RO104187B1 - Internal combustion engine - Google Patents
Internal combustion engine Download PDFInfo
- Publication number
- RO104187B1 RO104187B1 RO14718991A RO14718991A RO104187B1 RO 104187 B1 RO104187 B1 RO 104187B1 RO 14718991 A RO14718991 A RO 14718991A RO 14718991 A RO14718991 A RO 14718991A RO 104187 B1 RO104187 B1 RO 104187B1
- Authority
- RO
- Romania
- Prior art keywords
- axles
- piston
- bolts
- connecting rod
- pistons
- Prior art date
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 13
- 230000033001 locomotion Effects 0.000 claims abstract description 17
- 230000006835 compression Effects 0.000 claims abstract description 6
- 238000007906 compression Methods 0.000 claims abstract description 6
- 230000001131 transforming effect Effects 0.000 claims description 6
- 230000010355 oscillation Effects 0.000 claims description 5
- 238000005461 lubrication Methods 0.000 claims description 2
- 238000007789 sealing Methods 0.000 claims description 2
- 230000005540 biological transmission Effects 0.000 abstract description 2
- 230000003137 locomotive effect Effects 0.000 abstract description 2
- 230000009466 transformation Effects 0.000 abstract description 2
- 230000007246 mechanism Effects 0.000 description 8
- 238000010276 construction Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000003546 flue gas Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
- F02B75/222—Multi-cylinder engines with cylinders in V, fan, or star arrangement with cylinders in star arrangement
-
- 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
-
- 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
- F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B2075/1804—Number of cylinders
- F02B2075/1816—Number of cylinders four
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Transmission Devices (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
Invenția se refera la un motor cu ardere internă cu ciclul funcțional îh doi sau patru timpi, cu aprindere prin scînteie sau compresie, cu preluare centralizată a forței de presiune de la 5 pistoane, destinat utilizării în cele mai diverse domenii - industria de automobile și tractoare, locomotive, nave, mașini agricole autopropulsate, mașini pentru construcții și construcții de dru- 10 muri, grupuri electrogene, etc.The invention relates to an internal combustion engine with a functional cycle of two or four times, with spark or compression ignition, with centralized take-over of the pressure force from 5 pistons, intended for use in the various fields - the automotive and tractor industries. , locomotives, ships, self-propelled agricultural machines, construction machinery and 10-wall construction, generator sets, etc.
Sînt cunoscute motoare cu ardere internă care folosesc pentru transformarea mișcării de translație în mișcare de rotație mecanisme bielă-manivelă 15 individuale, cuplate la fiecare piston, la care dimensionarea mecanismului se face pe baza solicitărilor maxime care apar pe durata timpului activ de destindere a gazelor arse. Un asemenea 20 mecanism prezintă dezavantajul că în perioada timpilor pasivi de lueru-admise, compresie, evacuare-mecanismul de transformare a mișcării devine excesiv de dimensionat și constituie un 25 important consumator de energie pentru menținerea în mișcare a unor mase inerțiale real tiv mari.Internal combustion engines are known to use for transforming the movement of translation into rotational movement crank mechanisms 15 individual, coupled to each piston, to which the dimensioning of the mechanism is made based on the maximum demands that appear during the active time of flue gas release. . Such a 20 mechanism presents the disadvantage that during the passive times of lueru-admitted, compression, evacuation-the mechanism of transformation of the movement becomes excessively dimensioned and constitutes an important 25 energy consumer for maintaining in motion some really large inertial masses.
Se cunosc, de asemenea, motoare cu ardere internă cu mecanisme de 30 transformare a mișcării de translație în mișcare de rotație care constau din soluții tehnice ce permit preluarea centralizata a forțelor de presiune, și care au la bază came cu profil complex, 35 montate fix pe arborele motor, pe suprafața cărora apasă role situate în punctele de articulație ale elementelor de legătură dintre pistoane. Asemenea soluții prezintă dezavantajul ca sînt ca- 40 racterizate prin presiuni mari de contact dintre role și profilul camei și prin viteze periferice importante la role, ceea ce impietează asupra eficienței transformării mișcării de translație în 45 mișcare de rotație.Also known are internal combustion engines with mechanisms for transforming the translation movement into rotational motion, which consist of technical solutions that allow the centralized take-over of pressure forces, and which are based on complex profile cams, 35 fixedly mounted. on the motor shaft, on the surface of which it presses rollers located at the points of articulation of the connecting elements between the pistons. Such solutions have the disadvantage that they are characterized by high contact pressures between the rollers and the cam profile and by important peripheral speeds on the rollers, which impinges on the efficiency of transforming the translation movement into 45 rotational motion.
