EP0302851B1 - Hubkolben-Brennkraftmaschine - Google Patents

Hubkolben-Brennkraftmaschine Download PDF

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Publication number
EP0302851B1
EP0302851B1 EP88890183A EP88890183A EP0302851B1 EP 0302851 B1 EP0302851 B1 EP 0302851B1 EP 88890183 A EP88890183 A EP 88890183A EP 88890183 A EP88890183 A EP 88890183A EP 0302851 B1 EP0302851 B1 EP 0302851B1
Authority
EP
European Patent Office
Prior art keywords
connecting rod
pump
piston
crankcase
combustion engine
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.)
Expired - Lifetime
Application number
EP88890183A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0302851A2 (de
EP0302851A3 (en
Inventor
Kurt Prevedel
Peter Dipl.-Ing. Wünsche
Hans Dipl.-Ing. Oberth
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.)
AVL List GmbH
Original Assignee
AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
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 AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH filed Critical AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
Publication of EP0302851A2 publication Critical patent/EP0302851A2/de
Publication of EP0302851A3 publication Critical patent/EP0302851A3/de
Application granted granted Critical
Publication of EP0302851B1 publication Critical patent/EP0302851B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02B33/04—Engines with reciprocating-piston pumps; Engines with crankcase pumps with simple crankcase pumps, i.e. with the rear face of a non-stepped working piston acting as sole pumping member in co-operation with the crankcase
    • 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
    • F02B1/00—Engines characterised by fuel-air mixture compression
    • F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
    • F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • the invention relates to a reciprocating internal combustion engine, in which the piston sucks fresh gas through a controlled opening on its underside on its way to top dead center and precompresses this gas on its return movement and supplies the cylinder of the internal combustion engine via a connecting line and a further controlled opening and at which is provided in the crankcase, which is essentially circular in cross section, with a connecting rod which, including a large bearing eye, has constant dimensions in the direction of the crankshaft axis, and seals with its parallel end faces on flat counter-surfaces in the crankcase and forms two separate spaces there, which one by means of control elements Form the connecting rod pump.
  • a two-stroke internal combustion engine of this type is described in DE-PS 710 288, in which the entire crankcase is connected to the intake openings when being sucked in by the crankcase pump, but when the pump charge is compressed, the crankcase is compressed by the connecting rod which also serves as the delivery piston in addition to the working piston is divided into two rooms. Of these rooms, only the space in the direction of rotation in front of the connecting rod serves to compress the load, the separation of the two spaces being carried out by tightly guiding the connecting rod on its side faces and its crank rod on the flat and circular inner surfaces of the crank arms.
  • a side extension is attached to it, with its side parts and its outer end on the inner walls of a bulge arranged at the transition from the cylinder to the crankcase and with a contour corresponding to the movement of the extension.
  • crankcase pump for a two-stroke internal combustion engine
  • its low efficiency as a result of the large damaged spaces has only been increased slightly, and this with a relatively large structural size Expenditure.
  • Piston and connecting rod pumps are connected via the crankcase space as a common suction and pressure chamber, so that the application is limited to two-stroke engines.
  • US Pat. No. 3,973,532 describes a four-stroke reciprocating piston internal combustion engine, the piston of which draws air or fuel-air mixture into the crankcase on the way to its top dead center and, on its return movement in the crankcase, conveys pre-compressed air to the intake members of the internal combustion engine.
  • a poor pre-compression efficiency of the engine piston is particularly disadvantageous due to the large damage space formed by the crankcase.
  • DE-OS 36 37 811 it is known from DE-OS 36 37 811 to arrange an additional auxiliary piston which can be driven by the crankshaft in the opposite direction to the working piston. On the one hand, this results in high friction losses and overall poor mechanical efficiency.
  • the installation space dimensions increase in any case and there is a considerable additional effort.
  • the invention has for its object to avoid these disadvantages and also to create a versatile crankcase pump.
  • the invention is that a ring slide is rotatably mounted in the crankcase, which passes through the connecting rod with little play, so that the working space of a piston pump is formed by the piston, the liner and the ring slide, each having a valve-controlled intake and exhaust channel, and that the connecting rod seals over gaps on the one hand with the crank web and on the other hand with the end cover of the crankcase and thus form a suction and a pressure chamber of a separate connecting rod pump in the ring slide valve, each with a recess in the end cover of the crankcase, which is approximately mirror image of the one in the lower one Connecting rod standing dead center are arranged, each with subsequent, controlled inlet and outlet channels in connection.
