 22 telle que définie selon l'art antérieur comme montré en figure 3.Note that the cylindrical part of the piston 1 is of sufficient height to accommodate the segments, but does not have a skirt ensuring its longitudinal guidance (Figure 5). It is noted that according to a particular embodiment, the gear 14 may have a truncated profile so as to retain only the teeth useful for the transmission of movement between the piston 1 and the connecting rod 13 (Figure 5). It can be seen that the rolling surfaces are arranged respectively on the gear 14 and the racks 10, 11 ensuring the permanent centering of the said gear between the said racks, while the point of contact between the said rolling surfaces is permanently positioned at the level of the primitive of the gear 14 (Figure 5). The device according to the invention further comprises an additional intake valve 15 whose camshaft 16 controlling its opening is controlled by a device 17 which controls its angular offset relative to the crankshaft 7 of the engine. According to a variant, the function fulfilled by the additional intake valve 15 can be assumed by the intake valve 22 as defined according to the prior art as shown in FIG. 3.
Un dispositif additionnel permet alors de modifier le décalage angulaire du point de fermeture et d'ouverture de la soupape 22 par rapport au vilebrequin 7. Le dispositif additionnel peut comporter un arbre à cames additionnel 21 asservi à un dispositif non représenté qui contrôle son décalage angulaire par rapport au vilebrequin du moteur. L'arbre à cames additionnel 21 actionne la soupape d'admission 22 par l'intermédiaire d'une liaison mécanique 23 en complément du mouvement imprimé à ladite soupape par son arbre à cames 24 tel que défini selon l'art antérieur.An additional device then makes it possible to modify the angular offset of the point of closure and opening of the valve 22 relative to the crankshaft 7. The additional device may include an additional camshaft 21 slaved to a device not shown which controls its angular offset relative to the engine crankshaft. The additional camshaft 21 actuates the inlet valve 22 via a mechanical connection 23 in addition to the movement imparted to said valve by its camshaft 24 as defined according to the prior art.
Le dispositif selon l'invention peut également comporter divers accessoires non représentés tels que des sondes transmettant divers paramètres de fonctionnement du moteur, un ou plusieurs calculateurs ou dispositifs effectuant le traitement des informations en provenance desdites sondes et un système permettant d'assujettir le dispositif 12 qui contrôle la position de la crémaillère de commande 11 par rapport au bloc moteur 5 et le dispositif 17 qui contrôle le décalage angulaire de la soupape d'admission additionnelle 15 au résultat du traitement des informations en provenance desdites sondes.The device according to the invention may also include various accessories, not shown, such as probes transmitting various operating parameters of the engine, one or more computers or devices processing the information coming from said probes and a system allowing the device to be subjected 12 which controls the position of the control rack 11 with respect to the engine block 5 and the device 17 which controls the angular offset of the additional intake valve 15 as a result of the processing of the information from said probes.
Le fonctionnement du dispositif permettant de faire varier la cylindrée et/ou le rapport volumétrique effectifs d'un moteur à pistons est le suivant : La modification de la cylindrée effective du moteur en conservant un rapport volumétrique adéquat s'opère par l'action conjuguée des dispositifs permettant de contrôler durant son fonctionnement le rapport volumétrique du moteur d'une part et la cylindrée effective dudit moteur d'autre part. Le contrôle du rapport volumétrique du moteur s'opère par contrôle de la position d'origine de la course du piston 1 par rapport au cylindre 2, sans modifier la longueur de ladite course.The operation of the device making it possible to vary the effective displacement and / or the volumetric ratio of a piston engine is as follows: The modification of the effective displacement of the engine while maintaining an adequate volumetric ratio is effected by the combined action of the devices making it possible to control, during its operation, the volumetric ratio of the engine on the one hand and the effective displacement of said engine on the other. The volumetric ratio of the engine is checked by checking the original position of the stroke of the piston 1 relative to the cylinder 2, without modifying the length of said stroke.
Le contrôle de la cylindrée effective du moteur s'opère comme suit : Le dispositif de contrôle 12 de la crémaillère 11 reçoit l'ordre de déplacer ladite crémaillère de commande 11. Cet ordre est matérialisé, par exemple, par l'introduction dans un vérin hydraulique 25 d'un certain volume d'huile sous pression en provenance d'une pompe (non représentée).The effective displacement of the engine is checked as follows: The control device 12 of the rack 11 receives the order to move said control rack 11. This order is materialized, for example, by the introduction into a hydraulic cylinder 25 of a certain volume of pressurized oil from of a pump (not shown).
Le volume introduit est au préalable calculé par le ou les dispositifs (non représentés) effectuant le traitement des informations en provenance de sondes paramétriques du moteur (non représentées). L'action du dispositif de contrôle 12 sur la crémaillère de commande 11 par l'intermédiaire d'une liaison mécanique 20 a pour effet d'imprimer à ladite crémaillère de commande 11 un mouvement de translation parallèle à son axe longitudinal.The volume introduced is previously calculated by the device (s) (not shown) processing the information coming from parametric engine probes (not shown). The action of the control device 12 on the control rack 11 by means of a mechanical link 20 has the effect of imparting to said control rack 11 a translational movement parallel to its longitudinal axis.
La crémaillère de commande 11 constitue un système d'engrènement avec l'engrenage 14 monté libre dans la partie supérieure de la bielle 13 et la crémaillère 10 solidaire de la partie inférieure du piston 1. Le déplacement de la crémaillère de commande 11 implique une modification du point d'origine de la course du piston 1 par rapport au cylindre 2. La modification du point d'origine de la course a pour effet de modifier le volume de la chambre d'explosion 9, la longueur de ladite course étant inchangée, le rapport volumétrique du moteur est modifié.The control rack 11 constitutes a meshing system with the gear 14 mounted freely in the upper part of the connecting rod 13 and the rack 10 secured to the lower part of the piston 1. The displacement of the control rack 11 implies a modification the point of origin of the stroke of the piston 1 relative to the cylinder 2. The modification of the point of origin of the stroke has the effect of modifying the volume of the explosion chamber 9, the length of said stroke being unchanged, the engine's volumetric ratio is changed.
Le contrôle de la cylindrée effective du moteur s'opère également comme suit : Le dispositif 17 qui contrôle le décalage angulaire de l'arbre à cames 16 qui commande l'ouverture de la soupape d'admission additionnelle 15 reçoit l'ordre de retarder ou d'avancer la fermeture de ladite soupape d'admission additionnelle 15. Cet ordre est matérialisé selon un exemple particulier de réalisation du dispositif de contrôle 17 par l'introduction dans un vérin hydraulique 26 d'un certain volume d'huile sous pression en provenance d'une pompe (non représentée).The control of the effective displacement of the engine also operates as follows: The device 17 which controls the angular offset of the camshaft 16 which controls the opening of the additional intake valve 15 receives the order to delay or to advance the closing of said additional intake valve 15. This order is materialized according to a particular embodiment of the control device 17 by the introduction into a hydraulic cylinder 26 of a certain volume of pressurized oil from of a pump (not shown).
Le volume introduit est préalablement calculé par le ou les dispositifs non représentés effectuant le traitement des informations en provenance de sondes paramétriques du moteur (non représentées).The volume introduced is calculated beforehand by the device (s) not shown performing the processing of information coming from parametric engine probes (not shown).
Le vérin hydraulique 26 peut agir sur la position d'une poulie intermédiaire 18 qui modifie la longueur de courroie de distribution 27 ou de chaîne comprise entre la poulie 28 de l'arbre à cames 24 des soupapes d'admission 3 et d'échappement 4 du moteur, et la poulie 29 de l'arbre à cames 16 qui commande l'ouverture de la soupape d'admission additionnelle 15.The hydraulic cylinder 26 can act on the position of an intermediate pulley 18 which modifies the length of timing belt 27 or chain between the pulley 28 of the camshaft 24 of the intake 3 and exhaust 4 valves of the engine, and the pulley 29 of the camshaft 16 which controls the opening of the additional intake valve 15.
Selon l'invention, un retard calculé à la fermeture de la soupape d'admission additionnelle 15 a pour effet de permettre au piston 1 de refouler dans la tubulure d'admission 19 une certaine quantité de gaz frais admis en excès d'une part, et de n'exploiter qu'une partie de la longueur de la course du piston 1 pour compresser les gaz d'autre part. Selon une caractéristique de l'invention, sur moteur à cylindres multiples, les gaz frais refoulés dans la tubulure d'admission 19 peuvent être re-aspirés par un cylindre voisin en phase d'admission.According to the invention, a delay calculated on closing the additional intake valve 15 has the effect of allowing the piston 1 to discharge into the intake manifold 19 a certain quantity of fresh gas admitted in excess on the one hand, and to exploit only part of the length of the stroke of the piston 1 to compress the gases on the other hand. According to a characteristic of the invention, on multiple cylinder engine, the fresh gases discharged into the intake manifold 19 can be re-aspirated by a neighboring cylinder during the intake phase.