Scopul invenției este creșterea eficienței transformării mișcării de trans lație a pistoanelor în mișcare de rotație a arborelui cotit.The object of the invention is to increase the efficiency of transforming the movement of the piston transition into a rotating shaft movement.
Problema pe care o rezolvă invenția este de a concepe un motor cu ardere internă cu o largă aplicabilitate practică, dotat cu un mecanism simplu, robust și cu proprietăți cinematice și dinamice adaptate scopului propus de transformare eficientă a energiei rezultată din arderea amestecului carburant în lucru mecanic util la arborele motor.The problem solved by the invention is to design an internal combustion engine with a wide practical applicability, equipped with a simple, robust mechanism and with kinematic and dynamic properties adapted to the proposed purpose of efficient conversion of energy resulting from combustion of fuel into mechanical work. useful for the motor shaft.
Prezenta invenție înlătură dezavantajele de mai sus prin aceea că mijloacele punților de legătură se articulează prin intermediul unor bolțuri de punte cu niște diagonale de balans ce oscilează coaxial cn fusurile palier ale arborelui cotit, pe manetonul căruia se așază Jiber prin intermediul unor cuzineți capul unei biele, iar piciorul bielei se prinde liber de unul din bolțurile de piston, distanța dintre axele bolțurilor de punte măsurată de- a lungul proiecțiilor diagonalelor de balans pe planul cercului de referință este egală cu diametrul acestui cerc, mărime la care se raportează cu un raport echiunitar și lungimea punților de legătură măsurată între axele bolțurilor de piston, iar centrele de oscilație ale punților de legătură situate pe axele bolțurilor de punte și centrele de oscilație ale diagonalelor de balans situate pe axa fusurilor palier a arborelui cotit sînt așezate echidistant față de bolțurile de piston de care le despart distanțe egale cu raza cercului de referință.The present invention removes the above disadvantages by the fact that the means of the connecting axles are articulated by means of axle bolts with balancing diagonals coaxially oscillating at the crankshaft shaft bearings, on the handle which Jiber sits through a bearing. , and the leg of the connecting rod is free from one of the piston bolts, the distance between the axes of the axles measured along the projections of the balance diagonals on the plane of the reference circle is equal to the diameter of this circle, the size of which is related to an equitable ratio and the length of the connecting axes measured between the axes of the piston pins, and the centers of oscillation of the connecting axles located on the axes of the axles and the centers of oscillation of the diagonals of the balances located on the axis of the crankshaft of the crankshaft are equidistant from the piston pins from which they come rt distances equal to the radius of the reference circle.
Se dă în continuare un exemplu de realizare a invenției, în legătură cu fig.l și 2, care reprezintă:The following is an example of embodiment of the invention, in connection with FIGS. 2 and 2, which represents:
- fig.l, secțiune transversală prin motorul cu ardere internă care face obiectul invenției;FIG. 1 shows a cross-section through the internal combustion engine subject to the invention;
- fig.2, schema relațiilor geometrice din cadrul sfertului de cerc, utilizate, în cadrul invenției.- Figure 2, the schematic of the geometric relations within the quarter circle, used, within the invention.
Motorul cu ardere internă cu preluare centralizată a forței de presiune de la pistoane este format dintr-un bloc al cilindrilor 1, prevăzut cu un număr de cilindri de lucru 2, ca, de exemplu, patra cilindri dispuși radial în același plan, cu un decalaj de un sfert de cerc între axele lor, în fiecare din cilindri 2 se deplasează în mișcare de translație radială cîte un piston 3, prevăzut cu niște segmenți de foc, etanșare și ungere 4. Niște bolțuri. de piston 5 sînt montate fix in bosajele pistoanelor. Pe partea de mijloc a bolțurilor 5 se montează liber capetele unor punți de legătură 6, ale căror mijloace se articulează liber, prin intermediul unor bolțuri de punte 7, cu capetele a două diagonale de balans 8, montate cu mijlocul lor coaxial cu fusurile palier ale unui arbore cotit 9, cu posibilitate de oscilare.The internal combustion engine with centralized take-over of the piston pressure force consists of a cylinder block 1, provided with a number of working cylinders 2, such as, for example, four cylinders radially arranged in the same plane, with a gap by a quarter of a circle between their axes, in each of the cylinders 2, a piston 3 is moved in radial translation movement 3, provided with segments of fire, sealing and lubrication 4. Some bolts. of piston 5 are fixedly fixed in the piston bearings. On the middle of the bolts 5 the ends of connecting bridges 6 are freely mounted, the means of which are freely articulated, by means of axles 7, with the ends of two balance diagonals 8, mounted with their coaxial means with the bearing axles of of a crankshaft 9, with the possibility of oscillation.