  • the damage volume of the piston pump is very small and Pressure increases in this pump are therefore correspondingly large.
  • the connecting rod divides the chamber enclosed by the ring slide into two continuously changing volumes, a suction and a pressure chamber.
  • the flow rate can be varied while changing the stroke by changing the connecting rod width and thus adapted to different tasks.
  • the small damage space created by this arrangement increases the pre-compression efficiency considerably.
  • the air volume conveyed is used for purging a two-stroke engine and a four-stroke engine as pre-compressed charge air.
  • This invention thus provides a possibility of charging without an external flushing or charging blower for two- and four-stroke diesel or gasoline engines as well as for internal combustion engines that use other fuels e.g. Gas, are operated.
  • fuels e.g. Gas
  • a simple embodiment according to the invention results from the fact that the passage opening for the connecting rod in the ring slide is constant and the widths of the connecting rod are dimensioned along their length such that the play of the connecting rod with respect to the passage opening is approximately constant at all angular positions of the connecting rod.
  • the connecting rod pump draws in and compresses air and, together with the piston pump, conveys it into a collecting pipe arranged on the suction side.
  • the connecting rod pump can advantageously serve as an independent pump for conveying foreign gases and the piston pump for supercharging the engine.
  • Frictional losses can be kept low by dynamically sealing gaps.
  • the two-stroke internal combustion engine consists of the crankcase 1 with a cast liner 2, the crankshaft 3, the piston 4 and the connecting rod 5.
  • the crankshaft 3 is mounted in the crankcase 1 by means of the roller bearing 6 and has a stepped crank web 7, which with its peripheral surface until it just touches the crankcase 1 or the liner 2 and carries the crank pin 8.
  • This crank pin 8 is encompassed by the large bearing eye 9 of the connecting rod 5, the length of the crank pin being equal to the continuously identical dimension of the connecting rod 5 in the direction of the crankshaft axis 3 ⁇ .
  • the connecting rod 5, which is drive-connected to the piston 4 via the piston pin 10, has two parallel end faces 5 ⁇ and 5 ′′, of which the end face 5 ⁇ seals with the crank web 7 and the end face 5 ′′ with the end cover 11 of the crankcase 1.
  • a ring slide 12 is rotatably supported by means of needles 13.
  • needles 13 instead of the needle bearing, grooves running in the direction of the crankshaft axis can also be provided on one of the sliding surfaces. It is also conceivable to replace the ring slide with a knife gate valve.
  • the connecting rod 5 passes through the ring slide 12, which is centered on the shoulder 7 ⁇ of the crank arm 7 with the aid of the shoulder 12 ⁇ , in a slot 12 ′′, which is determined by the two rounded end edges 14 and 15 of the ring slide 12, with little play this game remains the same in all positions of the connecting rod, the contour of the connecting rod 5 is adapted accordingly, as FIGS. 3 to 6 clearly show.
  • the connecting rod 5 divides the space enclosed by the ring slide 12 into the suction chamber A and the pressure chamber B, each of which has a kidney-shaped recess 16 and 17 stand in the end cover 11 with the inlet channel 18 or the outlet channel.
  • the inlet channel 18 is controlled by the membranes 20, which prevent backflow.
  • Corresponding membranes are provided in the outlet channel 19, not shown.
  • the piston pump As a result of the closure of its working space relative to the crankcase by the ring slide 12, the piston pump has only a very small clearance, as is readily apparent from FIG. 1.
  • This piston pump sucks in air via the suction channel 21, which is controlled by the membrane 22, and conveys the compressed air through the outlet channel 23, which is controlled by membranes 24.
  • the compressed air flows through the inlet slots 25 in the liner 2 into the cylinder space 26, as indicated by the dashed line 27.
  • the burned gases flow out through the outlet slot 28, as indicated by the broken line 29.
  • the air flowing into the connecting rod pump is illustrated by the broken line 30 and the flowing air is shown by the broken line 31.
  • a manifold 32 can expediently be provided, into which both the connecting rod pump and the piston pump deliver.
  • Areas of application of the internal combustion engine according to the invention are both petrol and diesel engines and gas engines in two and four stroke construction, in particular small engines for use e.g. for chainsaws, portable generators and pumps, moped engines and motors for motorcycles and aircraft propulsion e.g. Gliders.
  • the design according to the invention can also be used for larger and larger engines, both in the single-cylinder and in the multi-cylinder design, with a corresponding structural design of the crankcase space.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
EP88890183A 1987-08-05 1988-07-11 Hubkolben-Brennkraftmaschine Expired - Lifetime EP0302851B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT1986/87 1987-08-05
AT0198687A AT399371B (de) 1987-08-05 1987-08-05 Hubkolben-brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP0302851A2 EP0302851A2 (de) 1989-02-08
EP0302851A3 EP0302851A3 (en) 1989-08-16
EP0302851B1 true EP0302851B1 (de) 1991-03-06

Family

ID=3525374

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88890183A Expired - Lifetime EP0302851B1 (de) 1987-08-05 1988-07-11 Hubkolben-Brennkraftmaschine