Le dispositif selon l'invention prévoit que le rapport entre le volume de la chambre d'explosion défini par le système qui contrôle le rapport volumétrique et la longueur de la course du piston utilisée pour compresser les gaz frais peut ne pas rester constant, ceci afin de permettre au moteur de travailler selon le rapport volumétrique effectif le plus élevé possible autorisé par les conditions de fonctionnement dudit moteur.The device according to the invention provides that the ratio between the volume of the explosion chamber defined by the system which controls the volumetric ratio and the length of the piston stroke used to compress the fresh gases may not remain constant, in order to to allow the engine to work according to the highest effective volumetric ratio possible authorized by the operating conditions of said engine.
En fonctionnement, la cylindrée effective du moteur ainsi que son rapport volumétrique effectif sont assujettis en permanence aux impératifs d'optimisation du rendement du moteur. On a montré en figures 5 à 7 une variante de réalisation du dispositif 12 qui contrôle la position de la crémaillère de commande 11 par rapport au bloc moteur 5.In operation, the effective displacement of the engine as well as its effective volumetric ratio are permanently subject to the imperatives of optimization of the engine efficiency. FIGS. 5 to 7 show an alternative embodiment of the device 12 which controls the position of the control rack 11 relative to the engine block 5.
Le dispositif de contrôle 12 comporte essentiellement un corps de vérin 45 monté fixe par rapport au bloc moteur 5 parallèlement à la crémaillère de commande 11 , un couvercle de vérin 46 monté fixe par rapport au corps de vérin 45, un piston de vérin 47, un axe de vérin 48 et un prolongateur d'axe de vérin 49 assemblés avec la crémaillère de commande 11 , qui constituent le système de guidage supérieur de ladite crémaillère de commande 11 et qui peuvent se déplacer longitudinalement par rapport au corps de vérin 45.The control device 12 essentially comprises a jack body 45 mounted fixed relative to the engine block 5 parallel to the control rack 11, a jack cover 46 mounted fixed relative to the jack body 45, a jack piston 47, a cylinder axis 48 and a cylinder axis extension 49 assembled with the control rack 11, which constitute the upper guide system of said control rack 11 and which can move longitudinally relative to the cylinder body 45.
En figures 6 et 7 on a montré le dispositif 12 comportant des moyens de contrôle 42 qui sont constitués d'une tige de contrôle 50 munie d'un épaulement 51 et pouvant se déplacer longitudinalement.In Figures 6 and 7 there is shown the device 12 comprising control means 42 which consist of a control rod 50 provided with a shoulder 51 and which can move longitudinally.
La tige de contrôle 50 est positionnée parallèlement à l'axe de vérin 48 et traverse de part en part le couvercle de vérin 46, le corps de vérin 45 et le piston de vérin 47 grâce à des conduits aménagés dans lesdits couvercles de vérin 46, corps de vérin 45 et piston de vérin 47.The control rod 50 is positioned parallel to the actuator axis 48 and passes right through the actuator cover 46, the actuator body 45 and the actuator piston 47 by means of conduits arranged in said actuator covers 46, cylinder body 45 and cylinder piston 47.
Les moyens de contrôle 42 sont également constitués de valves 52, 53 logées dans un conduit 54 aménagé dans la masse du piston de vérin 47.The control means 42 also consist of valves 52, 53 housed in a conduit 54 arranged in the mass of the cylinder piston 47.
Les valves 52, 53 permettent d'autoriser ou d'interdire la circulation du fluide hydraulique entre les chambres supérieure 40 et inférieure 41 du vérin telles que définies par la position du piston de vérin 47 relative au corps de vérin 45. Les valves 52, 53 sont constituées de bagues pouvant coulisser autour de la tige de contrôle 50. Le diamètre intérieur des bagues est prévu inférieur au diamètre de l'épaulement 51 de la tige de contrôle 50 de telle sorte qu'il soit possible de les maintenir ouvertes grâce audit l'épaulement 51. Lorsque les valves 52, 53 ne sont pas maintenues ouvertes par l'épaulement 51 , elles sont maintenues sur leur siège par des ressorts 55, 56. Les moyens de contrôle 42 sont constitués d'un clapet anti-retour 43 logé dans un conduit d'arrivée de fluide hydraulique 57 dont l'un des orifices débouche dans la partie centrale du corps de vérin 45. Le clapet anti-retour 43 autorise l'entrée du fluide hydraulique dans le corps de vérin 45, mais en interdit la sortie. Le clapet 43 peut être constitué, selon un mode particulier de réalisation, d'une bille 58 maintenue sur une portée par un ressort 59 afin d'obturer un orifice 44.The valves 52, 53 make it possible to authorize or prohibit the circulation of the hydraulic fluid between the upper 40 and lower 41 chambers of the jack as defined by the position of the jack piston 47 relative to the jack body 45. The valves 52, 53 consist of rings which can slide around the control rod 50. The internal diameter of the rings is provided smaller than the diameter of the shoulder 51 of the control rod 50 so that it is possible to keep them open by said audit the shoulder 51. When the valves 52, 53 are not kept open by the shoulder 51, they are held in their seat by springs 55, 56. The control means 42 consist of a non-return valve 43 housed in a hydraulic fluid inlet conduit 57, one of the orifices of which opens into the central part of the jack body 45. The non-return valve 43 authorizes the entry of hydraulic fluid into the cylinder body 45, but prohibits the exit. The valve 43 may consist, according to a particular embodiment, of a ball 58 held on a surface by a spring 59 in order to close an orifice 44.
Les moyens de contrôle 42 du dispositif 12 prévoient que le piston de vérin 47 comporte une cavité 30 sur sa surface cylindrique en regard avec le conduit d'arrivée 57 prévu dans la partie centrale du corps de vérin 45. La cavité 30 est d'une hauteur au moins équivalente à la course maximale du piston de vérin 47. La cavité 30 communique avec le conduit 54 placé longitudinalement et de façon excentrée afin de relier les surfaces circulaires inférieures et supérieures du piston de vérin 47, par un canal de liaison 31.The control means 42 of the device 12 provide that the jack piston 47 has a cavity 30 on its cylindrical surface opposite the inlet duct 57 provided in the central part of the jack body 45. The cavity 30 is of a height at least equivalent to the maximum stroke of the cylinder piston 47. The cavity 30 communicates with the conduit 54 placed longitudinally and eccentrically in order to connect the lower and upper circular surfaces of the cylinder piston 47, by a connecting channel 31.
Les moyens de contrôle 42 prévoient également que sur les éléments en mouvement 49, 48, 47, 50, 52, 53 soient respectivement prévus des éléments d'étanchéité qui peuvent être constitués de joints toriques en caoutchouc 32, 33, 34, 35, 36, 37, 38, 39.The control means 42 also provide that the moving elements 49, 48, 47, 50, 52, 53 are respectively provided with sealing elements which may consist of rubber O-rings 32, 33, 34, 35, 36 , 37, 38, 39.
Le fonctionnement du dispositif de contrôle 12 montré en figures 5 à 7 est le suivant :The operation of the control device 12 shown in Figures 5 to 7 is as follows:
Le contrôle de la position de la crémaillère de commande 11 s'effectue par l'intermédiaire de la tige de contrôle 50 dont la position détermine la position du piston de vérin 47 grâce à l'action des deux valves 52, 53.The position of the control rack 11 is checked by means of the control rod 50, the position of which determines the position of the jack piston 47 by the action of the two valves 52, 53.
Les valves 52, 53 permettent de contrôler le volume d'huile emprisonné respectivement dans la chambre supérieure 40 et inférieure 41 du vérin hydraulique.The valves 52, 53 make it possible to control the volume of oil trapped respectively in the upper 40 and lower 41 chamber of the hydraulic cylinder.
Le contrôle de la position de la crémaillère de commande 11 s'opère comme suitThe control of the position of the control rack 11 operates as follows
• Obtention d'une nouvelle position de la crémaillère de commande 11 :• Obtaining a new position of the control rack 11:
* Le calculateur non représenté qui définit en permanence la hauteur adéquate de la crémaillère de commande 11 tenant compte des conditions de fonctionnement du moteur agit sur la position de la tige de contrôle 50 par l'intermédiaire d'un dispositif d'asservissement pouvant par exemple être constitué d'un moteur électrique pas à pas de faible puissance (non représenté). La nouvelle position de la tige de contrôle 50 par rapport au piston de vérin 47 solidaire de la crémaillère de commande 11 , a pour effet d'ouvrir la valve 52, 53 située du côté du sens du déplacement de ladite tige de contrôle 50, la valve étant alors soulevée par l'épaulement 51.* The computer not shown which permanently defines the adequate height of the control rack 11 taking into account the operating conditions of the engine acts on the position of the control rod 50 via a servo device which can for example consist of a low power electric stepper motor (not shown). The new position of the control rod 50 relative to the cylinder piston 47 integral with the control rack 11, has the effect of opening the valve 52, 53 located on the side of the direction of movement of said control rod 50, the valve then being lifted by the shoulder 51.
