EP2241736A2 - Moteur à combustion interne avec chargement intégré - Google Patents

Moteur à combustion interne avec chargement intégré Download PDF

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Publication number
EP2241736A2
EP2241736A2 EP10005353A EP10005353A EP2241736A2 EP 2241736 A2 EP2241736 A2 EP 2241736A2 EP 10005353 A EP10005353 A EP 10005353A EP 10005353 A EP10005353 A EP 10005353A EP 2241736 A2 EP2241736 A2 EP 2241736A2
Authority
EP
European Patent Office
Prior art keywords
piston
internal combustion
combustion engine
der
valve
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Withdrawn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
EP10005353A
Other languages
German (de)
English (en)
Other versions
EP2241736A3 (fr
Inventor
Peter Pelz
Wilfried Ball
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
Publication of EP2241736A2 publication Critical patent/EP2241736A2/fr
Publication of EP2241736A3 publication Critical patent/EP2241736A3/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F02B33/10—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder
    • F02B33/12—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder the rear face of working piston acting as pumping member and co-operating with a pumping chamber isolated from crankcase, the connecting-rod passing through the chamber and co-operating with movable isolating member
    • 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
    • F02B33/18—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with crankshaft being arranged between working and pumping cylinders
    • 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
    • F02B33/28—Component parts, details or accessories of crankcase pumps, not provided for in, or of interest apart from, subgroups F02B33/02 - F02B33/26
    • F02B33/30—Control of inlet or outlet ports
    • 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
    • F02B75/065—Engines with means for equalising torque with double connecting rods or crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/02—Air cleaners
    • F02M35/022—Air cleaners acting by gravity, by centrifugal, or by other inertial forces, e.g. with moistened walls
    • 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
    • F02B33/26—Four-stroke engines characterised by having crankcase pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M29/00—Apparatus for re-atomising condensed fuel or homogenising fuel-air mixture
    • F02M29/04—Apparatus for re-atomising condensed fuel or homogenising fuel-air mixture having screens, gratings, baffles or the like
    • F02M29/06—Apparatus for re-atomising condensed fuel or homogenising fuel-air mixture having screens, gratings, baffles or the like generating whirling motion of mixture

