EP1503049A1 - Moteur à combustion avec soupape à tiroir rotatif - Google Patents

Moteur à combustion avec soupape à tiroir rotatif Download PDF

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Publication number
EP1503049A1
EP1503049A1 EP03425516A EP03425516A EP1503049A1 EP 1503049 A1 EP1503049 A1 EP 1503049A1 EP 03425516 A EP03425516 A EP 03425516A EP 03425516 A EP03425516 A EP 03425516A EP 1503049 A1 EP1503049 A1 EP 1503049A1
Authority
EP
European Patent Office
Prior art keywords
cylindrical
engine according
distributor
lubricating
duct
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.)
Withdrawn
Application number
EP03425516A
Other languages
German (de)
English (en)
Inventor
Mario Brighigna
Edoardo Ruggiero
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
Application filed by Individual filed Critical Individual
Priority to EP03425516A priority Critical patent/EP1503049A1/fr
Publication of EP1503049A1 publication Critical patent/EP1503049A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/16—Sealing or packing arrangements specially therefor
    • 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
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L7/021—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with one rotary valve
    • F01L7/022—Cylindrical valves having one recess communicating successively with aligned inlet and exhaust ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/024—Belt drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2301/00—Using particular materials
    • F01L2301/02—Using ceramic materials

Definitions

  • the present invention relates to an internal combustion engine with rotary distribution.
  • the present invention relates to a reciprocating engine with a rotary device for distribution of the exhaust and intake gases.
  • rotary valves may reach a high speed of rotation and are extremely silent since there are neither elastic elements for the return strokes, nor metal impacts at the end of each stroke.
  • the problem of the seal has been partially solved by adopting an engine structure which basically consists of a cylinder block, one or more cylindrical bodies which can be slidably housed in respective holes in the cylinder block and a rotary distributor rotatably housed in a sealed fashion in a continuous hole made both in the walls of the cylinder block and in the cylindrical bodies so as to act as an assembly element for them.
  • the solution described above improves the seal because it increased proportionally to increases in the pressure in the axial holes of the cylindrical bodies, that is to say, in the combustion chambers. Despite this, following experimental testing, the solution described above did not proved entirely satisfactory.
  • the rotary distributor normally consists of a drum opposite the cylinder combustion chambers, through which hot exhaust gases pass, and rotating inside a special housing at very high speed. These characteristics contribute to heating up the distributor, exposing it to the risk of thermal deformation and consequent dangerous malfunctions.
  • the aim of the present invention is to provide an internal combustion engine with rotary distribution with an improved fluid seal, rotary distributor lubrication and cooling and mechanical strength, which can overcome the above-mentioned problems and disadvantages.
  • the reciprocating internal combustion engine disclosed labelled 1 as a whole, comprises a cylinder block 2, two modular units 3 and a rotary distributor 4.
  • the engine 1 is represented as being of the four-stroke type, with two in-line cylinders. This configuration is used by way of example only and in no way limits the many possible different configurations of the engine made in accordance with the present invention.
  • the cylinder block 2 comprises a base wall 5 and three vertical walls 6, 7, 8 extending from the base wall 5.
  • the cylinder block 2 comprises a chamber 10 which houses a crankshaft 11 with an axis of rotation A.
  • the vertical walls 6, 7, 8 of the cylinder block 2 form two substantially cylindrical cavities 13 extending from the chamber 10 and having respective central axes B, parallel with one another and perpendicular to the axis of rotation A of the crankshaft 11.
  • the crankshaft 11 passes through the two cavities 13 and is supported, by means of bearings of the known type, by the walls 6, 7 and 8 of the cylinder block 2.
  • the cavities 13 comprise respective lower ends 13a, opposite the chamber 10, and upper ends 13b, longitudinally opposite according to the central axis B.
