Classifications

• • 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
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
  • F01B3/0005—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
• • 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
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
• • 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
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
  • F01B3/0017—Component parts, details, e.g. sealings, lubrication
  • F01B3/0023—Actuating or actuated elements
• • 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, not specific to groups F01B1/00 - F01B7/00
  • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts, not specific to groups F01B1/00 - F01B7/00 with rotary main shaft other than crankshaft
• • 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
  • F02B75/26—Engines with cylinder axes coaxial with, or parallel or inclined to, main-shaft axis; Engines with cylinder axes arranged substantially tangentially to a circle centred on main-shaft axis
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H23/00—Wobble-plate gearings; Oblique-crank gearings
  • F16H23/02—Wobble-plate gearings; Oblique-crank gearings with adjustment of throw by changing the position of the wobble-member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H23/00—Wobble-plate gearings; Oblique-crank gearings
  • F16H23/04—Wobble-plate gearings; Oblique-crank gearings with non-rotary wobble-members
  • F16H23/08—Wobble-plate gearings; Oblique-crank gearings with non-rotary wobble-members connected to reciprocating members by connecting-rods
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • F02G2254/00—Heat inputs
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T74/00—Machine element or mechanism
  • Y10T74/18—Mechanical movements
  • Y10T74/18056—Rotary to or from reciprocating or oscillating
  • Y10T74/18208—Crank, pitman, and slide

Definitions

• the invention relates to a device for converting a linear movement into a rotational movement in an adjustable manner.
• barrel motors also called axial motors
• This type of engine can be used advantageously in the automotive field where it is important to have engines that can accept many types of fuels, operate optimally at different engine speeds, and for different engine pairs.
• the invention is not limited to this type of application: it can, for example, also apply to pumps for which it is advantageous to vary the compression ratio and or the displacement and therefore the maximum pressure and the debit.
• barrel motors which generally comprise three to five cylinders arranged in an engine block.
• the pistons housed in these cylinders operate an oscillating structure.
• This oscillating structure comprises a fixed ball relative to the engine block. A protrusion of this oscillating structure is then rotated around the motor axis.
• these motors have drawbacks that make them slightly less attractive than conventional rod / crank engines.
• these barrel motors do not include adjustment means enabling them to adapt effectively including the fuel type, the real octane number of the fuel, the temperature of the fuel, the density of the fuel, engine temperature, engine speed, engine speed, engine torque, or even air intake pressure.
• the present invention aims to overcome these disadvantages by providing a device for improving the performance of use of motors or barrel pumps and to make them more efficient than conventional engines rod / crank.
• this device proposes a device of similar structure to that of a motor or a barrel pump, this device comprising: a fixed structure a rotary shaft that can be driven in the case of a motor and driven in the case of a pump, this rotary shaft having a main axis XX '
• this piston comprising a stress recovery point
• an oscillating structure comprising an outgrowth of axis YY ', this structure being mounted oscillating around a bearing point integral with the fixed structure and situated on said main axis XX'
• At least one connecting rod transmitting the forces between the point of recovery of force of the piston and a point of force recovery provided on the oscillating structure, so that when the piston moves in the cylinder, the axis YY 1 of the oscillating structure sweeps a cone of axis XX 'and vertex O and a stress recovery point provided on the protrusion describes a circle of center C located on the axis XX' and of radius R
• crankshaft associated with the rotary shaft and rotatable about the axis XX ', this crankshaft comprising a force recovery point, off-center with respect to the main axis XX'
• this device is characterized in that:
• the aforesaid articulated connection means comprise at least two articulations connected to one another by a connecting element, these two joints being parallel to each other and perpendicular to the aforesaid main axis XX '
• an adjusting device involving an actuator comprising an actuating member articulated on said connecting element so as to cause a tilting of said rigid connecting element and consequently a variation of the aforesaid radius R 5 and the compression ratio and / or the cubic capacity of the device
• the actuating member may consist of the rotary shaft, said shaft being rotatably mounted while being axially movable, actuating means being provided for axially displacing said shaft.
• the actuating member may consist of a jack arranged between said connecting element and said crankshaft, this jack being able to be incorporated in said shaft.
