EP0451466B1 - Kolbenbrennkraftmaschine - Google Patents

Kolbenbrennkraftmaschine Download PDF

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Publication number
EP0451466B1
EP0451466B1 EP91102426A EP91102426A EP0451466B1 EP 0451466 B1 EP0451466 B1 EP 0451466B1 EP 91102426 A EP91102426 A EP 91102426A EP 91102426 A EP91102426 A EP 91102426A EP 0451466 B1 EP0451466 B1 EP 0451466B1
Authority
EP
European Patent Office
Prior art keywords
piston
rocker arm
internal combustion
combustion engine
engine according
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
EP91102426A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0451466A1 (de
Inventor
Werner Mayer
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Individual
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Individual
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Filing date
Publication date
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Publication of EP0451466A1 publication Critical patent/EP0451466A1/de
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Publication of EP0451466B1 publication Critical patent/EP0451466B1/de
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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
    • F02B75/00—Other engines
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial 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
    • F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
    • F02B33/08—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the working-cylinder head arranged between working and pumping cylinders
    • 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
    • F02M49/00—Fuel-injection apparatus in which injection pumps are driven or injectors are actuated, by the pressure in engine working cylinders, or by impact of engine working piston
    • F02M49/02—Fuel-injection apparatus in which injection pumps are driven or injectors are actuated, by the pressure in engine working cylinders, or by impact of engine working piston using the cylinder pressure, e.g. compression end pressure
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F7/006—Camshaft or pushrod housings