* Le changement fréquent du sens de l'effort sur le piston de vérin 47, dû au mouvement alternatif des pièces mécaniques qui constituent une partie de l'ensemble mobile inférieur du moteur à cylindrée variable, implique une pression alternativement plus forte au dessus, puis au dessous du piston de vérin 47.* The frequent change of the direction of the force on the cylinder piston 47, due to the reciprocating movement of the mechanical parts which constitute a part of the lower mobile assembly of the variable displacement engine, implies a alternately higher pressure above, then below the cylinder piston 47.
* Lorsque la pression devient plus importante du côté de la valve 52, 53 maintenue ouverte par la tige de contrôle 50, le fluide hydraulique s'échappe par l'orifice alors ouvert et soulève la valve 52, 53 du côté opposé libre par rapport à la tige de contrôle et maintenue fermée jusqu'alors par un ressort 55, 56. Le fluide hydraulique se déplace alors vers le côté opposé tant que le piston de vérin n'a pas une position telle que la tige de contrôle ne permette plus le maintien en ouverture de ladite valve ouverte.* When the pressure becomes greater on the side of the valve 52, 53 kept open by the control rod 50, the hydraulic fluid escapes through the orifice then open and lifts the valve 52, 53 on the opposite side free relative to the control rod and kept closed until then by a spring 55, 56. The hydraulic fluid then moves to the opposite side as long as the cylinder piston does not have a position such that the control rod no longer allows the maintenance when opening said open valve.
* Si un cycle de changement de sens de l'effort n'a pu suffire à obtenir la position désirée, et si le piston de vérin 47 n'est pas arrivé a une position telle que la tige de contrôle 50 ne puisse plus maintenir ouverte la valve 52,* If a cycle of change of direction of effort was not sufficient to obtain the desired position, and if the cylinder piston 47 has not arrived at a position such that the control rod 50 can no longer keep open valve 52,
53 ouverte, un ou plusieurs cycle de changement de sens de l'effort supplémentaires peuvent être nécessaires. La valve 52, 53 restée libre par rapport à la tige de contrôle 50 assurant alors un rôle d'anti-retour interdisant au fluide hydraulique stocké de son côté de retourner du côté de la valve 52, 53 est maintenue ouverte par la tige de contrôle 50, et ce jusqu'à obtention de la position désirée du piston de vérin 47 par rapport au corps de vérin 45.53 open, one or more cycles of change of direction of the additional effort may be necessary. The valve 52, 53 remained free relative to the control rod 50 then ensuring a non-return role preventing the hydraulic fluid stored on its side from returning to the side of the valve 52, 53 is kept open by the control rod 50, and this until the desired position of the cylinder piston 47 is obtained relative to the cylinder body 45.
Maintien permanent à une position définie de la crémaillère de commande 11Permanent maintenance at a defined position of the control rack 11
* Des petites fuites ou des suintements peuvent survenir au niveau des joints d'étanchéité 32 à 39, et cela en raison des pressions importantes qui régnent dans le corps du vérin 45. Pour conserver en position adéquate la crémaillère de commande 11 malgré ces pertes hydrauliques, il est nécessaire de corriger en permanence, même de façon infime, sa position par rapport à la tige de contrôle 50.* Small leaks or oozing can occur at the seals 32 to 39, and this due to the high pressures prevailing in the body of the jack 45. To keep the control rack 11 in an adequate position despite these hydraulic losses , it is necessary to permanently correct, even in minute detail, its position relative to the control rod 50.
* Ce résultat est obtenu par l'action conjuguée des deux valves 52, 53 qui permettent de contrôler le volume d'huile emprisonné respectivement dans la chambre supérieure 40 et inférieure 41 du vérin hydraulique, et du clapet anti-retour 43 logé dans le conduit 57 d'arrivée de fluide hydraulique dont l'orifice débouche dans la partie centrale du corps de vérin 45.* This result is obtained by the combined action of the two valves 52, 53 which make it possible to control the volume of oil trapped respectively in the upper chamber 40 and lower 41 of the hydraulic cylinder, and the non-return valve 43 housed in the conduit 57 of hydraulic fluid inlet, the orifice of which opens into the central part of the cylinder body 45.
* Si une fuite de fluide hydraulique existe dans la chambre supérieure 40 ou inférieure 41 du vérin dont les volumes respectifs sont définis par la position du piston de vérin 47 par rapport au corps de vérin 45, il s'ensuit, lorsque la pression est importante du côté de la chambre qui fuit, un déplacement du piston de vérin 47 dans le sens de ladite chambre qui fuit non autorisé par la position de la tige de contrôle 50. Ce déplacement non autorisé a pour conséquences de maintenir fermée la valve 52, 53 positionnée du côté de la chambre qui fuit, mais d'ouvrir la valve 52, 53 positionnée du côté opposé, ceci étant induit par l'épaulement 51 de la tige de contrôle 50 dont la position par rapport au piston de vérin 47 ne sera plus adéquate. La fermeture et l'ouverture des valves correspondantes a pour effet de remplir la chambre opposée à la chambre qui fuit de fluide hydraulique admis via le clapet anti-retour 43 logé dans le conduit 57. Le fluide hydraulique est acheminé vers la chambre 40, 41 opposée à la chambre qui fuit grâce à la cavité 30 aménagée sur la surface cylindrique du piston de vérin 47 qui est en regard d'une part avec l'orifice du conduit 57 débouchant dans la partie centrale du corps de vérin 45 et d'autre part avec le canal de liaison 31 qui relie ladite cavité 30 au conduit 54, aménagé dans la masse du piston de vérin 47.* If a hydraulic fluid leak exists in the upper 40 or lower 41 chamber of the jack whose respective volumes are defined by the position of the jack piston 47 relative to the jack body 45, it follows, when the pressure is high on the side of the leaking chamber, a displacement of the jack piston 47 in the direction of said leaking chamber not authorized by the position of the control rod 50. This unauthorized displacement has the consequences of keeping the valve 52, 53 closed positioned on the side of the leaking chamber, but to open the valve 52, 53 positioned on the opposite side, this being induced by the shoulder 51 of the control rod 50 whose position relative to the cylinder piston 47 will no longer be adequate. Closing and opening the corresponding valves has the effect of filling the chamber opposite to the leaking chamber of hydraulic fluid admitted via the non-return valve 43 housed in the conduit 57. The hydraulic fluid is conveyed to the chamber 40, 41 opposite to the leaking chamber thanks to the cavity 30 provided on the cylindrical surface of the cylinder piston 47 which is opposite on the one hand with the orifice of the conduit 57 opening into the central part of the cylinder body 45 and on the other hand with the connecting channel 31 which connects said cavity 30 to the conduit 54, arranged in the mass of the cylinder piston 47.
* Lorsque le sens de l'effort appliqué au piston de vérin 47 par la crémaillère de commande 11 s'inverse, le fluide hydraulique admis dans la chambre 40, 41 opposée à la chambre qui fuit est refoulé vers ladite chambre qui fuit jusqu'à ce que la valve 52, 53 maintenue ouverte par l'épaulement 51 de la tige de contrôle 50 repose sur son siège, assurant alors la remise en bonne position de la crémaillère de commande 11.* When the direction of the force applied to the cylinder piston 47 by the control rack 11 is reversed, the hydraulic fluid admitted into the chamber 40, 41 opposite the leaking chamber is discharged towards said leaking chamber until that the valve 52, 53 kept open by the shoulder 51 of the control rod 50 rests on its seat, then ensuring that the control rack 11 is returned to the correct position.
Selon l'invention, la position de la tige de contrôle 50 conditionne donc en permanence la position de la crémaillère de commande 11 par rapport au bloc moteur 5, et donc le volume de la chambre d'explosion 9 du moteur. Il est ainsi possible de contrôler le volume de chambre du moteur avec un dispositif d'asservissement de très faible puissance (non représenté).According to the invention, the position of the control rod 50 therefore permanently conditions the position of the control rack 11 relative to the engine block 5, and therefore the volume of the explosion chamber 9 of the engine. It is thus possible to control the chamber volume of the engine with a very low-power servo device (not shown).
On constate que, outre les avantages inhérents au dispositif lui même qui, selon l'invention, permet de faire varier durant leur fonctionnement la cylindrée et/ou le rapport volumétrique effectifs d'un moteur à pistons et d'augmenter son rendement global lorsqu'il est utilisé à charge et régime variables, l'invention présente celui de ne poser aucun problème particulier de faisabilité. L'invention fait appel à des procédés et techniques connus et éprouvés. La présente invention n'est pas limitée à l'exemple de réalisation qui vient d'être décrit ; elle est, au contraire, susceptible de modifications et de variantes qui apparaîtront à l'homme de l'art. It is noted that, in addition to the advantages inherent in the device itself which, according to the invention, makes it possible to vary during their operation the effective displacement and / or the volumetric ratio of a piston engine and to increase its overall efficiency when it is used at variable load and speed, the invention presents that of posing no particular feasibility problem. The invention uses known and proven methods and techniques. The present invention is not limited to the embodiment which has just been described; on the contrary, it is subject to modifications and variants which will appear to those skilled in the art.

