EP1355050A1 - Brennkraftmaschine - Google Patents

Brennkraftmaschine Download PDF

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Publication number
EP1355050A1
EP1355050A1 EP02405309A EP02405309A EP1355050A1 EP 1355050 A1 EP1355050 A1 EP 1355050A1 EP 02405309 A EP02405309 A EP 02405309A EP 02405309 A EP02405309 A EP 02405309A EP 1355050 A1 EP1355050 A1 EP 1355050A1
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EP
European Patent Office
Prior art keywords
piston
engine
opening
combustion chamber
cylinder
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Withdrawn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
EP02405309A
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English (en)
French (fr)
Inventor
Denys Wasem
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
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to EP02405309A priority Critical patent/EP1355050A1/de
Publication of EP1355050A1 publication Critical patent/EP1355050A1/de
Withdrawn legal-status Critical Current

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    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
    • 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
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F02B75/287—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with several pistons positioned in one cylinder one behind the other
    • 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
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
    • F02B75/30—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders with one working piston sliding inside another

Definitions

  • the present invention relates to a combustion engine internal comprising at least one cylindrical space of which the volume is a function of the axial position of a piston motor associated with a crank rod system, this space cylindrical containing a second piston, integral with a end of an axial tubular element, a variable volume formed between said pistons, means for admitting a combustible mixture associated with said axial tubular element, provided with at least one lateral opening, adjacent to said second piston, means for igniting this combustible mixture and means for the evacuation of the burnt gases.
  • WO 98/26166 has already proposed a motor comprising a cylinder containing two pistons, one of which is a movable piston, integral with a crank rod system, while that the other is a fixed piston secured to a conduit tubular coaxial with the cylindrical combustion chamber.
  • the end of this duct located near the fixed piston is open, while its other end is connected to a fuel mixture supply.
  • the combustion chamber is formed between the face of the movable piston located at the exterior of an intermediate chamber formed between the two pistons and the cylinder which encloses them.
  • the explosion of compressed mixture in the combustion chamber occurs in end of stroke of the movable piston.
  • the fuel mixture drawn into the intermediate chamber is compressed by the movable piston, until it sets in communication the two rooms, at the same time that it clears an exhaust port formed in the wall of the cylinder, so that the burnt gas escapes, simultaneously with the transfer of the combustible mixture of the intermediate chamber in the combustion chamber.
  • this engine works like a two-stroke engine with an annular movable piston and supplied by a coaxial conduit to the cylinder.
  • this engine has two pistons, the exhaust burnt gas from the combustion chamber is not improved compared to two- or four-stroke engines. At on the contrary, this engine has the same disadvantages in this respect than two-stroke engines, i.e. in particular of a polluting engine, necessarily rejecting a certain proportion of unburned gases since these enter the combustion chamber during evacuation burnt gases.
  • the aim of the present invention is in particular to remedy, at least in part, to the disadvantages of internal combustion.
  • the subject of this invention is a motor with internal combustion as defined by claim 1.
  • the engine object of the invention has many advantages, most of which will be mentioned after the description detail of the invention, to the extent that they will be better understood following this description.
  • the attached drawing illustrates, very schematically and to as an example, two forms of execution and a variant of the motor object of the present invention.
  • Figure 1 is an axial sectional view of a cylinder engine according to the first embodiment representing mobile organs, participating in the explosion process of a combustible mixture, in a first corresponding position at the start of an explosion cycle;
  • Figure 2 is a view similar to Figure 1, showing the moving parts in a second position of the explosion cycle;
  • Figure 3 is a view similar to Figure 1, in a third position of the explosion cycle
  • Figure 4 is a view similar to Figure 1, in a fourth position of the explosion cycle
  • Figure 5 is a view similar to Figure 1 in the final position of the explosion cycle
  • Figure 6 is an axial sectional view of a cylinder motor according to the second embodiment representing mobile organs, participating in the explosion process of a combustible mixture, in a first corresponding position maximum compression of the fuel mixture;
  • Figure 7 is a view similar to Figure 6 in the explosion phase
  • Figure 8 is a view similar to Figure 6 in an expansion phase of the fuel mixture after the explosion;
  • Figure 9 is a view similar to Figure 6 in a phase of exhaust of the burnt gases and suction of the gas mixture;
  • Figure 10 is a view similar to Figure 6 in the maximum expansion position of the engine piston
  • Figure 11 is a view similar to Figure 6 in the position of total evacuation of the burnt gases
  • Figure 12 is a view similar to Figure 6 at during the transfer of the combustible mixture from the space between the two pistons in the combustion chamber;
  • figure 13 is a diagram representing displacements of the different organs of a combustion cylinder in function of time during an explosion cycle, relative to the embodiment of Figures 1 to 5;
  • Figure 14 is a diagram similar to that of Figure 13, relating to the second embodiment.
  • the engine part illustrated in FIG. 1 comprises a cylinder 1 in which two pistons slide, a piston motor 2, the external face of which is associated with the connecting rod B and a second piston 3.
  • the face of this second piston 3, located at outside the cylindrical space formed between it and the motor piston 2, is integral with an axial tubular rod 4 sliding mounted inside a shutter 5 of form also tubular, itself slidably mounted in part central tubular 1b formed in the bottom of the cylinder 1.
