WO2010081930A1 - Moteur à compression variable et cycle d'atkinson sans frottements ni vibrations - Google Patents

Moteur à compression variable et cycle d'atkinson sans frottements ni vibrations Download PDF

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Publication number
WO2010081930A1
WO2010081930A1 PCT/ES2010/070023 ES2010070023W WO2010081930A1 WO 2010081930 A1 WO2010081930 A1 WO 2010081930A1 ES 2010070023 W ES2010070023 W ES 2010070023W WO 2010081930 A1 WO2010081930 A1 WO 2010081930A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
piston
vibration
variable compression
atkinson cycle
Prior art date
Application number
PCT/ES2010/070023
Other languages
English (en)
Spanish (es)
Inventor
Eduardo García Sánchez
Original Assignee
Garcia Sanchez Eduardo
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
Application filed by Garcia Sanchez Eduardo filed Critical Garcia Sanchez Eduardo
Publication of WO2010081930A1 publication Critical patent/WO2010081930A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0269—Controlling the valves to perform a Miller-Atkinson cycle
    • 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
    • F01B9/042—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 the connections comprising gear transmissions
    • 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
    • F02B75/06—Engines with means for equalising torque
    • 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
    • F01B9/042—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 the connections comprising gear transmissions
    • F01B2009/045—Planetary gearings
    • 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
    • F02B69/00—Internal-combustion engines convertible into other combustion-engine type, not provided for in F02B11/00; Internal-combustion engines of different types characterised by constructions facilitating use of same main engine-parts in different types
    • 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
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a high efficiency thermal machine, which has several features aimed at reducing consumption. To these advantages joins a balanced of first and second order and a greater longevity of the cylinders and pistons.
  • variable compression ratio is used to optimize and regulate said thermodynamic cycles.
  • An interesting configuration consists of a crown system of inner and planetary teeth that allows the connecting rod to be fixed at a point whose trajectory is a straight line, which converts the movement of the connecting rod into a translational movement. By preventing the crank from tilting, the cylinder's clamping on the piston and the associated friction disappear.
  • the present invention uses said configuration, replacing the piston, which is attached to the planetarium, by two kinematic links that constitute the head of the piston and its foot, and have relative motion to each other, achieving a height difference in the upper dead center and thereby modifying the compression ratio.
  • a rotary intake valve In order to achieve a great variation in the effective stroke of the intake and compression, necessary to perform an Atkinson cycle, a rotary intake valve is used, the closure of which can be offset, and which operates in series with a second valve , of conventional design.
  • a drawback of the Atkinson cycle is that the specific power achieved is lower than that of a traditional engine.
  • the lack of a power reserve affects active safety. (Overtaking, incorporation to a fast track through the acceleration lane, etc.)
  • variable compression system is used that improves the thermodynamic cycle for any power demand.
  • the system of the present invention patent basically consists of one or more sets consisting of: 1) A crankshaft Fig. (1), whose crank (distance between its axis of rotation and the axis of the muflequilla) will be designated by: m
  • a kinematic link linking the crankshaft with the piston or pistons Fig. (2) equivalent to the connecting rod in traditional engines, whose essential feature is that it has an angular velocity of the same module as that of the crankshaft and opposite sign. It will be designated by rotating rod Fig. (2). It consists of one or two pinions whose axis of rotation is the crankshaft and whose original radius is (m). The joints that bind this part to the piston, or the pistons, are formed by one or two offset discs with respect to the pinion axis a value equal to (m).
  • a protrusion guide of the piston head Fig. (11) and Fig. (13). formed by a conical pinion and a drill with stretch marks.
  • a rotary valve formed by a plate that rotates inside a slot Fig. (18) and (19), or by means of a rotating shaft with a transverse bore that cuts off the gas flow.
  • Another alternative is to use a tube with one or several ports and admit the gas axially.
  • This design ensures that the articulation or articulations of the rotating rod that are attached to the feet of the pistons describe a straight line (in prolongation of the axis of symmetry of the cylinder), even before the pistons have been assembled: This means that, when turning the crankshaft, and without having yet mounted the pistons, the anchor point of the piston (which is an offset disc belonging to the connecting rod rotating) will have a fully defined movement, its center describing a fixed crown diameter, which is superimposed on the continuation of the cylinder axis.
  • the rotor Fig. (2) It is formed by one or several gears whose axis of rotation will be the crankshaft muffie Fig. (3). These gears are integral with one or several offset discs and are located in different planes Fig. (2). The measure between the center of these discs and the axis of the gears is m. These discs will serve as piston joints.
  • This piece connects crankshaft and piston and therefore plays the role of the connecting rod in a traditional engine.
  • the crown has twice the number of teeth as the gear, and the absolute angular speed of this gear is the same as that of the crankshaft and in the opposite direction.
  • the teeth that constitute the gear of the rotating pinion and the crown are not standardized, exceeding the head height of the pinion tooth more than twice the height of the tooth foot, thus achieving a functional set with oversized teeth.
  • the piston head Fig. (8) consisting of a disc with a protrusion with external striations and with a threaded bore, allows the piston foot, Fig. (7) whose tip is threaded and acts as a screw, when screwed on, modify the total length of the assembly, thereby varying the maximum height reached and modifying the compression.