Definitions

  • the invention relates to a piston internal combustion engine for operating with gaseous and / or liquid fuels with a fuel supply system, which for compressing fuel per working cylinder has a piston compressor associated with this on the cylinder head side with a compressor cylinder and a stepped piston accommodated in the latter, the larger area of which with the pressure of the combustion chamber of the associated working cylinder and which compresses the fuel by means of its smaller area when the pressure rises in the combustion chamber of the working cylinder, and with at least one overflow path which extends between a compression chamber of the piston compressor and the combustion chamber of the working cylinder and which has at least one in the guideway of the stepped piston has lying and can be shut off or released from a control edge of this piston into the combustion chamber.
  • This internal combustion engine has been improved according to the present invention in that in each case two working cylinders with oppositely movable working pistons are assigned to one another and in that the stepped pistons of the piston compressors assigned to the respective working cylinders are positively coupled in opposite directions for compressing the fuel.
  • the springless drive system of the compressor pistons developed here enables the internal combustion engine to work even at very high speeds and simplifies its control under various operating conditions.
  • the support of the movements of the compressor pistons by a third-party drive brings with it further possible uses of the internal combustion engine, including in Operation with different fuels.
  • the fuel can be, in particular, gaseous fuels and those with gas admixtures, but also liquid fuels in vaporized or atomized form with a wide variety of gas admixtures, including in the form of exhaust gases or air.
  • part of the fuel can combine with the oxygen in the gas admixtures, generate heat and evaporate the rest of the liquid fuel, as a result of which combustion takes place largely without soot particles.
  • Characteristic of the invention is the interaction of two working cylinders in each case and, accordingly, the compressor piston of the fuel compressors assigned to these working cylinders. Due to the forced coupling of the compressor pistons, the two fuel compressors are operated in opposite directions depending on the opposite mode of operation of the working pistons accommodated in the working cylinders.
  • the number of working cylinders of such an internal combustion engine can be any integer.
  • step pistons of the piston compressors are mechanically oppositely coupled from each other by associated working cylinders via a rocker arm.
  • the rocker arm ends can advantageously be articulated on the piston extensions via self-adjusting eccentric bearings, an eccentric sleeve penetrated by a pivot pin imparting the articulation being freely rotatably received in a bearing recess in the rocker arm or piston extension, while the trunnion is then permanently stored in the other part.
  • the compensation of constraints during the movement of the rocker arm is characterized by the articulation of its ends on the extensions of the compressor pistons by means of a link articulated on the rocker arm on the one hand and on the relevant piston extension on the other and extending essentially in the axial direction of the associated compressor cylinder.
  • the handlebars perform slight pivoting movements around the articulation points on the piston extensions during the upward and downward movement of the compressor pistons.
  • the links connecting a piston extension to a rocker arm end are articulated at one end by means of a ball joint and at the other end by means of a bearing pin.
  • a structurally simple solution of this development consists in that the ends of the link on the piston extension side are provided with a bearing ball and the latter are received in bearing pans of the piston extensions.
  • the ends of the rocker arms can be designed as toothed segments and toothed racks which mesh with them can be arranged on the piston extensions.
  • Another important embodiment of the invention is characterized by an external drive derived from a camshaft, the stage piston of the fuel compressor which is positively coupled in opposite directions by means of a rocker arm, and which acts in addition to the loads acting from the combustion chambers of the working cylinders the larger areas of the stepped piston act on the latter.
  • the external drive can have a rocker arm driven by tappets and bumpers, and the latter and the rocker arm which provides the positive control of the stepped piston can be arranged in a rotationally fixed manner on a common bearing axis, so that the drive movements acting on the rocker arms belonging to the external drive act directly on the positive coupling the stepped piston are transmitted by two fuel compressors assigned to one another.
  • the external drive for each fuel compressor comprises a rocker arm driven by the camshaft and engaging the piston extension of the respective stepped piston, which rocker arm is then in a suitable operative connection with its associated stepped piston.
  • rocker arms belonging to the external drive derived from the camshaft, can be driven in a known manner via tappets and bumpers, or also from an overhead camshaft, wherein the rocker arms acting on the piston extensions of the fuel compressors can then be equipped with a roller as a cam disk follower.