  • Each modular unit 3 comprises a head 16 and a cylindrical body 17, connected to the head 16 and inserted, so that it slides axially, in one of the cavities 13 in the cylinder block 2, coaxial with the cavity.
  • the cylindrical body 17 is advantageously connected to the head 16 by forced screwing down.
  • the cylindrical body 17 has an internal cylindrical wall 18 extending from the head 16 and, at the bottom, leading into the chamber 10 of the cylinder block 2.
  • the cylindrical wall 18 of each modular unit 3 houses, sealed and axially sliding, a piston 19 kinematically connected to the crankshaft 11, in the known way and using methods that are also known and, therefore, not described in further detail.
  • the cylindrical wall 18 of each modular unit 3 forms a combustion chamber 20 between the head 16 and the piston 19.
  • each head 16 there passes, transversally to the axis of the cylindrical body 17, a cylindrical hole 21 made in alignment with the circular holes 15.
  • the different heads 16 are aligned with one another in succession in such a way that the respective cylindrical holes 21 are coaxial with one another.
  • each of the holes 21 has its own internal cylindrical surface 22.
  • the hole 21 in the head 16 is in communication with one or more exhaust and/or intake ducts 23, 24 leading to the outside of the head 16 and, through respective ports 25 and 26, in communication with the combustion chamber 20.
  • the number of ducts 23, 24 for each head 16 substantially depends on the type of engine to be made. For two-stroke engines there is only one exhaust duct 23, whilst four-stroke engines, like the one illustrated in the accompanying drawings, have two ducts, respectively one intake 24 and one exhaust 23.
  • the rotary distributor 4 is cylindrical and is housed in the cylindrical holes 21 in the heads 16, supported, in such a way that it can rotate freely, by two radial bearings 27 and 29.
  • the rotary distributor 4 has its own axis of rotation C.
  • the above-mentioned radial bearings 27 and 29 are inserted in respective housings 30, 32 formed by the above-mentioned holes 15, made in the vertical walls 6, 8 of the cylinder block 2.
  • each of the bearings 27, 29 has a recess 100 forming a zone 101 for accumulation of a lubricating fluid. As illustrated in Figure 7, the recess 100 extends along the circumference for an angle ⁇ less than 180°.
  • the rotary distributor 4 constitutes an assembly element between the modular units 3 and the cylinder block 2 since, once inserted in the respective holes 15 and 21, it prevents them from being separated from one another.
  • the dimensions of the holes 15 and 21 therefore differ only in terms of the presence, at the holes 15, of the bearings 27, 29 supporting the rotary distributor 4.
  • the bearings 27 and 29 are advantageously of the plain type or brasses or, in alternative embodiments not illustrated, of the rolling bearing type.
  • the rotary distributor 4 has a substantially cylindrical external side surface 33 and a plurality of transversal through-openings 34, distributed axially along the axis C and designed to allow communication between the ports 25 and 26 of each head 16 and the respective exhaust and intake ducts 23 and 24.
  • the openings 34 are diametric through-openings and the ports 25, 26 are, therefore, diametrically opposed to the ducts 23, 24, relative to the rotary distributor 4.
  • the external side surface 33 of the distributor 4 is formed by a cylindrical covering liner 102, made of metal material with high strength and hardness.
  • the liner 102 is made of ceramic material.
  • the external side surface 33 of the distributor 4 is hardened using heat treatments on the surface of the distributor 4.
  • the rotary distributor 4 is kinematically connected to the crankshaft 11 by a toothed belt 35, as illustrated in Figure 1. In this way, the distributor is rotated in such a way that it is synchronised with the rotation of the crankshaft 11.
  • the gear ratio between the crankshaft 11 and the rotary distributor 4 is, with reference to the case illustrated for a four-stroke engine, 1/4.
  • the rotary distributor 4 has a plurality of circular radial seal segments 36, housed in respective circular recesses 37 made in the liner 102 and inserted between the distributor 4 and the internal cylindrical surfaces 22 of the holes 21.
  • the details of the segments 36 and recesses 37 are clearly illustrated in Figure 6 which is an enlarged view of the detail P illustrated in Figure 1.
  • two circular recesses 37 are made respectively upstream and downstream of the opening relative to the axis C of the rotary distributor 4, to house relative seal segments 36.