  • the protrusion guide of the piston head Fig. (11) and rig. (13). formed by a conical pifion and a drill with stretch marks, in addition to allowing the piston to slide vertically, it rotates when it is intended to screw it onto its foot. In order to avoid watering, the grooves of the guide have a slight curvature. Engrana with another conical pifión that allows to turn it from outside the cylinders Fig. (13), by means of an electric motor or a kinematic chain moved by fluid power. It can be supported on several peripheral bearings Fig. (11)
  • the rotary valve formed by a plate that rotates inside a slot Fig. (18) and (19), cuts off the gas flow in the intake process before the second valve, which has a delayed closure, is fully closed.
  • This second valve similar to any usual valve, is responsible for completing the closure of the intake and combat high pressures.
  • the plate can be moved with an alternative turn sent by an electromagnetic system or fluid power, piloted by a microprocessor, or with turns synchronized with the crankshaft, and in this case, the offset can be modified to control the filling. Depending on its geometric shape, it can rotate at the same speed as the crankshaft, or twice as slow.
  • the same plate can be used to control the admission of a second cylinder in parallel.
  • the rotary valve can also be carried out by means of a rotating shaft with a transverse bore that cuts off the gas flow. Another alternative is to use a tube with ports and admit the gas axially. Fig. (20)
  • variable volume that is formed under the pistons can be used to make, by valves and ports a displacement compressor positive.
  • This configuration due to the absence of friction, is suitable for using ceramic materials in the combustion environment in order to increase the working temperature and improve performance.
  • Fig. (1) represents the crankshaft with the crank (wheelbase) equal to m.
  • Fig. (2) depicts the rotor, which acts as a connecting rod with the distances between the gear shaft (which rotates with respect to the muffler) and the centers of the discs (around which the pistons rotate) equal to m . Being also the primitive radius of the pinions equal to m.
  • Fig. (3) represents the crankshaft with the rotating rod.
  • Fig. (4) represents a crown with inner teeth whose original radius is 2 m, which is mounted concentrically with the crankshaft and fixed to the bench.
  • Fig. (5) represents the crankshaft with the rotating rod, whose pinion meshes with the crown.
  • Fig. (6) represents the assembled assembly and the bed with a sectioned cylinder.
  • the piston corresponding to this cylinder would articulate with the rotor disk which in this drawing is hidden by the crown.
  • Fig. (7) depicts the piston foot with a thread to join with the protrusion of the piston head.
  • Fig. (8) represents the piston with its ribbed protuberance. Inside, coast of a threaded drill.
  • Fig. (9) represents the assembly formed by the piston and its foot, its size can vary according to the threaded part.
  • Fig. (10) represents the assembly formed by the piston with its foot, articulating on one of the rotor discs.
  • the disk observed represents the horizontal piston joint, not drawn.
  • Fig. (11) represents the grooved guide for the protrusion of the piston head.
  • Fig. (12) represents the guide and the protrusion of the piston head mounted. Complementary stretch marks allow vertical sliding but not relative rotation.
  • Fig. (13) represents the assembly formed by the pinion integral to the guide and another with an axis that allows rotation from outside the cylinders.
  • Fig. (14) represents the assembled front assembly where the grooved guide is supported on several peripheral bearings.
  • Fig. (15) represents by means of a thick line, the crankshaft crank schematized.
  • Fig. (16) shows, by thick lines, the crank of the measuring crankshaft (m), and the connecting rod constituted by the measuring rotor (m).
  • the horizontal piston rotor disc and upper fixed crown are omitted.
  • Fig. (17) represents figure 16 where the crankshaft is also omitted.
  • Fig. (18) and Fig. (19) represent a rotary valve formed by a plate that rotates inside a groove, thus being able to cut off the gas flow in the intake process.
  • Fig. (20) represents a rotary valve formed by a tube that receives the gas axially and distributes it by means of ports.
  • Fig. (21) shows a cut of the engine without the pistons in which only the crankshaft wrist which is the axis of rotation of the planetary connecting rod is shown.
  • the crown gear has been shown sectioned.
  • Fig. (22) shows an overview of the sectioned motor and without all the assembled parts.
  • the crown gear has been shown sectioned.
  • Fig. (23) shows an overview of the engine, shaded, sectioned and without all the assembled parts.
  • the crown gear has been shown sectioned.
  • the present invention concerns an engine or compressor that is essentially composed of the members whose parts are shown in Fig. (1), (2) , (3), (6), (7), (8), (13), (18) and (20).
  • the system described here Fig. (22) consists of two V-cylinders with:
  • crankshaft Fig. (1) whose distance m between its main shaft and wrist is designated by crank.
  • the joints that connect said rotating connecting rod to the crankshaft and the two pistons are separated by a distance (m) that measures the same as the crankshaft crank. Fig. (2).
  • Two piston-foot assemblies each formed by:
  • a protrusion guide of the piston head Fig. (11) to Fig. (13). formed by a conical pinion and a bore with splines that, in addition to guiding the piston vertically, has the mission of making it rotate, screwing on its foot, when it is intended to vary the compression.
  • This guide meshes with another conical pinion that allows rotation from outside the cylinders Fig. (13). This guide rests on several peripheral bearings.
  • a rotary valve formed by a plate that rotates inside a slot. Fig. (18) and Fig. (19), thus being able to cut off the gas flow in the intake process.
  • a rotary valve formed by a tube with a port. Fig. (20) thus being able to cut off the gas flow in the intake process.
  • the rotor Fig. (2) rotates around the crankshaft wrist Fig. (1), situation represented by figure (3). - The relative position of the internal toothed crowns Fig. (4) and the assembly Fig.
  • crowns are centered with respect to the axis of the crankshaft and will be mounted anchored without the possibility of turning the bench Fig. (6).
  • the piston-foot head assembly is housed in the bench Fig. (10). positioning the toothed crowns in such a way that the joints of the feet of the pistons, describe, when the movement starts, straight lines in prolongation to the axes of symmetry of the cylinders Fig. (22)