• this means for varying the value of the radius R which may for example consist of a slave control acting Automatically and instantaneously, whatever the variations in the conditions of use of this engine, and some evolutions of any internal or external elements influencing the operation of this engine.
• the value of the radius R is set once and for all in the factory to correspond to a type of operation of the motor
• the value of the radius R is adjustable by the operator when the engine is stopped to take into account the type of fuel used for example.
• the value of the radius R may vary according to the engine speed.
• the value of the radius R can vary according to the engine torque.
• the value of the radius R can vary according to the operating temperature
• the value of the radius R can vary according to the temperature of the flue gases.
• Figures 1 and 2 are schematic axial sections of a cylinder engine including the device according to the invention, the crankshaft being in the upper position ( Figure 1) and in the lower position ( Figure 2).
• Figure 3 schematically shows a section of an embodiment of the invention of the drive of the crankshaft in rotation by the oscillating structure.
• Figure 4 schematically shows a top view of an exemplary embodiment according to the invention of the drive of the crankshaft in rotation by the oscillating structure (the part belonging to the oscillating structure being omitted).
• FIGS. 5 and 6 are two schematic sections of an alternative embodiment of a cylinder engine according to the invention:
• FIG. 5 showing the motor set for a zero compression ratio (pistons deactivated)
• Figure 7 is a schematic axial section of a cylinder engine of the type shown in Figures 5 and 6, equipped with a self-serviced external control system.
• Figure 8 is a coaxial section of a variant of the embodiment illustrated in Figure 7 in which the control system is incorporated in the crankshaft.
• the engine comprises a plurality of cylinders for example four arranged in a barrel within a motor unit (not shown). These cylinders are oriented parallel to a motor axis XX 'and are inscribed in a cylinder coaxial with the motor shaft
• FIGS. 1 and 2 only the two cylinders C 1 , C 2 of axes XiX 'i and X 2 X 2 through which the section plane passes are visible. Inside each of these cylinders Ci, C 2 is slidably mounted a piston Pl, P 2 having a cylindrical sealing surface and a spherical cavity CSi, CS 2 preferably placed at its center.
• each of the spherical cavities CS 1 , CS 2 engages the spherical head Ti, T 2 of a link Bi, B 2 whose other end comprises a spherical cavity CS 1 I 5 CS 2 .
• the engine block On the motor axis XX 1 the engine block comprises an anchor point O on which is mounted an oscillating structure SO via a cardan link LC or the like (not shown in detail).
• This oscillating structure SO has a pyramidal shape for example with a square base of axis YY '. At each vertex of the base is placed a spherical head TS 1 , TS 2 intended to engage in a corresponding spherical cavity CS'i, CS ' 2 of a link Bi, B 2 . In the center of the base, the oscillating structure SO has a point of attachment on which is fixed the cardan link LC.
• This cardan link LC prevents linear movements of the attachment point of the oscillating structure relative to the engine block, and rotations relative to the axis XX 'while leaving the oscillating structure SO free to oscillate around the other two axes of rotation.
• the crankshaft V comprises a rotating circular plate PT of axis XX 1 mounted at the end of a splined coaxial AM motor shaft mounted on two bearings PAi, PA 2 allowing both the rotation of the crankshaft V as well as its displacement in translation along the axis XX '.
• the plate PT is provided with two diametrically opposed lugs OR 1 respectively provided with two coaxial radial bores forming a hinge yoke.
• the connecting fork F comprises, on the one hand, on one side two parallel ears OR 2 distant from each other respectively provided with two respective coaxial cylindrical holes UU axes 1 and on their outer faces, a face d support and, on the other hand, on the other side a load-bearing connection LR comprising an annular bearing R 1 , for example ball or roller, pivotally mounted on the fork F about an axis Z, Z 'perpendicular to the axis of rotation of said bearing Ri.
• the two ears OR 2 of the fork F engage between the two ears OR 1 of the plate PT so that the bores are arranged coaxially with the holes and can be traversed by a common joint axis AC.
• the cylindrical section TC tightly engages in the free volume defined by the central ring 54 of the bearing R 1 , so that the protuberance of the oscillating structure is secured to said central ring 51.
• the force recovery connection LR can for example comprise, as represented in FIG. 4, a circular cage 55, which receives at its center a ball or roller bearing R 1 or a lubricated bearing to allow rapid rotation of the two bearing rings. or of the bearing around the axis YY ', the rotation frequency around this axis being the same as the rotation frequency of the motor.