  • the ends of the rocker arms which convey the external drive and which face away from the stepped piston of the fuel compressor are mounted in adjustable articulation points, for example on tappets which are adjustable with respect to the articulation point.
  • the configuration with an additional external drive of the stepped piston derived from the camshaft can also, according to another development of the invention, by a hydraulically acting external drive, each with a pump driven by the camshaft and in each case one that is operatively connected to a pump via a hydraulic line and engages a piston extension Hydraulic cylinder be characterized in such a way that with each working stroke of the feed pump driven by the camshaft, the hydraulic cylinder assigned to the latter is acted upon, which acts directly on the piston extension of a stepped piston and thereby drives it in the opposite direction to the other positively coupled stepped piston. It has proven to be advantageous if an adjustable attenuator is switched on in each of the hydraulic lines.
  • the angle of rotation of the camshaft relative to the crankshaft of the engine can also be adjustable and finally the cams imparting the external drive can also be designed in such a way that the fuel supply to the combustion chambers takes place in accordance with a predetermined law.
  • the internal combustion engine according to the invention is equally executable as a two-stroke and a four-stroke engine.
  • the internal combustion engine illustrated in FIGS. 1 to 5 is an air-cooled two-cylinder two-stroke engine 10 with working cylinders 11, 11 'arranged side by side in parallel and pistons 12, 12' working in opposite directions.
  • opening openings 13 for combustion air or a fuel-air mixture and outflow openings 14 for exhaust gases which break through, open out and which are controlled in a known manner from the upper edges of the working pistons 12, 12 ', which, however, is of no further interest here.
  • a cylinder head 16 which closes this on the upper side, is accommodated on the working cylinders.
  • the cylinder head comprises a cylinder head plate 18 screwed in a known manner to the working cylinders with the interposition of cylinder head gaskets 17, in which a piston compressor 20, 20 'for compressing and supplying fuel to the combustion chambers of the working cylinders is arranged coaxially with each working cylinder.
  • This can be gaseous fuel, a fuel-air mixture, but also a mixture of fuel and combustion gases, natural gas or hydrogen, without exhaustively listing the mixtures that can be used.
  • the cylinder liners are screwed into recesses 23, 23 'which extend coaxially to the two working cylinders 12, 12' through the cylinder head plate 18.
  • the stepped pistons 22, 22 'accommodated in the cylinder liners each have a piston section 27, 27' facing the associated working cylinder, which is guided in the enlarged cylinder bore 25, 25 'in a fluid-tight manner, and a piston shaft 28 which is smaller in diameter than this , 28 ', which is guided in the bore section 24, 24' of the compressor cylinder remote from the respective working cylinder in a fluid-tight manner.
  • the compressor pistons are stepped pistons and the compression spaces 30, 30 'for compressing the fuel are located in the region of the enlarged cylinder bores 25, 25' of the cylinder liners, which are closed off by the piston section 27, 27 'on the side pointing toward the respective working cylinder are, which has a larger diameter than the piston shaft 28, 28 '.
  • the compressor pistons 22, 22 'of the fuel compressors 20, 20' assigned to the two working cylinders 11, 11 'on the cylinder head side are positively coupled in opposite directions by means of a rocker arm arrangement 32.
  • This positive coupling is provided by a rocker arm 33 which is pivotally mounted on a bearing bracket 35 symmetrically about the axes of the working and compressor cylinders about a bearing axis 34.
  • the bearing bracket 35 is in turn arranged vertically adjustable on stud bolts 36, 36 'screwed to the cylinder head plate 18 and forms the bearing axis 34 for the rocker arm 33, which extends at right angles to the cylinder axes.
  • the stepped pistons 22, 22 'of the fuel compressors 20, 20' are articulated to the ends 38, 38 'of the rocker arm which are distant from the mentioned bearing axis.
  • the articulation mediate journals 40, 40 ' which penetrate the extensions mentioned and the ends of the rocker arms.
  • eccentric bearings 43, 43 ' are accommodated, which in turn are penetrated by the bearing journals 40, 40', which are otherwise fixed in the fork-like extensions 39, 39 'of the piston shafts 28, 28'.
  • the eccentric bearings 43, 43 ' experience a limited rotation in the bearing recesses 42, 42' when the stepped pistons move up and down. This automatically avoids constraints that would otherwise have to occur in the articulation points of the rocker arm ends on the compressor pistons because the rocker arm ends move on circular arc pieces.
  • wall sections 45 extend from the cylinder head plate 18 screwed to the working cylinders and enclose a cavity 46 which receives the rocker arm arrangement 32 and which is closed at the top by means of a cover 47 screwed to the said wall sections.
  • the wall sections 45 Symmetrical to the fuel compressors 20, 20 'accommodated in the cylinder head, the wall sections 45, which extend upward from the cylinder head plate 18, are pierced by air guide channels 48, 48'.
  • a fuel-air mixture can also be introduced into the working cylinder 11, 11 ', but this does not change the mode of operation of the internal combustion engine.