  • the engine 1 comprises a pump 38 for the lubricating fluid, located in a special housing 38a made in the vertical wall 6 of the cylinder block 2. From the pump 38 there extends a lubricating duct 39, a first portion 39a of which supplies the pressurised lubricating fluid to the bearing 27 which supports the rotary distributor 4.
  • the first portion 39a leads into the recess 100 forming the zone 101 for accumulation of the lubricating fluid.
  • the distributor 4 has a first radial channel 40, designed to allow fluid communication between the first portion 39a of the lubricating duct 39 and the second portion 39b of the duct 39.
  • the second portion 39b is inside the rotary distributor 4 and extends longitudinally according to the distributor axis C.
  • the lubricating duct 39 also comprises a third portion 39c, extending from the bearing 29 and connected to the chamber 10 housing the crankshaft 11.
  • the lubricating fluid supplied to the bearing 29 flows through the third portion 39c of the duct 39 and into the chamber 10 from which it is drawn again by the pump 38 and again circulated in the duct 39, according to known methods, not described in further detail herein.
  • Each channel 42 is connected, in a way not illustrated, to the lubricating duct 39 and to a vacuum part 103 located outside the vertical wall 6, at one end of the distributor 4.
  • the vacuum part 103 is of the type with vanes, commonly used in the automobile sector.
  • the vacuum part 103 draws the lubricating fluid through the channel 42 and returns it to the duct 39.
  • the pump 38, duct 39 with its portions 39a, 39b and 39c, first channels 40, second channels 42, groove 41 and vacuum part 103 together form lubricating means 43 for the engine 1 and, in particular, for the rotary distributor 4.
  • the engine 1 comprises a duct 44 for cooling the rotary distributor 4 designed to supply the distributor 4 with a cooling fluid.
  • the cooling duct 44 is also the lubricating duct 39, meaning that the cooling fluid is also the lubricating fluid.
  • the cooling duct 44 forms, for the engine 1, cooling means 45, in particular for cooling the rotary distributor 4.
  • the channels 40 connected to the bearing 29 are connected, in a way not illustrated, to the vacuum part 103 which promotes the return of the lubricating fluid accumulated at the bearing 29 to the chamber 10 then towards the pump 38 again.
  • the suction action of the vacuum part 103 guarantees constant limitation of the accumulation of lubricating fluid on the internal surface 22, preventing excess lubricating fluid from being drawn up by the vacuum produced in the combustion chamber 20 during the piston expansion stage.
  • the above-mentioned cooling duct 44 is separate from the lubricating duct 39 but still partially extends inside the rotary distributor 4.
  • the cooling fluid may be separate from the lubricating fluid.
  • the engine 1 also comprises, for each modular unit 3, a ring-shaped cavity 48 substantially coaxial with the cylindrical body 17, the cavity 48 being in fluid connection with the cooling duct 44 so as to carry away from the cylindrical body 17 the heat produced in the combustion chamber 20 during normal engine 1 operation.
  • the engine 1 disclosed allows effective lubrication of the rotary distributor 4 as well as equally effective distributor cooling.
  • the engine 1 differs from the above description referring to the four-stroke configuration only in terms of the presence of an intake chamber, not illustrated, at the side of the cylindrical body 17, and the presence, inside the cylindrical body 17, of a plurality of intake ports left open by the piston 19 when it reaches its bottom dead centre.
  • the engine disclosed comprises four modular units 3 arranged in line alongside one another with a single rotary distributor 4 passing through them. Therefore, advantageously, the engine disclosed allows the modular assembly of various numbers of units 3, starting with a single unit 3, guaranteeing maximum versatility and flexibility during the design stage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP03425516A 2003-07-31 2003-07-31 Moteur à combustion avec soupape à tiroir rotatif Withdrawn EP1503049A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03425516A EP1503049A1 (fr) 2003-07-31 2003-07-31 Moteur à combustion avec soupape à tiroir rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03425516A EP1503049A1 (fr) 2003-07-31 2003-07-31 Moteur à combustion avec soupape à tiroir rotatif