Claims

REVENDICATIONS
1. Dispositif permettant de faire varier la cylindrée et/ou le rapport volumétrique effectifs d'un moteur à pistons, pendant son fonctionnement, caractérisé en ce qu'il comprend :1. Device making it possible to vary the effective displacement and / or the volumetric ratio of a piston engine, during its operation, characterized in that it comprises:
• Un premier dispositif permettant de contrôler le rapport volumétrique du moteur en agissant par modification de l'origine de la course du piston (1 ) par rapport au cylindre (2) sans modifier la longueur de ladite course ;• A first device making it possible to control the volumetric ratio of the engine by acting by modifying the origin of the stroke of the piston (1) relative to the cylinder (2) without modifying the length of said stroke;
• Et un second dispositif permettant de contrôler la cylindrée effective du moteur en opérant par refoulement des gaz admis en excès dans le cylindre (2) du moteur dans la tubulure d'admission (19) et par ajustement de la longueur de la course ascensionnelle du piston utilisée pour compresser les gaz.• And a second device making it possible to control the effective displacement of the engine by operating by repressing the gases admitted in excess into the cylinder (2) of the engine in the intake manifold (19) and by adjusting the length of the upward stroke of the piston used to compress gases.
2. Dispositif suivant la revendication 1 , caractérisé en ce que le premier dispositif permettant de contrôler le rapport volumétrique du moteur est constitué d'un système d'engrènement qui comprend :2. Device according to claim 1, characterized in that the first device making it possible to control the volumetric ratio of the engine consists of a meshing system which comprises:
• Une crémaillère (10) solidaire de la partie inférieure du piston (1) et qui est maintenue dans un système de guidage autorisant un mouvement de translation longitudinale à ladite crémaillère ;• A rack (10) integral with the lower part of the piston (1) and which is held in a guide system allowing a longitudinal translational movement to said rack;
• Une crémaillère de commande (11 ) guidée en translation longitudinale dans le bloc moteur (5) ;• A control rack (11) guided in longitudinal translation in the engine block (5);
• Un dispositif (12) permettant de contrôler la position de la crémaillère de commande (11) ;• A device (12) for controlling the position of the control rack (11);
• Et un engrenage (14) monté libre sur une bielle (13) également libre sur un vilebrequin (7) de manière que l'engrenage (14) soit disposé entre les deux crémaillères (10, 11) pour constituer l'élément de transmission du mouvement entre le piston (1) et la bielle (13).• And a gear (14) mounted free on a connecting rod (13) also free on a crankshaft (7) so that the gear (14) is disposed between the two racks (10, 11) to constitute the transmission element movement between the piston (1) and the connecting rod (13).
3. Dispositif suivant la revendication 1 , caractérisé en ce que le second dispositif permettant de contrôler la cylindrée effective du moteur est constitué d'une soupape d'admission additionnelle (15) et d'un dispositif (16,3. Device according to claim 1, characterized in that the second device for controlling the effective displacement of the engine consists of an additional intake valve (15) and a device (16,
17) qui contrôle son ouverture/fermeture et qui permet de modifier le décalage angulaire du point de fermeture et d'ouverture de ladite soupape par rapport au vilebrequin (7).17) which controls its opening / closing and which makes it possible to modify the angular offset of the point of closing and opening of said valve relative to the crankshaft (7).
4. Dispositif suivant la revendication 1 , caractérisé en ce que le second dispositif permettant de contrôler la cylindrée effective du moteur, sans soupape d'admission additionnelle (15), est constitué d'un dispositif (21) qui contrôle l'ouverture et la fermeture d'une soupape d'admission (22) connue en soi et qui permet de modifier le décalage angulaire du point de fermeture et d'ouverture de ladite soupape par rapport au vilebrequin (7).4. Device according to claim 1, characterized in that the second device for controlling the effective displacement of the engine, without additional intake valve (15), consists of a device (21) which controls the opening and the closing of a known intake valve (22) per se and which makes it possible to modify the angular offset of the point of closure and opening of said valve relative to the crankshaft (7).
5. Dispositif suivant la revendication 3, caractérisé en ce que le dispositif qui contrôle l'ouverture et la fermeture de la soupape d'admission additionnelle5. Device according to claim 3, characterized in that the device which controls the opening and closing of the additional intake valve
(15) est un arbre à cames (16) asservi à un dispositif (17) qui contrôle son décalage angulaire par rapport au vilebrequin (7) du moteur.(15) is a camshaft (16) controlled by a device (17) which controls its angular offset relative to the crankshaft (7) of the engine.
6. Dispositif suivant la revendication 4, caractérisé en ce que le dispositif qui contrôle l'ouverture et la fermeture de la soupape d'admission (22) connue en soi est constitué d'un arbre à cames additionnel (21) asservi à un dispositif qui contrôle son décalage angulaire par rapport au vilebrequin (7) du moteur, ledit arbre à cames additionnel (21 ) actionnant ladite soupape par l'intermédiaire d'une liaison mécanique (23) en complément du mouvement imprimé à ladite soupape par son arbre à cames (24).6. Device according to claim 4, characterized in that the device which controls the opening and closing of the inlet valve (22) known per se consists of an additional camshaft (21) controlled by a device which controls its angular offset relative to the crankshaft (7) of the engine, said additional camshaft (21) actuating said valve by means of a mechanical connection (23) in addition to the movement imparted to said valve by its shaft cams (24).
7. Dispositif suivant la revendication 5, caractérisé en ce que le dispositif (17) qui contrôle le décalage angulaire de l'arbre à cames (16) qui commande l'ouverture de la soupape d'admission additionnelle (15) est constitué d'une poulie intermédiaire (18) dont la position définit la longueur de courroie de distribution ou de chaîne comprise entre la poulie (28) de l'arbre à cames (24) des soupapes d'admission (3) et d'échappement (4) du moteur et la poulie (29) de l'arbre à cames (16) qui commande l'ouverture de la soupape d'admission additionnelle (15).7. Device according to claim 5, characterized in that the device (17) which controls the angular offset of the camshaft (16) which controls the opening of the additional intake valve (15) consists of an intermediate pulley (18) whose position defines the length of the timing belt or chain between the pulley (28) of the camshaft (24) of the intake (3) and exhaust (4) valves of the engine and the pulley (29) of the camshaft (16) which controls the opening of the additional intake valve (15).
8. Dispositif suivant la revendication 2, caractérisé en ce que le dispositif (12) qui contrôle la position de la crémaillère de commande (11 ) est constitué d'un vérin hydraulique (25) qui agit sur ladite crémaillère par l'intermédiaire d'une liaison mécanique (20).8. Device according to claim 2, characterized in that the device (12) which controls the position of the control rack (11) consists of a hydraulic cylinder (25) which acts on said rack by means of a mechanical link (20).
9. Dispositif suivant la revendication 7, caractérisé en ce que le dispositif (17) qui contrôle la position de la poulie intermédiaire (18) est constitué d'un vérin hydraulique (26). 9. Device according to claim 7, characterized in that the device (17) which controls the position of the intermediate pulley (18) consists of a hydraulic cylinder (26).
10. Dispositif suivant la revendication 2, caractérisé en ce que l'engrenage (14) présente un profil tronqué de manière à conserver uniquement les dentures utiles à la transmission du mouvement entre le piston (1) et la bielle (13).10. Device according to claim 2, characterized in that the gear (14) has a truncated profile so as to retain only the teeth useful for the transmission of movement between the piston (1) and the connecting rod (13).
11. Dispositif suivant la revendication 2, caractérisé en ce que des surfaces de roulement son aménagées respectivement sur l'engrenage (14) et les crémaillères (10, 11) assurant le centrage permanent dudit engrenage entre lesdites crémaillères, tandis que le point de contact entre lesdites surfaces de roulement est en permanence positionné au niveau de la primitive de l'engrenage (14).11. Device according to claim 2, characterized in that the rolling surfaces are arranged respectively on the gear (14) and the racks (10, 11) ensuring the permanent centering of said gear between said racks, while the point of contact between said rolling surfaces is permanently positioned at the level of the pitch of the gear (14).
12. Dispositif suivant la revendication 2, caractérisé en ce que la partie cylindrique du piston (1) est d'une hauteur suffisante pour loger des segments, mais ne comporte pas de jupe assurant son guidage longitudinal. 12. Device according to claim 2, characterized in that the cylindrical part of the piston (1) is of a sufficient height to accommodate segments, but does not include a skirt ensuring its longitudinal guidance.