Definitions

  • the piston simultaneously rotates in its up and down movement and connected via a non-rotatably connected to the piston piston shaft which moves linearly during the up and down movement of the piston relative to the piston with an output shaft.
  • a precompression space defined by the piston, the cylinder inner wall and a partition wall, through which the piston shaft is rotatably and tightly guided, is arranged in which fresh air is precompressed and subsequently supplied to the combustion space arranged above the piston.
  • the piston is connected via a shaft with a crank mechanism, which converts a linear reciprocating motion of the shaft into a rotational movement of at least one crankshaft.
  • At least one further piston which operates within a space guided between two partitions of the cylinder and compresses air which is supplied to the combustion chamber, is fastened to the shaft.
  • a so-called double crank drive as in the DE 198 39 227 A1 is used to convert a linear reciprocating motion of the piston connected to the shaft in a rotary motion of at least one crankshaft, is also from the DE 102 47 196 B4 and the DE 102 47 197 A1 known.
  • the invention has for its object to provide an internal combustion engine with integrated charging, which works with high charging efficiency and provides low-emission exhaust gas.
  • the internal combustion engine according to the invention can be made particularly compact, since the cylinder chamber can be widely used because of the small intrinsic volume of the piston.
  • the claim 3 indicates the internal combustion engine according to the invention in four-stroke operation.
  • the claim 4 characterizes the internal combustion engine according to the invention in two-stroke operation.
  • FIG. 1 shows a section through a median plane of the cylinder in the direction of movement of the piston of an internal combustion engine according to the invention, wherein also located outside of the cutting plane parts are shown.
  • a cylinder 2 of the internal combustion engine operates a disc-shaped piston 4, which forms a working space 8 between its top and a cylinder head 6.
  • the cylinder 2 is closed on its underside by a bottom wall 10, through which a shaft 12, which is preferably rigidly connected to the piston 4, is linearly reciprocatingly guided in a reciprocating fashion. Between the bottom of the piston 4 and the bottom wall 10, a compression space 14 is created in this way.
  • crankshafts 18 and 20 which are formed with crank disks 22 and 24 via peripheral gears 26 and 28 rotatably with each other in Are engaged.
  • the directions of rotation of the crankshafts are preferred as in FIG. 1 specified.
  • a supply valve 38 ( FIG. 2 ) arranged in the region of the mouth of the feed channel 34 in the compression chamber 14 in the compression chamber 14 in the region of the mouth of the feed channel 34 in the compression chamber 14 in the region of the discharge valve 38 ( FIG. 2 ) arranged in the region of the discharge of the discharge channel 36 from the compression chamber 14.
  • a discharge valve 40 is arranged in the region of the discharge of the discharge channel 36 from the compression chamber 14.
  • the supply valve 38 and the discharge valve 40 are formed by a slotted valve disc 42 which is non-rotatably connected in a manner not shown with one of the crankshafts and rotates at the same speed as the crankshafts. More specifically, the valve disk 42 has a feed slot 44 sweeping an angular segment in the circumferential direction (FIG. FIG. 1 ) and an angular segment sweeping in the circumferential direction discharge slot 46.
  • the radial distance of the slots 44 and 46 from the axis of rotation of the valve disc 42 is such that the slots are aligned with the mouth of the supply channel 34 and the discharge of the discharge channel 36, respectively.
  • the discharge channel 36 is connected to a buffer volume or a buffer container 48, which in turn is connected to an inlet channel 52 leading to a cylinder head 6 arranged inlet channel 52.
  • a control valve 54 is arranged in the inlet channel 52.
  • At least one outlet valve 56 is furthermore arranged in a manner known per se, which in the open state connects the working space 8 with an outlet channel 58.
  • a spark plug 59 is disposed in the cylinder head 6, which may be missing in diesel engine training or replaced by a glow plug.
  • the buffer container 48 is provided with a cooler 60, which is preferably connected to a cooling system of the internal combustion engine, preferably also cooled with the cylinder walls are. Corresponding cooling channels are designated 61.
  • the cooler 60 may be designed as an intercooler in a conventional manner as an air cooler.
  • the pressure in the buffer tank 48 is preferably controllable with a blow-off valve 62, which is connected to a control unit.
  • a check valve 64 is advantageously arranged.
  • the internal combustion engine according to the invention is designed with integrated charging, which is extremely efficient, to which the cooling of the buffer tank 48 contributes.
  • the volume of the working chamber 8 changes by the same amount as the volume of the compression chamber 14.
  • the volume of the buffer container 48 has an influence on the dynamics of the system. The larger the volume of the buffer tank 48, the lower the pressure fluctuations. However, when the pressure in the buffer tank 48 is lowered, the engine will react due to the opening of the bleed valve support and will not return to full charge pressure until delayed.
  • the buffer container 48 may include a spring-loaded membrane for pressure stabilization, wherein the spring pressure may be adjustable.
  • the buffer container 48 may also be formed by a rubber-type container whose volume adapts to the pressure. It is possible to let the buffer tank or the buffer volume unfold completely by the charge air is only performed by required connection lines. The geometric compression ratio of the compression space may be higher than that of the working space, since in UT of the piston only the smallest possible dead volume should be present.
  • the check valve 64 ensures that no fresh air already contained in the buffer tank 48 flows back into the compression chamber 14.
  • control times are: Inlet opens: 5 ° before TDC includes: 20 ° to UT Outlet opens: 40 ° before UT includes: 5 ° to UT
  • the blow-off valve 62 is advantageously opened so that no overpressure arises in the buffer container 48. If operation is to be performed with less filling, the cross-section of the inlet channel 52 is advantageously reduced with the control valve 54, which may be designed as a throttle valve. The control of the operation without charging is thus advantageously via the control valve 54. When charging is required, the control valve 54 is fully opened and the control is carried out via the blow-off valve 62, which is completely closed at full load.