  • the bottom of this cylinder 1 has an exhaust opening 6 controlled by a valve 7 and a spark plug ignition 8.
  • This supply device 10 can also be connected to two other solenoids 11 and 12 in which are engaged respectively an elongated part 5a of material magnetic, integral with the tubular obturator 5 and a magnetic rod 7a integral with the valve 7.
  • the valve 7 can also be operated by a conventional camshaft instead of being by the solenoid 12.
  • the spark plug 8 can be supplied by this same servo-powered feeder 10.
  • the sweeping piston 3 has a central opening 3a, preferably of frustoconical shape, which allows the conduit formed inside the axial tubular part 4 of communicate with the space between the two pistons 2 and 3.
  • side openings 4c pass through the axial tubular part 4 and are thus likely to communicate the part of the cylinder 1 located below the sweeping piston 3 and constituting the combustion chamber 15 with the space between the two pistons 2, 3 and constituting the intake anteroom fresh gases 14, as can be seen in particular in FIG. 4.
  • These lateral openings 4c are checked by shutter 5, capable of closing them as illustrated by Figures 1 to 3 or open them as illustrated by Figures 4 and 5.
  • the internal face of the driving piston 2 has, in its center, a tapered plug 2a of shape complementary to the frustoconical opening 3a formed in the center of the sweeping piston 3, so that it closes this opening 3a when the two pistons 2, 3 meet, as illustrated by the Figures 1 and 5.
  • An axial rod 2b projects from the center of this frustoconical plug 2a. This axial rod 2b is dimensioned to close the nozzle dispensing opening supply 13 when the piston 2 descends in the direction from the bottom of cylinder 1, as shown in Figure 3.
  • the two pistons 2, 3 make it possible to delimit two chambers variable volumes, the fresh gas suction anteroom 14 ( Figure 3) which has substantially the shape of a cylinder full and the combustion chamber 15 (FIG. 5) which is annular shape, since it is formed around the shutter tubular 5.
  • the diameter of this central tubular part formed by the shutter 5 and of the tubular rod 4 of the sweeping piston 3 can be increased, so that the volume ratio between the anteroom fresh gas intake 14 and combustion chamber 15 be relatively large, with the advantages that will be explained thereafter.
  • the side wall of the cylinder 1 still has pressure relief lights 1a, located just below the sweeping piston 3 in the maximum expansion position illustrated in Figure 1.
  • Position 0 of this diagram corresponds to the explosion of the compressed fuel mixture as illustrated in the figure 5. Following the expansion of the gases, following this explosion, the two pistons 2 and 3 applied one against the other are pushed into the maximum expansion position illustrated by Figure 1 and corresponding to 90 ° of the explosion cycle on the diagram in figure 13. During this movement, the shutter 5 follows the sweeping piston 3.
  • valve 7 will close the exhaust opening 6, the tubular shutter 5 is lowered by the solenoid 11, to clear the openings side 4c and the sweeping piston is moved by the solenoid 9 towards the engine piston 2.
  • the driving piston 2 continues its lowering, compressing the fresh gas at the same time as this is transferred from the anteroom 14 formed between the two pistons 2, 3 to the combustion chamber 15 through the openings lateral 4c.
  • the axial rod 2b integral with the piston engine 2 closes the outlet of the fresh gas nozzle 13, preventing the discharge of these gases to the carburetor (not shown) as illustrated in figure 4.
  • the volume of the combustion chamber 15, at maximum compression of fresh gases before explosion can be increased, which corresponds to an increase of engine power.
  • the ratio between the volume of the suction anteroom 14 and the combustion chamber 15, or more exactly the ratio between the cylindrical surface of the anteroom 14 and the annular surface of the combustion chamber 15 allows to determine the pressure of the fresh gases in the chamber combustion before explosion.
  • the driving piston 22 is here a bell piston whose the tubular part 22c constitutes the side wall of the antechamber of fresh gas 34 ( Figure 9) and the combustion 35.
  • the bottom of this combustion chamber 35 is formed by the fixed frame part 21 which carries the spark plug 28.
  • This fixed part therefore no longer contains cylinder, the latter being formed by the tubular side wall 22c of the bell piston 22.
  • This tubular part 22c of the bell piston 22 is slidably mounted along a wall lateral lateral 21c of the fixed part 21 of the motor which extends below the bottom of the combustion chamber 35.
  • Exhaust lights 22d are provided through the tubular side wall 22c of the bell piston 22.
  • this second embodiment no longer requires a valve for the evacuation of the burnt gases, these being completely evacuated by the sweeping piston 23 through the lights exhaust 22d.
  • Figure 11 shows the sweeping piston at the end of the stroke, corresponding to 180 ° of the explosion cycle illustrated by the diagram in Figure 14. This position of the sweeping piston 23 coincides with the closing exhaust lights 22d from the side wall 22c of the piston bell 22, so that all of the gases burned can be evacuated from the combustion chamber 35 without require valve.
  • valves therefore entails that of the camshaft, which is a simplification notable compared to the first embodiment as well as compared to four-stroke engines.
  • this second form of execution differs from that of the first form in that the sweeping piston 23 leaves the piston 22, as soon as the exhaust lights 22d begin to open, as can be seen in the diagram in the Figure 14, while the driving piston 22 continues its movement sine up, opening the lights 22d exhaust maximum. As soon as the external face of the sweeping piston 23 reaches the upper edge of the lights exhaust 22d from the side wall 22c of the engine piston 22 ( Figure 10), the two pistons descend together. The rest of the cycle corresponds to that of the first form execution.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
EP02405309A 2002-04-16 2002-04-16 Brennkraftmaschine Withdrawn EP1355050A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP02405309A EP1355050A1 (de) 2002-04-16 2002-04-16 Brennkraftmaschine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP02405309A EP1355050A1 (de) 2002-04-16 2002-04-16 Brennkraftmaschine