  • While one air duct 48 is connected to an air supply line 49, the other air duct 48 'opens into a manifold 50 which extends in an arc downwards into the area of the working cylinders 11, 11' and in turn to the air inlet openings 13 of the working cylinders in Connected branching part 51 is connected.
  • the combustion air flowing into the working cylinders 11, 11 'depending on the movement of the working pistons 12, 12' is passed through the space 46 of the cylinder head which receives the rocker arm arrangement 32.
  • An injection nozzle 52 for injecting lubricating oil into the combustion air also opens into the air inlet duct 48 connected to the air supply line 49.
  • the lubricating oil particles carried in the combustion air can also lubricate the parts in the crankcase of the internal combustion engine.
  • the cylinder head plate 18 and / or the cylinder liners 21, 21 'of the fuel compressor 20, 20' are approximately in the middle of the longitudinal extension of the cylinder bores 24, 24 'leading the piston shafts 28, 28' with radial Provided annular grooves 54, 54 'and in each case in the area of these annular grooves a transverse bore 55, which extends through the cylinder head plate 18, opens into which the supply line 65 for gaseous or vaporized fuels opens or gas admixtures, as well as the feed line 66 for liquid fuels.
  • the gaseous and / or liquid fuels can also be combined in another way and then enter the transverse bore 55 together.
  • annular grooves 53, 53 'and longitudinal grooves 58, 58' are pierced into the piston shafts, each of which ends on the side facing away from the associated working cylinder in front of the piston ring received on the respective piston shaft and extends by such a dimension
  • the compression spaces 30, 30 'of the fuel compressors are in communication with the annular groove 54, 54' inserted into the cylinder liners when the compression pistons 22, 22 'are in their lower positions.
  • This position of the compressor pistons is shown by the left halves of FIGS. 2 and 3.
  • the ends of the piston sections 27, 27' facing the enlarged pistons reach Longitudinal grooves 58, 58 ', which form overflow channels, in the region of the cylinder bores 24, 24' which guide the piston shafts, so that the compression spaces 30, 30 'of the piston compressors of the annular groove 54, 54 'providing the fuel supply in the cylinder liners are blocked.
  • FIGS. 2 and 3 show the working piston 12 of the - in FIG. 2 left - working cylinder 11 in its lowest position, in which the exhaust gas outlet opening 14 and the air inlet openings 13 are open.
  • the arrangement of these openings shows that when the working piston 12 descends, the exhaust gas outlet opening 14 is released first, and the air inlet openings 13 are only opened when the working piston continues to decline. Accordingly, after the exhaust gas outlet opening 14 has been released, the exhaust gases flow out of the combustion chamber of the working cylinder and out via a connected exhaust gas line 60, 60 'before the working piston clears the air inlet openings 13 and fresh air enriched with injected lubricating oil flows into the working cylinder, with displacement of remaining residual gases.
  • the stepped piston 22 of the fuel compressor 20 assigned to this working cylinder is also in its lowermost position, in which the annular groove 54 in the cylinder bushing 21, which is not connected to a fuel line, is shown in FIG Radial bores 57, the annular groove 53 and the longitudinal grooves 58 in the piston skirt are connected to the compression space 30 of the fuel compressor.
  • the compressor piston 22 has from the moment in which the lower ends of the longitudinal grooves 58 have run over the upper end of the compression space 30, fuel is sucked into the compression space.
  • Fig. 2 shows that when the working piston 12 of the one working cylinder 11 and the corresponding step piston 22 of the fuel compressor 20 associated with this working cylinder are at the bottom, the working piston 12 'of the other working cylinder 11' and accordingly also the step piston 22 'of the associated fuel compressor 20' in it stand in the upper position.
  • FIG. 6 illustrates the articulation of a rocker arm end 138 to the extension 139 of a stepped piston 122 via a sliding block 170, which is received in a reciprocating manner in an elongated hole 171 arranged at the end of the rocker arm 133 and extending in the longitudinal direction of the rocker arm.
  • the sliding block is otherwise penetrated by a bearing pin 140 which is fixedly mounted on the extension of the stepped piston and thus conveys the actual articulation point of the stepped piston to the rocker arm.
  • the embodiment according to FIG. 7 differs from the embodiment according to FIG. 6 in that a link 274 is arranged between the end 238 of the rocker arm 233 and the shaft of the stepped piston 222 of the fuel compressor and equally with the rocker arm end and with the stepped piston extension by means of a bearing pin each 240, 275 is articulated.
  • This link extends essentially in the direction of the axis of the compressor cylinder and thus in the direction of movement of the stepped piston.
  • the end 338 of the rocker arm 333 is connected to the extension of the stepped piston 322 by means of a link 374 articulated via a bearing pin 375 and a bearing ball 377 received in a ball socket 376 of the stepped piston extension.
  • the bearing ball 377 is held in the ball socket 376 by means of a cap 378 screwed onto the stepped piston extension, which is designed in the manner of a union nut.