13. Dispositif suivant la revendication 2, caractérisé en ce que le dispositif de contrôle (12) comporte :13. Device according to claim 2, characterized in that the control device (12) comprises:
• Un vérin hydraulique comportant des moyens (49) pour le prolongement de son axe (48) permettant de conserver un volume de fluide déplacé en fonction de la course du piston de vérin qui est identique pour chacune des chambres supérieure (40) et inférieure (41) dudit vérin.• A hydraulic cylinder comprising means (49) for the extension of its axis (48) making it possible to maintain a volume of fluid displaced as a function of the stroke of the cylinder piston which is identical for each of the upper (40) and lower ( 41) of said cylinder.
• Des moyens de contrôle (42) qui permettent de déplacer vers une position déterminée ou de maintenir dans une position déterminée l'axe (48) du vérin par rapport au corps du vérin (45).• Control means (42) which make it possible to move the axis (48) of the actuator relative to the body of the actuator (45) to a determined position or to maintain in a predetermined position.
14. Dispositif suivant la revendication 13, caractérisé en ce que le dispositif de contrôle (12) comporte :14. Device according to claim 13, characterized in that the control device (12) comprises:
• Un corps de vérin (45) monté fixe par rapport au bloc moteur (5) parallèlement à la crémaillère de commande (11), un couvercle de vérin (46) monté fixe par rapport au corps de vérin (45), un piston de vérin (47), un axe de vérin (48) et un prolongateur d'axe de vérin (49) assemblés avec la crémaillère de commande (11 ), qui constituent le système de guidage supérieur de ladite crémaillère de commande (11 ) et qui peuvent se déplacer longitudinalement par rapport au corps de vérin (45),• A cylinder body (45) mounted fixed relative to the engine block (5) parallel to the control rack (11), a cylinder cover (46) mounted fixed relative to the cylinder body (45), a piston cylinder (47), a cylinder axis (48) and a cylinder axis extension (49) assembled with the control rack (11), which constitute the upper guide system of said control rack (11) and which can move longitudinally relative to the cylinder body (45),
• Des moyens de contrôle (42) qui sont constitués d'une tige de contrôle (50) comportant un épaulement (51) et pouvant se déplacer longitudinalement, ladite tige de contrôle (50) étant positionnée parallèlement à l'axe de vérin (48) et traversant de part en part le couvercle de vérin (46), le corps de vérin (45) et le piston de vérin (47) grâce à des orifices aménagés dans lesdits couvercle de vérin (46), corps de vérin (45) et piston de vérin (47), de valves (52, 53) logées dans un conduit (54) placé longitudinalement et de façon excentrée aménagé dans la masse du piston de vérin (47), lesdites valves (52, 53) permettant d'autoriser ou d'interdire la circulation du fluide hydraulique entre les chambres supérieure (40) et inférieure (41) du vérin telles que définies par la position du piston de vérin (47) relative au corps de vérin (45), lesdites valves (52, 53) étant constituées de bagues qui peuvent coulisser autour de la tige de contrôle (50), et leur diamètre intérieur étant inférieur au diamètre de l'épaulement (51) de la tige de contrôle (50) de telle sorte qu'il soit possible de les maintenir ouvertes grâce audit épaulement (51) de ladite tige de contrôle (50), lorsque lesdites valves ne sont pas maintenues ouvertes par ledit épaulement (51 ) de ladite tige de contrôle (50), elles sont maintenues sur leur siège par des ressorts (55, 56), et d'un clapet anti-retour (43) logé dans un conduit (57) d'arrivée de fluide hydraulique dont l'un des orifices débouche dans la partie centrale du corps de vérin (45), ledit clapet anti-retour autorisant l'entrée du fluide hydraulique dans le corps de vérin (45), mais en interdisant la sortie.• Control means (42) which consist of a control rod (50) comprising a shoulder (51) and which can move longitudinally, said control rod (50) being positioned parallel to the cylinder axis (48 ) and passing right through the actuator cover (46), the actuator body (45) and the actuator piston (47) by means of orifices arranged in said actuator cover (46), actuator body (45) and piston of cylinder (47), of valves (52, 53) housed in a conduit (54) placed longitudinally and eccentrically arranged in the mass of the piston of cylinder (47), said valves (52, 53) making it possible to authorize or prohibit the circulation of hydraulic fluid between the upper (40) and lower (41) chambers of the jack as defined by the position of the jack piston (47) relative to the jack body (45), said valves (52 , 53) being made up of rings which can slide around the control rod (50), and their internal diameter being less than the diameter of the shoulder (51) of the control rod (50) so that it is possible to keep them open by means of said shoulder (51) of said control rod (50), when said valves are not kept open by said shoulder (51) of said control rod (50), they are held in their seats by springs (55, 56), and a non-return valve (43) housed in a hydraulic fluid inlet pipe (57) one of the orifices of which opens into the central part of the cylinder body (45), said non-return valve allowing the entry of hydraulic fluid into the cylinder body (45 ), but by prohibiting the exit.
15. Dispositif suivant la revendication 14, caractérisé en ce que le piston de vérin (47) comporte une cavité (30) sur sa surface cylindrique en regard avec l'orifice du conduit (57) d'arrivée de fluide hydraulique débouchant dans la partie centrale du corps de vérin (45), ladite cavité (30) étant d'une hauteur au moins équivalente à la course maximale dudit piston de vérin (47) et étant reliée au conduit (54) placé longitudinalement et de façon excentrée aménagé dans la masse dudit piston de vérin (47) reliant les surfaces circulaires inférieure et supérieure dudit piston de vérin (47), par un canal de liaison (31).15. Device according to claim 14, characterized in that the jack piston (47) has a cavity (30) on its cylindrical surface facing the orifice of the conduit (57) for the arrival of hydraulic fluid opening into the central part of the cylinder body (45), said cavity (30) being of a height at least equivalent to the maximum stroke of said cylinder piston (47) and being connected to the conduit (54) placed longitudinally and eccentrically arranged in the mass of said cylinder piston (47) connecting the lower and upper circular surfaces of said cylinder piston (47), by a connecting channel (31).
16. Dispositif suivant la revendication 14, caractérisé en ce que le clapet antiretour (43) est constitué d'une bille (58) maintenue sur une portée par un ressort (59) et obturant un orifice (44).16. Device according to claim 14, characterized in that the non-return valve (43) consists of a ball (58) held on a bearing by a spring (59) and closing an orifice (44).
17. Dispositif suivant la revendication 14, caractérisé en ce que le conduit (57) d'arrivée de fluide hydraulique dont l'un des orifices débouche dans la partie centrale du corps de vérin (45) est connecté au circuit hydraulique sous pression assurant la lubrification du moteur à cylindrée variable.17. Device according to claim 14, characterized in that the conduit (57) of hydraulic fluid inlet of which one of the orifices opens into the central part of the cylinder body (45) is connected to the hydraulic circuit under pressure ensuring the variable displacement engine lubrication.
18. Dispositif suivant la revendication 14, caractérisé en ce qu'il comporte des éléments d'étanchéité constitués de joints toriques en caoutchouc (32, 33, 34, 35, 36, 37, 38, 39).18. Device according to claim 14, characterized in that it comprises sealing elements consisting of rubber O-rings (32, 33, 34, 35, 36, 37, 38, 39).
19. Dispositif suivant la revendication 14, caractérisé en ce que l'épaulement (51) de la tige de contrôle (50) assure le centrage de ladite tige de contrôle dans le conduit (54) longitudinal excentré aménagé dans la masse du piston de vérin (47), ledit épaulement comporte des rainures ou des gorges autorisant la circulation du fluide au travers dudit conduit. 19. Device according to claim 14, characterized in that the shoulder (51) of the control rod (50) ensures the centering of said control rod in the eccentric longitudinal conduit (54) arranged in the mass of the cylinder piston (47), said shoulder has grooves or grooves allowing the circulation of the fluid through said conduit.
EP98924396A 1997-05-09 1998-05-07 Device for varying a piston engine effective volumetric displacement and/or volumetric ratio of during its operation Expired - Lifetime EP0980466B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
FR9705943 1997-05-09
FR9705943A FR2763096B1 (en) 1997-05-09 1997-05-09 DEVICE FOR VARYING THE EFFECTIVE CYLINDER AND / OR THE VOLUMETRIC RATIO OF PISTON ENGINES DURING THEIR OPERATION
FR9804601A FR2763097B1 (en) 1997-05-09 1998-04-07 DEVICE FOR CONTROLLING THE POSITION OF THE CONTROL RACK OF A VARIABLE CYLINDER MOTOR
FR9804601 1998-04-07
PCT/FR1998/000918 WO1998051911A1 (en) 1997-05-09 1998-05-07 Device for varying a piston engine effective volumetric displacement and/or volumetric ratio of during its operation