• the circular cage 55 also has on two diametrically opposed locations two trunnions TR 1 , TR 2 disposed along an axis ZZ 'perpendicular to YY'. These two trunnions TR 1 , TR 2 are supported by two coaxial bearings integral with the fork Fet allow pivoting of the cage 55 relative to the fork F about the axis ZZ '.
• the relative displacements between the cage 55 and the fork F are a function of the stresses imposed for the adjustment of the motor.
• the lubrication constraints on these links are therefore much less severe than on the YY 'axis.
• the rotary assembly comprising the motor shaft 20 and the plate 21 is axially fixed.
• the plate 21 comprises an eccentric hinge 22 on which is articulated one of the ends of a fork 23 similar to the fork F of the embodiment illustrated in Figures 1 to 4.
• the other end of the fork F is connected to the top of an oscillating structure 24 similar to the structure SO.
• the connecting element of the fork is made in two parts joined to each other by means of a central articulation AC oriented parallel to the axes of the two joints of the fork.
• the adjustment of the radius R is then obtained by varying the angle formed between the two parts of the fork 23.
• This adjustment can be obtained by means of an actuator for example hydraulic or electric provided between the plate and the fork or even d a cylinder incorporated in the motor shaft 20.
• the motor shaft 20 is tubular and defines a cylindrical central passage through which engages and slides axially an adjusting rod 25 of which one of the ends is connected to the fork by means of a connecting rod 26, one end of which is articulated to the rod 25 while the other end is articulated to the fork 23, at the level of the central articulation AC, around the same axis of articulation as this one.
• the main advantage in being able to vary the compression ratio of an internal combustion engine and spark ignition is the fact of being able to constantly adapt the efficiency of the engine according to its use (the compression ratio must be high to improve the performance of the engine). yield, but reduced when the called torque or the speed or the operating temperature are high to avoid the phenomenon of rattling).
• the fact of being able to vary the rate of compression has other ancillary advantages:
• pistons Pi, P 2 it can be very useful for certain engine configurations: - when starting the engine, the flywheel (rotating masses) can be launched, pistons disengaged, just before starting effective engine, thus reducing the instantaneous power called on the starter, so the weight of this starter, or facilitating the introduction of an alternator in direct drive on the motor shaft (weight reduction, removal of transmission belts and therefore of friction),
• stop and go systems, where the engine is stopped when the vehicle is temporarily immobilized, in order to reduce fuel consumption, the disengagement of the only pistons makes it easier to restart the engine thanks to the kinetic energy conserved then restored by the masses in rotation,
• the radial force is of the reciprocating type, in the shape of a sawtooth, it passes through a very important maximum at the moment of the explosion of the gases, about 3 tons on a medium engine, then down during the rotation, and can go through a slightly negative value depending on the number of cylinders and the engine cycle (this is the case for example for a 4-stroke / 5-cylinder)
• the tangential force which creates the motor torque is also of the alternative type, with extreme values less important than for the radial force, and of form closer to a sinusoid. It turns out that in the fields of application concerned by the present invention, the maximum value of the tangential force corresponds approximately to the minimum value of the radial force, and vice versa.
• the invention takes advantage of these two antagonistic but not simultaneous forces to control the adjusting rod 25 of the inclination of the oscillating structure 24: the radial force tends to push the adjusting rod 25 thus reducing the angle of the oscillating structure 24.
• the invention therefore provides a device for example, mechanical, hydraulic ... which exploits a portion of the engine torque transmitted to transmit in turn to the adjusting rod a force opposing the force induced by the radial force and which tends thus to increase the angle of inclination of the oscillating structure 2.
• One thus obtains an unstable system, which would tend to oscillate if one left it free. So we use a regulator, controlled by the outside that can control this set.
• This regulator is designed to have three types of operation: it blocks the system in a specific setting position, or it allows the movement of the rod is in one direction or in the other direction.
• this regulator acts as an electric rectifier, by "passing" one of the forces resulting from the radial force or tangential force, and blocks the other.
• the controller is returned to its home position which prohibits any movement.
• the control energy of the regulator being considered negligible (for example the energy required to actuate a distributor spool in the case of a hydraulic control system).