Country Status (5)

Country Link
US (1) US4813387A (enrdf_load_stackoverflow)
EP (1) EP0302851B1 (enrdf_load_stackoverflow)
JP (1) JPS6463618A (enrdf_load_stackoverflow)
AT (1) AT399371B (enrdf_load_stackoverflow)
DE (1) DE3861935D1 (enrdf_load_stackoverflow)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69006341T2 (de) * 1989-12-29 1994-05-11 Inst Francais Du Petrol Zweitaktmotor mit gesteuerter pneumatischer Einspritzung.
US5771849A (en) * 1995-09-15 1998-06-30 Hamy; Norbert Internal combustion engine with crankcase pressure barrier
JPH09217628A (ja) * 1996-02-13 1997-08-19 Yamaha Motor Co Ltd ２サイクルエンジン
DE19707772A1 (de) * 1997-02-26 1998-08-27 Norbert Dipl Ing Hecke Zahntrieb (Getriebe) zur wechselseitigen Umsetzung einer linearen Bewegung in eine Drehbewegung und dessen Anwendung hauptsächlich bei Hubkolben-Brennkraftmaschinen bzw. Hubkolbenmotoren (Motoren ohne Kurbeltrieb) = Triebstockkolbenmotoren (TSM)
FR2810077A1 (fr) * 2000-06-08 2001-12-14 Michel Bretegnier Perfectionnements aux moteurs a deux temps
US20110146601A1 (en) * 2009-12-22 2011-06-23 Fisher Patrick T Self-Aspirated Reciprocating Internal Combustion Engine
CN103953538A (zh) * 2014-04-11 2014-07-30 宝鸡石油机械有限责任公司 压裂泵连杆十字头机构

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE516725C (de) * 1928-09-05 1931-01-26 Franz Lohe Zweitaktbrennkraftmaschine mit einem Kurbelgehaeusegeblaese
US1795551A (en) * 1929-11-26 1931-03-10 Geisse John Harlin Internal-combustion engine
US1977657A (en) * 1931-01-14 1934-10-23 Frank E Liveranee Internal combustion engine
DE710288C (de) * 1938-06-28 1943-05-27 Hans Figge Zweitaktbrennkraftmaschine mit Kurbelgehaeusepumpe
US2215793A (en) * 1938-11-29 1940-09-24 Mayes Graham Internal combustion engine
US2445715A (en) * 1946-11-12 1948-07-20 Hoof Products Company Crankcase compression, two-cycle engine
US2564913A (en) * 1950-05-04 1951-08-21 Malcolm S Mead Internal-combustion motor
FR1061504A (fr) * 1952-02-23 1954-04-13 Moteur à combustion interne à deux temps
DE954654C (de) * 1954-05-12 1956-12-20 Paul Schauer Zweitaktbrennkraftmaschine mit gesteuerten UEberstroemkanaelen
AT198063B (de) * 1955-08-24 1958-06-10 Promotor Anstalt Fuer Motortec Zweitakt-Brennkraftmaschine mit einer Kurbelgehäusepumpe
US2844131A (en) * 1956-04-16 1958-07-22 Beveridge John Herbert Reciprocating piston machine
US3003486A (en) * 1959-12-24 1961-10-10 Robert O Werner Rear compression two stroke cycle internal combustion engine with connecting rod actuated arcuate valve means
GB1237211A (en) * 1967-05-12 1971-06-30 Richard Grant Parker Improvements in crankcase pumps in two-stroke engines
ZA732299B (en) * 1972-04-10 1974-03-27 E Stenner Improvements in or relating to rotary pumps or engines
US3973532A (en) * 1973-11-09 1976-08-10 Harold Litz Crankcase-scavenged four stroke engine
GB2135385A (en) * 1983-02-11 1984-08-30 Anthony Willoughby Jackson Reciprocating piston crankcase compression machine
AT384080B (de) * 1985-11-08 1987-09-25 Steyr Daimler Puch Ag Viertakt-hubkolbenbrennkraftmaschine mit vorverdichtung der ladung im kurbelgehaeuse
DE3704635A1 (de) * 1987-02-12 1987-06-11 Wollenhaupt Horst Dipl Ing Fh Pleuelgeblaese mit vorspuelung fuer verbrennungsmotoren

Also Published As

Publication number Publication date
EP0302851A2 (de) 1989-02-08
US4813387A (en) 1989-03-21
DE3861935D1 (de) 1991-04-11
JPS6463618A (en) 1989-03-09
JPH0577847B2 (enrdf_load_stackoverflow) 1993-10-27
ATA198687A (de) 1994-09-15
AT399371B (de) 1995-04-25
EP0302851A3 (en) 1989-08-16

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