Publications (1)

Publication Number Publication Date
EP1355050A1 true EP1355050A1 (de) 2003-10-22

Family

ID=28459617

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02405309A Withdrawn EP1355050A1 (de) 2002-04-16 2002-04-16 Brennkraftmaschine

Country Status (1)

Country Link
EP (1) EP1355050A1 (de)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR501308A (fr) * 1916-06-14 1920-04-09 Joseph De Cosmo Moteur à deux temps sans soupapes avec piston distributeur et piston balayeur
JPS56159518A (en) * 1980-05-08 1981-12-08 Kiyoshi Sakumoto Four-stroke-cycle internal-combustion engine
US5509382A (en) * 1995-05-17 1996-04-23 Noland; Ronald D. Tandem-differential-piston cursive-constant-volume internal-combustion engine
WO1998026166A1 (en) 1996-12-09 1998-06-18 Julia Boon An internal combustion engine
WO1998049434A1 (en) * 1997-04-24 1998-11-05 William Richard Mitchell Internal combustion engine
WO2000077366A1 (en) * 1999-06-11 2000-12-21 Lotus Cars Limited Cyclically operated fluid displacement machine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR501308A (fr) * 1916-06-14 1920-04-09 Joseph De Cosmo Moteur à deux temps sans soupapes avec piston distributeur et piston balayeur
JPS56159518A (en) * 1980-05-08 1981-12-08 Kiyoshi Sakumoto Four-stroke-cycle internal-combustion engine
US5509382A (en) * 1995-05-17 1996-04-23 Noland; Ronald D. Tandem-differential-piston cursive-constant-volume internal-combustion engine
WO1998026166A1 (en) 1996-12-09 1998-06-18 Julia Boon An internal combustion engine
WO1998049434A1 (en) * 1997-04-24 1998-11-05 William Richard Mitchell Internal combustion engine
WO2000077366A1 (en) * 1999-06-11 2000-12-21 Lotus Cars Limited Cyclically operated fluid displacement machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 006, no. 045 (M - 118) 20 March 1982 (1982-03-20) *

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