Publications (1)

Publication Number Publication Date
EP1503049A1 true EP1503049A1 (fr) 2005-02-02

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Family Applications (1)

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EP03425516A Withdrawn EP1503049A1 (fr) 2003-07-31 2003-07-31 Moteur à combustion avec soupape à tiroir rotatif

Country Status (1)

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EP (1) EP1503049A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITPA20100018A1 (it) * 2010-04-20 2011-10-21 Vincenzo Adamo Sistema di distribuzione a flauti.
IT201800006897A1 (it) * 2018-07-03 2020-01-03 Testata con distribuzione rotante

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1672564A (en) * 1922-05-15 1928-06-05 Pearl G Frazier Engine and valve structure
US2137129A (en) * 1936-11-11 1938-11-15 Brown John Rotary valve for internal combustion engines
GB699169A (en) * 1952-04-07 1953-10-28 Alfred Boorer Improvements in or relating to rotary valves for internal combustion engines
EP0258511A1 (fr) * 1986-05-09 1988-03-09 Kabushiki Kaisha S.S Limited Moteur à combustion interne à distributeur rotatif
EP0285539A2 (fr) * 1987-03-30 1988-10-05 Lopez Garcia-Monge, Maria Guadalupe Carmen Dispositif d'admission et d'échappement par arbre à orifices rotatif dans des moteurs à quatre temps
US5074265A (en) * 1989-06-23 1991-12-24 George Ristin Rotary valve with facility for stratified combustion in the internal combustion engine
US5526780A (en) * 1992-11-06 1996-06-18 A. E. Bishop Research Pty. Limited Gas sealing system for rotary valves
US5771849A (en) * 1995-09-15 1998-06-30 Hamy; Norbert Internal combustion engine with crankcase pressure barrier
WO2000071858A2 (fr) * 1999-05-20 2000-11-30 John Francis Grimwood Systemes a soupapes rotatives
US6308677B1 (en) * 1999-01-20 2001-10-30 William Louis Bohach Overhead rotary valve for engines

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1672564A (en) * 1922-05-15 1928-06-05 Pearl G Frazier Engine and valve structure
US2137129A (en) * 1936-11-11 1938-11-15 Brown John Rotary valve for internal combustion engines
GB699169A (en) * 1952-04-07 1953-10-28 Alfred Boorer Improvements in or relating to rotary valves for internal combustion engines
EP0258511A1 (fr) * 1986-05-09 1988-03-09 Kabushiki Kaisha S.S Limited Moteur à combustion interne à distributeur rotatif
EP0285539A2 (fr) * 1987-03-30 1988-10-05 Lopez Garcia-Monge, Maria Guadalupe Carmen Dispositif d'admission et d'échappement par arbre à orifices rotatif dans des moteurs à quatre temps
US5074265A (en) * 1989-06-23 1991-12-24 George Ristin Rotary valve with facility for stratified combustion in the internal combustion engine
US5526780A (en) * 1992-11-06 1996-06-18 A. E. Bishop Research Pty. Limited Gas sealing system for rotary valves
US5771849A (en) * 1995-09-15 1998-06-30 Hamy; Norbert Internal combustion engine with crankcase pressure barrier
US6308677B1 (en) * 1999-01-20 2001-10-30 William Louis Bohach Overhead rotary valve for engines
WO2000071858A2 (fr) * 1999-05-20 2000-11-30 John Francis Grimwood Systemes a soupapes rotatives

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITPA20100018A1 (it) * 2010-04-20 2011-10-21 Vincenzo Adamo Sistema di distribuzione a flauti.
IT201800006897A1 (it) * 2018-07-03 2020-01-03 Testata con distribuzione rotante

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