  • the phase of the valve disc 42 relative to the crankshaft or the circumferential angular range of the slots 44, 46 may be adjustable.
  • the feed valve 38 and discharge valve 40 formed by the valve disk 42 and its slots can be replaced by simple check valves, wherein the check valve 38 allows an inflow into the compression chamber 14 and the check valve 40 allows an outflow from the compression chamber 14.
  • the supply valve 38 and the discharge valve 40 can also be replaced by freely controllable valves, such as rotary valves. These valves can be individually controlled, whereby a load control is possible. A load control can also take place in that a non-illustrated throttle valve is arranged in the supply channel 34.
  • the throttle valve 54 or a valve arranged in the supply channel 34 may be formed as a tube valve whose flow area is changeable by squeezing.
  • the integrated charging according to the invention can be used on any type of four-stroke reciprocating internal combustion engine, for example gasoline engines with intake manifold injection, direct injection or diesel engines with direct injection, etc.
  • the charging according to the invention provides a spontaneously available high torque even at low speeds. If necessary, it can be supplemented by an exhaust gas turbocharger if very high boost pressures are required.
  • the described double crank drive is an easy way to bring about a linear guide of the shaft 12, whereby an oil-tight separation between the crank chamber and compression chamber is possible.
  • a better efficiency is achieved because of the changed relationship between the position of the piston and the rotational position of the crankshaft.
  • the double crank drive may be replaced by another crank drive, such as a slider-type crank-wheel drive, which allows linear movement of the piston shaft through the opening in the bulkhead.
  • a cyclone 72 has an overall cylindrical housing 74 which is widened in diameter in its lower region and has a flow body 76 projecting into the axis of the cylinder in its bottom wall.
  • An inlet 77 leads eccentrically or tangentially into the extended lower region of the cyclone 72.
  • the housing 74 is double-walled, at least in some areas, wherein the inner wall 78, which consists for example of sheet metal, formed by punching tabs projecting towards the outer wall or inwardly, so that tangentially to the inner wall along flowing air due to the lobes in the Space between the inner wall 78 and the outer wall is directed. From the spaces between the inner wall 78 and the outer wall exit outlets 80, which form storage volumes, which are emptied periodically or permanently.
  • the inner wall 78 which consists for example of sheet metal, formed by punching tabs projecting towards the outer wall or inwardly, so that tangentially to the inner wall along flowing air due to the lobes in the Space between the inner wall 78 and the outer wall is directed. From the spaces between the inner wall 78 and the outer wall exit outlets 80, which form storage volumes, which are emptied periodically or permanently.
  • Such a cyclone 72 may for example be mounted directly in the fresh air inlet of the internal combustion engine instead of the vortex generator 70, where it replaces an air filter or arranged upstream upstream of the air filter, so that the air filter can be formed with lower flow resistance.
  • the vortex generator described by way of example can be varied in many ways.
  • vortex generators without the possibility of particle separation may be inserted at locations where vortex generation is advantageous for other reasons, such as upstream of the cooled buffer vessel for better heat exchange or upstream of the intake valve for better combustion in the combustion chamber.
  • Fig. 4 shows a modified embodiment of an internal combustion engine according to the invention, wherein for parts of Fig. 1 corresponding parts the same reference numerals are used.
  • a further cylinder 82 in which a compressor piston 84 operates, which is attached to the guided through the bottom of the crankcase 16 under sealing shaft 12.
  • compression chambers 86, 88 are formed in the cylinder 82, which are connected via inlet valves with the environment and via outlet valves 94, 96 with the buffer tank 48.
  • the intake valves and exhaust valves may be simple check valves.
  • the cylinder 2 has arranged in the region of the bottom dead center of the piston 4 Matterströmschlitze 98 which release a connection between the compression chamber 14 and the working space 8 in the lower region of the dead center of the piston 4.
  • the inner wall of the cylinder 2 is provided shortly above the dead center of the piston with outlet slots 100, which open into the outlet channel 58.
  • a valve 102 operates in the outlet passage 58.
  • the engine according to Fig. 4 can be varied in many ways. For example, a two-stroke operation is also possible if in the mouth of the inlet channel into the working space 8, a valve similar to the Fig. 1 is arranged. Also, the outlet slots 100 with the additional valve 102 may by an exhaust valve according to Fig. 1 be replaced, so that the engine can be completely head-controlled.
  • the engine according to the invention may have a plurality of, for example, successively arranged cylinder.
  • the compressed in the individual cylinders air can be assigned to the individual cylinders or by a collecting volume, eg. B. a buffer container are performed, which is common to at least one group of cylinders.
  • ⁇ are between about 20 ° and 45 °, depending on the type and design of the internal combustion engine.
  • crank mechanism Another advantage of the basic design of the crank mechanism according to the FIGS. 1 and 5 is achieved, is that the connecting rods are essentially claimed only to train, because the point of articulation of the connecting rod on the piston shaft is constantly below the line connecting the centers of the crank disks.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
EP10005353A 2006-08-16 2007-08-14 Moteur à combustion interne avec chargement intégré Withdrawn EP2241736A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006038081A DE102006038081A1 (de) 2006-08-16 2006-08-16 Verfahren zum Aufladen einer Brennkraftmaschine sowie Brennkraftmaschine mit integrierter Aufladung
EP07786686A EP2054594B1 (fr) 2006-08-16 2007-08-14 Moteur à combustion interne avec chargement intégré