Publications (2)

Publication Number Publication Date
EP0980466A1 true EP0980466A1 (en) 2000-02-23
EP0980466B1 EP0980466B1 (en) 2002-03-20

Family

ID=26233534

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98924396A Expired - Lifetime EP0980466B1 (en) 1997-05-09 1998-05-07 Device for varying a piston engine effective volumetric displacement and/or volumetric ratio of during its operation

Country Status (11)

Country Link
US (1) US6354252B1 (en)
EP (1) EP0980466B1 (en)
JP (1) JP4154622B2 (en)
KR (1) KR100595778B1 (en)
AT (1) ATE214784T1 (en)
AU (1) AU723539B2 (en)
CA (1) CA2289568C (en)
DE (1) DE69804297T2 (en)
ES (1) ES2174440T3 (en)
FR (1) FR2763097B1 (en)
WO (1) WO1998051911A1 (en)

Families Citing this family (50)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3353709B2 (en) * 1998-07-08 2002-12-03 トヨタ自動車株式会社 In-cylinder injection spark ignition internal combustion engine
FR2786530B1 (en) * 1998-11-26 2001-01-19 Vianney Rabhi MECHANICAL TRANSMISSION DEVICE FOR A VARIABLE CYLINDER MOTOR
FR2827634B1 (en) * 2001-07-18 2003-10-03 Vianney Rabhi IMPROVEMENTS ON MECHANICAL TRANSMISSION DEVICES FOR A VARIABLE CYLINDER ENGINE
DE10240913A1 (en) * 2002-09-04 2004-03-18 Schatz Thermo Engineering Air inlet control for IC engine has a fast acting rotating air valve in the inlet duct for each cylinder to vary the compression ratio for fuel injection engines
FR2867515B1 (en) * 2004-03-11 2006-06-02 Vianney Rabhi ADJUSTING DEVICE FOR VARIABLE VOLUMETRIC RATIO ENGINE
US20060243227A1 (en) * 2005-04-28 2006-11-02 Greve Christopher G Variable-compression engine
FR2896544B1 (en) * 2006-01-26 2008-05-02 Vianney Rabhi CYLINDER HEAD ASSEMBLY AND MOTOR BLOCK FOR A VARIABLE VOLUMETRIC RATIO ENGINE
FR2896539B1 (en) * 2006-01-26 2008-05-02 Vianney Rabhi PRESS DEVICE FOR MOTOR WITH VARIABLE VOLUMETRIC RATIO.
FR2896538B1 (en) * 2006-01-26 2008-05-02 Vianney Rabhi ELECTROMECHANICAL DEVICE FOR CONTROLLING A VARIABLE VOLUMETRIC RATIO ENGINE
FR2902145B1 (en) * 2006-06-07 2008-08-08 Renault Sas METHOD AND SYSTEM FOR CONTINUOUSLY CONTROLLING THE POSITION OF A COMPRESSION RATE CHANGE ACTUATOR OF A THERMAL ENGINE
WO2008006042A1 (en) * 2006-07-07 2008-01-10 Borgwarner Inc Control method for a variable compression actuator system
US20080060628A1 (en) * 2006-09-07 2008-03-13 Heimbecker John A Self-lubricating piston
US7475666B2 (en) * 2006-09-07 2009-01-13 Heimbecker John A Stroke control assembly
EP2063084B1 (en) * 2006-09-15 2010-03-31 HONDA MOTOR CO., Ltd. Engine with variable stroke characteristics
FR2914950B1 (en) 2007-04-16 2012-06-15 Vianney Rabhi DEVICE FOR MEASURING DIRECTLY ON THE PISTON THE EFFECTIVE VOLUMETRIC RATIO OF A VARIABLE COMPRESSION RATE MOTOR.
FR2914951B1 (en) * 2007-04-16 2012-06-15 Vianney Rabhi ELECTROHYDRAULIC DEVICE FOR CLOSED LOOP DRIVING OF THE CONTROL JACK OF A VARIABLE COMPRESSION RATE MOTOR.
FR2919022B1 (en) * 2007-07-19 2012-10-26 Vianney Rabhi HYDRAULIC POWER PLANT FOR VARIABLE COMPRESSION RATE MOTOR.
FR2933140B1 (en) * 2008-06-26 2011-11-11 Vianney Rabhi DEVICE FOR ADJUSTING THE COMPRESSION RATE AT THE BILLED RISE FOR A VARIABLE COMPRESSION RATE MOTOR.
FR2933141B1 (en) * 2008-06-27 2011-11-11 Vianney Rabhi SCREW BALL LIFTING DEVICE FOR VARIABLE COMPRESSION RATE MOTOR.
FR2933471B1 (en) * 2008-07-03 2013-02-15 Vianney Rabhi BALANCED ELECTRO-HYDRAULIC VALVE FOR A VARIABLE COMPRESSION RATE MOTOR HYDRAULIC CONTROL UNIT
US8220422B2 (en) * 2009-08-25 2012-07-17 Manousos Pattakos Rack gear variable compression ratio engines
DE102010009911B3 (en) * 2010-03-02 2010-10-14 Daimler Ag Internal combustion engine operating method, involves adjusting lever element between turning positions for adjusting compression ratios of internal combustion engine, and supporting adjusting device at crank case of engine
DE102010009909B3 (en) * 2010-03-02 2010-10-14 Daimler Ag Reciprocating piston engine for adjustment compression ratio in crankshaft of combustion engine, comprises crankshaft with crank pin, at which lever element is connected with corresponding piston rod
FR2960263B1 (en) 2010-05-19 2015-08-07 Mce E Dev ELASTIC FASTENING FOR VARIABLE COMPRESSION RATE MOTOR PISTON
DE102010062047A1 (en) 2010-11-26 2012-05-31 Zf Friedrichshafen Ag Device for reducing the game in a transmission
FR2969705B1 (en) 2010-12-23 2014-04-04 Vianney Rabhi TUBULAR VALVE FOR CONTROLLING AN ENGINE WITH VARIABLE VOLUMETRIC RATIO
DE102011111089A1 (en) * 2011-08-18 2013-02-21 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Internal combustion engine, particularly spark-ignition engine, has cylinder and movable piston which is connected in articulated manner with end of connecting rod
KR101305572B1 (en) * 2011-11-30 2013-09-09 현대자동차주식회사 Crank Shaftless Internal Combustion Engine
FR2984399B1 (en) * 2011-12-16 2014-01-31 MCE 5 Development CLIP-FIXED BEARING SHAFT FOR VARIABLE COMPRESSION RATE MOTOR
US9316251B2 (en) 2011-12-19 2016-04-19 Mce-5 Development Clip-fastened raceway for a variable compression ratio engine