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)

Abstract

Ce moteur utilise une couronne dentée et un planétaire permettant de fixer la bielle en un point impliquant une trajectoire droite, convertissant ainsi son mouvement en translation. Du fait de l'absence d'inclinaison, le frottement piston-cylindre disparaît. Le mouvement sinusoïdal pur du piston s'équilibre complètement. Il descend plus lentement que dans les moteurs classiques, d'où une meilleure combustion. La bielle est remplacée par deux pièces filetées permettant une variation de taille par vissage avec une partie de jonction rainurée, ce qui permet de modifier le PMS et la compression. Cette particularité et l'absence de frottements sont idéales pour réaliser un cycle d'Atkinson asymétrique diminuant la course d'admission effective: on utilise une soupape rotative à déphasage variable, en série avec une autre soupape habituelle à ouverture retardée, d'où une réduction des pertes de charge. Ces caractéristiques (amélioration de la combustion, élimination des frottements, cycle symétrique, rapport de compression optimisé) garantissent des rendements pouvant rivaliser avec les systèmes hybrides.
PCT/ES2010/070023 2009-01-19 2010-01-19 Moteur à compression variable et cycle d'atkinson sans frottements ni vibrations WO2010081930A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ES200900136 2009-01-19
ES200900136 2009-01-19

Publications (1)

Publication Number Publication Date
WO2010081930A1 true WO2010081930A1 (fr) 2010-07-22

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017130323B3 (de) 2017-12-18 2019-05-02 Pierburg Gmbh Ventilvorrichtung für eine Verbrennungskraftmaschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56113006A (en) * 1980-02-14 1981-09-05 Yamaha Motor Co Ltd Suction amount controller for engine
GB2108198A (en) * 1981-04-13 1983-05-11 Norman Stinson Ritchie Variable capacity internal combustion engine and output shaft arrangement
US4422414A (en) * 1980-07-18 1983-12-27 John Douglas Rees Piston and cylinder arrangement including means to vary the compression ratio
US5233948A (en) * 1992-12-10 1993-08-10 Ford Motor Company Variable cycle engine
WO1994015073A1 (fr) * 1992-12-19 1994-07-07 Peter Graf Von Ingelheim Moteur a combustion interne a deux pistons par chambre de travail, notamment moteur a deux temps a balayage en equicourant
US20080066709A1 (en) * 2006-09-19 2008-03-20 Slemp David A Rotary valves and valve seal assemblies

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56113006A (en) * 1980-02-14 1981-09-05 Yamaha Motor Co Ltd Suction amount controller for engine
US4422414A (en) * 1980-07-18 1983-12-27 John Douglas Rees Piston and cylinder arrangement including means to vary the compression ratio
GB2108198A (en) * 1981-04-13 1983-05-11 Norman Stinson Ritchie Variable capacity internal combustion engine and output shaft arrangement
US5233948A (en) * 1992-12-10 1993-08-10 Ford Motor Company Variable cycle engine
WO1994015073A1 (fr) * 1992-12-19 1994-07-07 Peter Graf Von Ingelheim Moteur a combustion interne a deux pistons par chambre de travail, notamment moteur a deux temps a balayage en equicourant
US20080066709A1 (en) * 2006-09-19 2008-03-20 Slemp David A Rotary valves and valve seal assemblies

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017130323B3 (de) 2017-12-18 2019-05-02 Pierburg Gmbh Ventilvorrichtung für eine Verbrennungskraftmaschine

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