  • a extending from the bearing ball 377 shaft 379 penetrates the cap 378 and is with the Bearing pin 375 distal end of the handlebar 374 screwed and secured by a lock nut 380.
  • the stepped piston of the fuel compressor can be rotated about its longitudinal axis.
  • the stepped piston On its side facing the combustion chamber of the associated working cylinder, the stepped piston has an obliquely extending control edge 382, by means of which, by rotating the stepped piston about its longitudinal axis, the timing of the release of the overflow channels from the compression chamber of the fuel compressor to the combustion chamber of the assigned working cylinder and thus a control of the fuel supply to the combustion chamber of this working cylinder and control of the compression and heating of the fuel is possible.
  • the extension of the stepped piston 422 is equipped with a toothed rack 480 and the end of the rocker arm 433 is designed as a toothed segment 481 interacting with this toothed rack.
  • the center of the pitch circle of the toothed segment lies in the rocker arm pivot axis, so that in this embodiment there are no measures required to prevent constraints in the rocker arm movement.
  • the stepped piston of the two fuel compressors which is positively coupled by means of a rocker arm that can be pivoted about a bearing axis, is driven solely by the mutual action of its surfaces pointing toward the combustion chamber of the respective working cylinder.
  • FIG. 10 shows an embodiment with an external drive the positively coupled stage piston from two fuel compressors assigned to one another, derived from a camshaft 500 of the internal combustion engine.
  • the external drive serves to support the compression of the fuel by the piston compressors, stabilizes their movements and causes exact control of the combustion process.
  • the rocker arm that provides the positive coupling of the stepped piston is received in a rotationally fixed manner on a bearing axis 534, on which a further rocker arm 501 is arranged at an axial distance from this rocker arm.
  • This second rocker arm is driven in a manner known per se by the camshaft 500 provided with eccentric cams 502, 502 'via bumpers 503, 503' and tappets 504, 504 'with rollers 505, 505' as cam followers.
  • the drive of the second rocker arm 501 which is derived from the camshaft 500, is transmitted to the stepped piston in view of its torsionally rigid connection with the rocker arm which provides the positive coupling of the stepped piston and thus acts to support the loading of the respective actuating surface of the compressor pistons pointing to the combustion chamber of the associated working cylinder.
  • the embodiment according to FIG. 11 also derives from a camshaft 600 of the internal combustion engine has an external drive which, by the way, a stepped piston 622, 622 ', which is otherwise positively coupled by means of a first rocker arm 633, in such a way that in each case on the extension of a stepped piston another rocker arm 601, which can be pivoted about a pivot axis 608, engages, which in turn has a bumper 603 and one Tappet 604 is driven with a follower 605 engaging eccentric cam 602 of camshaft 600.
  • the external drive of the second stepped piston is designed in the same way and the further rocker arm 601 'assigned to this external drive is received on the same bearing axis 608 as the rocker arm 601 illustrated in the drawing and is driven by a cam 602'.
  • FIG. 12 shows an alternative drive to FIG. 11, which in turn has a stepped piston 722, 722 'which is positively coupled via a rocker arm 733 and which is derived from an overhead camshaft 700.
  • the rocker arm 701 illustrated in the drawing engages with one end on the extension of the step piston in question and is pivotally mounted at its other end by means of a pivot axis 708 on an adjustable plunger 707.
  • an idler roller 705 cooperating with the eccentric cam 702 of the camshaft 700 in question is arranged on the latter.
  • the external drive acting on the second stage piston of the fuel compressors assigned to one another in pairs is designed in the same way, but lies behind the rocker arm arrangement illustrated in the drawing and is driven by a cam 702 ′.
  • FIG. 13 illustrates such an external drive with a hydraulic transmission system.
  • the tappets 804, 804 ' which interact with the eccentric cams 802, 802' of the camshaft 800 via idler rollers 805, 805 ', are designed as hydraulic pumps and are each operatively connected via hydraulic lines 809, 809' to hydraulic cylinders 810, 810 ', which are directly connected to the extensions which engage compressor pistons 822, 822 'which are positively coupled by means of a rocker arm 833 pivotally mounted about a rocker arm 834 and drive them in dependence on their hydraulic medium loading.
  • rocker arm ends are articulated to the extensions of the compressor pistons in the manner explained above in connection with FIG. 6 via sliding blocks accommodated in longitudinal guides.
  • Each of the hydraulic fluid systems is additionally equipped with an adjustable damper 811, 811 'and the two hydraulic systems are connected to a common hydraulic fluid supply line 812 via check valves 813, 813', which allow the systems to be filled with hydraulic fluid, the latter, however, in the direction of the supply line cordon off.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
EP91102426A 1990-04-12 1991-02-20 Kolbenbrennkraftmaschine Expired - Lifetime EP0451466B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4011862 1990-04-12
DE4011862A DE4011862C2 (de) 1990-04-12 1990-04-12 Kolbenbrennkraftmaschine