DE112013005522T5 (en) * 2012-12-21 2015-08-13 Borgwarner Inc. Piston system with variable compression ratio
KR101454387B1 (en) 2013-01-17 2014-10-24 삼성중공업 주식회사 Apparatus for reducing rolling
RU2525372C1 (en) * 2013-03-12 2014-08-10 Ривенер Мусавирович Габдуллин Variable compression ratio ice
FR3003900A1 (en) 2013-03-29 2014-10-03 Vianney Rabhi TURBO-PRESSURE AIR-SUPPRESSING DEVICE WITH AIR-STRIPPING AND REGENERATION
US9243556B2 (en) * 2013-08-20 2016-01-26 Mohammad Hesham Fayiz Abazid Transmission mechanism for a vehicle internal combustion engine
CN106460659B (en) * 2014-06-26 2020-12-01 康明斯公司 Engine configurations having various displacements
FR3023893B1 (en) * 2014-07-15 2017-10-20 Andre Prieur GEAR MECHANISM TO REDUCE UNDESIRABLE LATERAL EFFORTS
FR3029977B1 (en) 2014-12-12 2018-11-30 MCE 5 Development DEVICE FOR TRANSMITTING AN ENGINE, IN PARTICULAR FOR A VARIABLE COMPRESSION AND / OR CYLINDER RATE ENGINE.
CN104612825B (en) * 2015-01-09 2023-11-17 范伟俊 Engine with variable compression ratio
CN104832286A (en) * 2015-05-23 2015-08-12 于德付 High-efficient energy-saving internal combustion engine main piece structure
RU2633473C2 (en) * 2015-12-17 2017-10-12 Евгений Николаевич Еременко Multicylinder free-piston engine-compressor unit
FR3051838B1 (en) 2016-05-24 2018-09-07 MCE 5 Development DEVICE FOR GUIDING A PISTON OF A COMBUSTION PISTON FOR A VARIABLE COMPRESSION RATE MOTOR
CN106014628A (en) * 2016-07-12 2016-10-12 魏伯卿 Gear control telescopic worm wheel boost adjusting device of radial movement variable-cylinder engine
CN106996333A (en) * 2017-05-04 2017-08-01 镇江市高等专科学校 A kind of low-powered engine variable length link
US10781903B2 (en) * 2017-11-14 2020-09-22 Tadatec, Llc Slider-crank mechanism for eliminating side forces
CN108104946B (en) * 2017-12-15 2020-04-03 东风汽车集团有限公司 Lubricating system for variable compression ratio engine
CN110594017A (en) * 2019-09-05 2019-12-20 辽宁工程技术大学 Variable compression ratio mechanism of automobile engine
WO2021201618A1 (en) * 2020-04-02 2021-10-07 장순길 Variable compression ratio engine
US11421588B2 (en) 2020-04-02 2022-08-23 Soon Gil Jang Variable compression ratio engine
RU2756153C1 (en) * 2020-12-25 2021-09-28 Илья Петрович Печкин Method for improving efficiency of reciprocating internal combustion engine

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB189915120A (en) * 1899-07-22 1899-10-07 Charles Thomas Brock Sangster Improvements in Variable Stroke Fluid-pressure Motors and Compressors.
US1434146A (en) * 1920-12-08 1922-10-31 A L Powell Power Co Internal-combustion engine
US1567172A (en) * 1921-09-12 1925-12-29 A L Powell Power Co Inc Internal-combustion engine
US1636612A (en) * 1926-04-24 1927-07-19 Leroy H Noah Internal-combustion engine
FR727994A (en) * 1931-12-08 1932-06-27 Internal combustion engine, compression automatically varying with load
US2088504A (en) * 1936-10-20 1937-07-27 Brzezinski Edward Crankless motor
FR1402509A (en) 1964-07-28 1965-06-11 Internal combustion engine improvements of the kind featuring opposing cylinders and variable stroke pistons
US4131094A (en) * 1977-02-07 1978-12-26 Crise George W Variable displacement internal combustion engine having automatic piston stroke control
CH651109A5 (en) * 1982-12-21 1985-08-30 Pierre Chatelain Device intended to vary the timing setting of a combustion engine
DE3475815D1 (en) * 1983-09-24 1989-02-02 Mazda Motor Intake arrangement for internal combustion engine
US4498430A (en) * 1983-11-14 1985-02-12 Giuliani Robert L Linear reciprocating piston engine
GB8712945D0 (en) * 1987-06-25 1987-07-08 Stidworthy F M Variable valves
JPH0745817B2 (en) * 1988-02-12 1995-05-17 本田技研工業株式会社 Direct injection multi-cylinder diesel engine
FR2630178B1 (en) * 1988-04-14 1993-02-05 Huret Sachs Sa DEVICE FOR ADJUSTING THE ANGULAR SETTING OF A DRIVEN SHAFT IN RELATION TO A DRIVING SHAFT
GB2245646B (en) * 1990-06-26 1994-01-26 Ford Motor Co Variable compression internal combustion engine
US5136987A (en) 1991-06-24 1992-08-11 Ford Motor Company Variable displacement and compression ratio piston engine
KR100200115B1 (en) * 1994-04-25 1999-06-15 정몽규 Combustion chamber for cylinder head
US5528946A (en) * 1994-05-06 1996-06-25 Yadegar; Iraj Apparatus for conversion of reciprocating motion to rotary motion and vise versa
DE4424802C1 (en) * 1994-07-14 1995-07-13 Daimler Benz Ag EGR system for four=stroke engine
US5673665A (en) * 1995-11-11 1997-10-07 Kia Motors Corporation Engine with rack gear-type piston rod
AT2333U1 (en) * 1997-08-11 1998-08-25 Avl List Gmbh INTERNAL COMBUSTION ENGINE
US5934243A (en) * 1998-03-26 1999-08-10 Kopystanski; George Drive mechanism for a reciprocating piston engine
US5950582A (en) * 1998-06-08 1999-09-14 Ford Global Technologies, Inc. Internal combustion engine with variable camshaft timing and intake valve masking
US5957096A (en) * 1998-06-09 1999-09-28 Ford Global Technologies, Inc. Internal combustion engine with variable camshaft timing, charge motion control valve, and variable air/fuel ratio