• a few motor turns may be enough to change the setting position, which is of the order of 1/100 or 1/10 second: it is indeed important, to fully exploit the benefit of variable compression, to have a very short response time depending on the engine load.
• the control of the regulator may be of a quite conventional type, and therefore has not been shown. Ideally a series of sensors (motor rotation speed, temperature, transmitted torque ...) transmit signals to an electronic computer, then an electric control drives the regulator. However, one can consider any other type of sensors and controls, for example mechanical ...
• This device can be of any kind, mechanical, hydraulic, electric ... and can be coupled directly to the tilt adjustment rod plateau, or any other intermediary able to take into account the actual inclination of the plate.
• crankshaft transmission shaft 30 is separated into two elements designated main section 31 and secondary section 32. These sections are hollow and traversed by the rod 33 for adjusting the inclination of the oscillating structure 34.
• the main section 31 :
• the secondary section 32 is a section of The secondary section 32.
• - is connected to the adjusting rod 33 by a helical coupling (screw / nut system) with a wide pitch 41, for example with an effective thread pitch of about 20 °, so that the movements are reversible (a relative rotation of the main shaft and the secondary shaft causes an axial displacement of the adjusting rod 33, and conversely the axial displacement of the rod 33 is possible if a force is exerted on said rod 33)
• - is also connected to the motor housing by means of a bearing 42 or ball bearing, with immobilization in the axial direction.
• the secondary shaft 32 is a double-acting cylinder 43, the working chambers 44, 45 of which are connected to one another by a distributor 46 and whose piston is secured to the adjustment rod. 33.
• This cylinder does not act as an actuator, but only as a regulator. According to the order, this distributor allows the circulation of hydraulic fluid between the two working chambers 44, 45 or on the contrary prohibits this circulation.
• phase difference generated between the two shafts 31 and 32 can be very easily obtained, in the desired direction, by taking advantage of on the one hand the inertia or the kinetic energy. rotating masses, on the other hand controlled variations in rotational speed of the starter-motor used (AD) ( Figure 8).
• the start-up procedure may include the following steps:
• a parallel hybrid traction train consisting of the engine to the wheels by: a heat engine with self-breaking cylinder, a transformer d transmitter / receiver energy such as an electric motor, a wet or dry type clutch, a variable speed ratio transmission member such as a gearbox.
• the start-up procedure may include the following operating phases
• the heat engine is then in the disengaged position, the crankshaft is directly coupled to the electric motor and is already rotating at a certain speed of rotation.
• the main clutch of the vehicle (conventional dry or wet type clutch, located between the electric motor and the gearbox) is open for a short time necessary for the realization of the points 3 / to 6 /
• the electric motor is slightly accelerated to impart additional kinetic energy to the crankshaft.
• the electric motor is slightly decelerated to allow to reverse the direction of transmission of the torque, and thus push back the control rod, and place the oscillating structure in normal position for the operation of the engine.
• control system could for example be incorporated in the assembly constituted by the plate and the first rotary shaft section.
• the cylindrical cavity of the jack is made directly in the assembly constituted by the plate 50 and the section 51.
• the piston 52 which slides in this hydraulic cavity is directly fixed to the adjustment rod 53
• the adjusting rod 53 itself comprises an axial cylindrical cavity in which a secondary rod 54 acting as a slide of the distributor associated with the jack slides in a sealed manner.
• This rod has at one of its ends axial grooves 55-56 intended to cooperate with channels made in the rod 53 and in the piston 52 to form the aforesaid distributor.
• the distributor associated with the cylinder comprises check valves. The nonreturn valves used in this distributor are housed in the piston 52.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Output Control And Ontrol Of Special Type Engine (AREA)
• Transmission Devices (AREA)

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• 2006
  • 2006-09-26 FR FR0608457A patent/FR2906332B1/fr not_active Expired - Fee Related
• 2007
  • 2007-09-25 US US12/443,038 patent/US20100093491A1/en not_active Abandoned
  • 2007-09-25 EP EP07858382A patent/EP2066922A2/de not_active Withdrawn
  • 2007-09-25 WO PCT/FR2007/001572 patent/WO2008037893A2/fr not_active Ceased

Non-Patent Citations (1)

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