Publications (2)

Publication Number Publication Date
EP0451466A1 EP0451466A1 (de) 1991-10-16
EP0451466B1 true EP0451466B1 (de) 1994-01-19

Family

ID=6404288

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91102426A Expired - Lifetime EP0451466B1 (de) 1990-04-12 1991-02-20 Kolbenbrennkraftmaschine

Country Status (7)

Country Link
US (1) US5136995A (uk)
EP (1) EP0451466B1 (uk)
JP (1) JPH04228871A (uk)
DE (1) DE4011862C2 (uk)
ES (1) ES2049054T3 (uk)
RU (1) RU1838642C (uk)
UA (1) UA13128A (uk)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106285783A (zh) * 2015-05-19 2017-01-04 高阳 水平对置气缸对置活塞往复汽轮机气马达直线发电机

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4334533A1 (de) * 1993-10-09 1995-04-13 Kloeckner Humboldt Deutz Ag Gemischbildungs- und Brennverfahren für eine Dieselbrennkraftmaschine und Dieselbrennkraftmaschine zur Durchführung des Verfahrens
IT1269717B (it) * 1994-02-02 1997-04-15 Piaggio Veicoli Europ Disposizione compatta di testata per motori a combustione interna,in particolare a due cilindri
CN106285934B (zh) * 2015-05-19 2019-11-08 高阳 一种二冲程均质压燃往复式直线发动机
CN107228060B (zh) * 2016-03-24 2019-03-22 王佐良 摇臂式双缸打抽气机

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL19047C (uk) * 1900-01-01
DE182649C (uk) *
FR431809A (fr) * 1911-06-27 1911-11-21 Antoine Jean Baptiste Jaubert Moteur à explosion à détente complète à deux pistons
GB103470A (uk) * 1916-01-17 1917-10-18 Binche Georges
GB181500A (en) * 1921-03-16 1922-06-16 Nelson Edward Davies Improvements in or relating to internal combustion engines
DE377318C (de) * 1921-12-04 1923-06-16 Moteurs Salmson Systeme Canton Drehgelenk fuer den um einen zylindrischen Zapfen schwingenden Ventilhebel von Explosionsmotoren
US1679794A (en) * 1925-11-09 1928-08-07 Herman A Schatz Valve gear
US2230920A (en) * 1936-08-31 1941-02-04 Wirtsen Ernst Injection valve for internal combustion engines
US2385239A (en) * 1943-02-08 1945-09-18 Samuel A Unsworth Diesel engine fuel injector
DE898825C (de) * 1950-08-02 1953-12-03 Gertrud Schnuerle Zweitakt-Brennkraftmaschine
US2799263A (en) * 1954-11-24 1957-07-16 Louis O French Fuel injection apparatus
DE2826807A1 (de) * 1978-06-19 1979-12-20 Werner Mayer Verfahren zum betreiben einer brennkraftmaschine und brennkraftmaschine zum durchfuehren dieses verfahrens

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106285783A (zh) * 2015-05-19 2017-01-04 高阳 水平对置气缸对置活塞往复汽轮机气马达直线发电机
CN106285783B (zh) * 2015-05-19 2019-10-29 高阳 水平对置气缸活塞往复式汽轮机

Also Published As

Publication number Publication date
EP0451466A1 (de) 1991-10-16
UA13128A (uk) 1997-02-28
ES2049054T3 (es) 1994-04-01
RU1838642C (ru) 1993-08-30
US5136995A (en) 1992-08-11
DE4011862A1 (de) 1991-10-17
JPH04228871A (ja) 1992-08-18
DE4011862C2 (de) 1995-04-27

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