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP07786686.1 Division 2007-08-14

Publications (2)

Publication Number Publication Date
EP2241736A2 true EP2241736A2 (fr) 2010-10-20
EP2241736A3 EP2241736A3 (fr) 2011-06-22

Family

ID=38658311

Family Applications (2)

Application Number Title Priority Date Filing Date
EP10005353A Withdrawn EP2241736A3 (fr) 2006-08-16 2007-08-14 Moteur à combustion interne avec chargement intégré
EP07786686A Not-in-force EP2054594B1 (fr) 2006-08-16 2007-08-14 Moteur à combustion interne avec chargement intégré

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP07786686A Not-in-force EP2054594B1 (fr) 2006-08-16 2007-08-14 Moteur à combustion interne avec chargement intégré

Country Status (4)

Country Link
EP (2) EP2241736A3 (fr)
AT (1) ATE470789T1 (fr)
DE (2) DE102006038081A1 (fr)
WO (1) WO2008019826A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012002566A1 (de) * 2012-02-06 2013-08-08 Rüdiger Sauer Wärmekraftmaschine mit Verbrennungslufteinblasung
RU2514468C2 (ru) * 2012-07-31 2014-04-27 Лев Владимирович Беднягин Двухтактный двигатель внутреннего сгорания с наддувом

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4027533C2 (fr) 1990-08-31 1992-09-10 Karl 4330 Muelheim De Sprenger
DE19825490A1 (de) 1998-06-08 1999-12-09 Dirk Loehr Ansaugverfahren für Hubkolbenmotor
DE19839227A1 (de) 1998-08-28 2000-03-02 Peter Pelz Kraftmaschine, insbesondere Brennkraftmaschine, sowie Kolben
DE10247197A1 (de) 2002-08-12 2004-02-26 Peter Pelz Hubkolbenbrennkraftmaschine und Verfahren zu deren Steuerung
DE10247196B4 (de) 2002-08-12 2006-07-13 Peter Pelz Hubkolbenbrennkraftmaschine sowie Kolben dafür

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5844251A (ja) * 1981-09-08 1983-03-15 Mitsubishi Electric Corp 内燃機関用混合気供給装置
DE3426487A1 (de) * 1984-07-18 1986-01-30 Helmut 7470 Albstadt Sauer Kraftuebertragungsprinzip fuer verbrennungskraftmaschinen
EP0263117A1 (fr) * 1986-02-17 1988-04-13 URQUHART, Robert Moteur a deux temps suralimente
IT1230383B (it) * 1988-08-02 1991-10-21 Sarno Cosimo Manovellism0 atto a migliorare il rendimento termodinamico
DE3920767C3 (de) * 1989-06-24 1996-03-21 Hengst Walter Gmbh & Co Kg Fliehkraft-Vorabscheider
DE4216565A1 (de) * 1991-06-03 1992-12-10 Volkswagen Ag Hubkolben-brennkraftmaschine nach art einer kurbelschleifenmaschine
FR2683857A1 (fr) * 1991-11-18 1993-05-21 Defarge Alexis Moteur thermique a trois bielles par piston.
RU2066379C1 (ru) * 1994-07-13 1996-09-10 Юрий Николаевич Скрипов Двухтактный двигатель внутреннего сгорания
NZ264915A (en) * 1994-11-14 1997-02-24 Quintessential Concepts Ltd Su Reciprocating machine including a cyclical kinematic chain to transfer power between translational and rotational motion
AUPR045600A0 (en) * 2000-09-29 2000-10-26 Raffaele, Peter Robert Fluid devices

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4027533C2 (fr) 1990-08-31 1992-09-10 Karl 4330 Muelheim De Sprenger
DE19825490A1 (de) 1998-06-08 1999-12-09 Dirk Loehr Ansaugverfahren für Hubkolbenmotor
DE19839227A1 (de) 1998-08-28 2000-03-02 Peter Pelz Kraftmaschine, insbesondere Brennkraftmaschine, sowie Kolben
DE10247197A1 (de) 2002-08-12 2004-02-26 Peter Pelz Hubkolbenbrennkraftmaschine und Verfahren zu deren Steuerung
DE10247196B4 (de) 2002-08-12 2006-07-13 Peter Pelz Hubkolbenbrennkraftmaschine sowie Kolben dafür

Also Published As

Publication number Publication date
ATE470789T1 (de) 2010-06-15
EP2241736A3 (fr) 2011-06-22
EP2054594A1 (fr) 2009-05-06
WO2008019826A1 (fr) 2008-02-21
DE102006038081A1 (de) 2008-02-21
EP2054594B1 (fr) 2010-06-09
DE502007004087D1 (de) 2010-07-22

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