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9851911A1 *

Also Published As

Publication number Publication date
FR2763097A1 (en) 1998-11-13
AU7660998A (en) 1998-12-08
ES2174440T3 (en) 2002-11-01
WO1998051911A1 (en) 1998-11-19
AU723539B2 (en) 2000-08-31
FR2763097B1 (en) 1999-09-03
EP0980466B1 (en) 2002-03-20
DE69804297D1 (en) 2002-04-25
DE69804297T2 (en) 2002-10-02
KR20010012405A (en) 2001-02-15
CA2289568A1 (en) 1998-11-19
JP4154622B2 (en) 2008-09-24
US6354252B1 (en) 2002-03-12
CA2289568C (en) 2008-04-15
ATE214784T1 (en) 2002-04-15
KR100595778B1 (en) 2006-07-03
JP2001525032A (en) 2001-12-04

Similar Documents

Publication Publication Date Title
EP0980466B1 (en) Device for varying a piston engine effective volumetric displacement and/or volumetric ratio of during its operation
EP0407436B1 (en) Motor propulsion, in particular for an automobile vehicle and vehicle comprising such a unit
EP0100713B1 (en) Sealing element for a gas-cycle control device for a combustion chamber
FR2512492A1 (en) VALVE CONTROL DEVICE FOR INTERNAL PISTON COMBUSTION ENGINES WITH MECANO-HYDRAULIC MOTION TRANSMISSION ARRANGEMENTS
EP1979591A2 (en) Pressure device for a variable compression ratio engine
FR2980516A1 (en) ELECTRO-HYDRAULIC VALVE ACTUATOR WITH ALTERNATIVE CAM
EP2310651A2 (en) Ball-screw lift device for variable compression-ratio engine
FR2673246A1 (en) DEVICE FOR INJECTING LIQUID, PARTICULARLY FUEL, IN AT LEAST ONE PRESSURIZED CHAMBER OF A PERIODICALLY OPERATING MACHINE SUCH AS AN INTERNAL COMBUSTION ENGINE AND SUCH AN ENGINE PROVIDED WITH SUCH A DEVICE.
EP0587479B1 (en) Two-stroke engine with pneumatic injection and first order belancing device for the alternating masses
CA2492844C (en) Hydraulic valve actuator for reciprocating engine
EP0577451B1 (en) Device for controlling the pneumatic injection of carburetted mixture for a two stroke internal combustion engine and its use
EP3692248B1 (en) Regenerative hydraulic valve drive
FR2765635A1 (en) DIRECT FUEL INJECTION PUMP FOR A CONTROLLED IGNITION ENGINE AND INJECTION SYSTEM COMPRISING SUCH A PUMP
FR2711736A1 (en) Liquid fuel injection device for diesel engine.
FR2763096A1 (en) IC engine with variable cylinder capacity or volume ratio
FR2668201A1 (en) Device serving to vary the volumetric ratio of piston engines while they are operating
FR2958333A1 (en) Volumetric ratio and/or variable control mechanism varying device for valve of piston thermal engine of vehicle i.e. car, has calculators or devices carrying processing of parameters of piston thermal engine and servo systems
FR2498686A1 (en) FUEL SUPPLY DEVICE OF AN INTERNAL COMBUSTION ENGINE
LU83433A1 (en) COMBUSTION ENGINE
FR1449708A (en) Free-piston engine machine
WO2021009466A1 (en) Hydraulic cam injection system
FR2711189A1 (en) Hydraulic engine-speed varying assembly for a motor vehicle
FR3054001A1 (en) HYDRAULIC VALVE CONTROL SYSTEM FOR INTERNAL COMBUSTION ENGINE WITH MAXIMUM ENERGY RECOVERY
FR2922953A1 (en) Compression ratio controlling method for e.g. four-stroke petrol engine of motor vehicle, involves carrying out controlled introduction of compressible fluid acting on face of piston of engine and non-turned toward cylinder head of engine
FR2922951A1 (en) Internal combustion engine e.g. spark ignition engine, for motor vehicle, has introducing unit introducing fluid between pistons to separate pistons by control chamber, and transmission mechanism with rod articulated on one of pistons

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19991108

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB IE IT LI NL SE

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 20010615

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE DK ES FR GB IE IT LI NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20020320

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20020320

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20020320

REF Corresponds to:

Ref document number: 214784

Country of ref document: AT

Date of ref document: 20020415

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 69804297

Country of ref document: DE

Date of ref document: 20020425

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020531

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20020524

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20020620

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2174440

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20021223

REG Reference to a national code

Ref country code: FR

Ref legal event code: TQ

REG Reference to a national code

Ref country code: FR

Ref legal event code: AU

REG Reference to a national code

Ref country code: FR

Ref legal event code: TQ

Free format text: BO 2003/18, PAGES: 329, IL Y A LIEU DE REMPLACER: TRANSMISSION PARTIELLE DE PROPRIETE (PT) PAR: AUTRE ACTE AFFECTANT LA PROPRIETE OU LA JOUISSANCE D UN TITRE DE PROPRIETE INDUSTRIELLE (AM)

REG Reference to a national code

Ref country code: FR

Ref legal event code: TQ

Free format text: BO 2003/18, PAGES: 329: IL Y A LIEU DE REMPLACER: TRANSMISSION PARTIELLE DE PROPRIETE (PT) PAR: AUTRE ACTE AFFECTANT LA PROPRIETE OU LA JOUISSANCE D UN TITRE DE PROPRIETE INDUSTRIELLE (AM)

REG Reference to a national code

Ref country code: FR

Ref legal event code: AU

REG Reference to a national code

Ref country code: FR

Ref legal event code: AU

REG Reference to a national code

Ref country code: FR

Ref legal event code: AU

REG Reference to a national code

Ref country code: FR

Ref legal event code: CA

REG Reference to a national code

Ref country code: FR

Ref legal event code: TQ

Owner name: VIANNEY RABHI, FR

Effective date: 20130211

Ref country code: FR

Ref legal event code: TQ

Owner name: MCE-5 DEVELOPMENT, FR

Effective date: 20130211

Ref country code: FR

Ref legal event code: AU

Effective date: 20130211

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20160527

Year of fee payment: 19

Ref country code: CH

Payment date: 20160527

Year of fee payment: 19

Ref country code: ES

Payment date: 20160526

Year of fee payment: 19

Ref country code: DE

Payment date: 20160527

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20160531

Year of fee payment: 19

Ref country code: SE

Payment date: 20160527

Year of fee payment: 19

Ref country code: IT

Payment date: 20160520

Year of fee payment: 19

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 69804297

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20170507

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170508

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170507

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170507

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170531

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20180622

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170508