Soluția propusă este fundamentată pe baza proprietăților segmentelor de dreaptă, tangente sau secante la circumferința sfertului de cerc, delimitate de razele extreme ale sfertului de cerc și de prelungirile acestora șî care fac cu aceste prelungiri unghiuri egale cu unghiul dintre raza corespunzătoare punctului de tangență sau punctului de intersecție al secantei și raza extremă cea mai apropiată, și anume: toate segmentele de dreaptă definite ea mai sus au lungimea constantă și egală cu diametral cercului; locul geometric al mijloacelor segmentelor de dreaptă se află pe circumferința sfertului de cerc; locul geometric al extremităților seg' mentelor de dreapta se află pe razele extreme ale sfertului de cerc și pe prelungirile acestora către exteriorul cercului.The proposed solution is based on the properties of the right, tangent or secant segments at the circumference of the quarter circle, delimited by the extreme radii of the quarter circle and by their extensions and which make with these extensions angles equal to the angle between the radius corresponding to the point of tangency or point of intersection of the secant and the nearest extreme radius, namely: all the straight segments defined above have a constant length and equal to the diameter of the circle; the geometric place of the means of the right segments is on the circumference of the quarter circle; the geometric place of the extremities of the right segments is on the extreme radii of the quarter circle and on their extensions to the outside of the circle.
În cadrul mecanismului descris, de legătură între pistoane, proprietățile menționate mai sus se concretizeze în aceea ca; lungimile diagonalelor de ba lans 8, măsurate pe proiecția lor în planul de așezare a cilindrilor între axele bolțurilor de punte 7 și lungimile punților de legătură 6, măsurate pe proiecția lor în planurile axelor bolțurilor de piston 5, sînt egale, atît între ele, cit și cu diametral cercului de referință, situat cu central său pe axa fusurilor palier a arborelui cotit 9, în planul de așezare a cilindrilor de lucru 2, și a cărei circumferință trece prin axele bolțurilor de punte 7.Within the described mechanism, of connection between the pistons, the properties mentioned above will materialize in that as; the lengths of the ball diagonals 8, measured on their projection in the plane of placing the cylinders between the axles of the axles of the bridge 7 and the lengths of the connecting axles 6, measured on their projection in the planes of the axes of the piston pins 5, are equal, both between them, as and with the diameter of the reference circle, located with its central axis on the axis of the crankshaft of the crankshaft 9, in the plane of position of the working cylinders 2, and whose circumference passes through the axles of the axles of the bridge 7.
Prin intermediul bolțului 5 al unuia din pistoanele 3, se prinde liber piciorul unei biele 10, iar capul acesteia se montează liber pe manetonul arborelui cotit 9, prin intermediul unor cuzineți de bielă 11. Fusurile arborelui cotit 9, așezate în niște cuzineți de palier 12, se prind liber în blocul cilindrilor 1, alcătuit, din patru elemente de bloc identice, asamblate fix între ele cu organe de asamblare.By means of the bolt 5 of one of the pistons 3, the leg of a connecting rod 10 is freely gripped, and its head is freely mounted on the crankshaft shaft lever 9, by means of connecting rod bearings 11. The crankshaft spindles 9, placed in bearing bearings 12 , are freely clamped in the cylinder block 1, consisting of four identical block elements, fixedly assembled together with assembly members.
Preluarea centralizată a forței de presiune de la pistoane pe o singură bielă, conform soluției constructive prezentate, crează condiții favorabile pentru trecerea la raporturi cursă piston/diametru cilindru subunitare.The centralized take-off of the pressure force by the pistons on a single connecting rod, according to the presented constructive solution, creates favorable conditions for switching to piston stroke / subunit cylinder diameter ratios.
în funcție de tipul aprinderii - prin scinteie sau prin compresie - și de numărul timpilor de lucra, celelalte componente ale motorului, precum și echipamente auxiliare sînt similare cu cele ale motoarelor actuale, cu adaptările specifice structurii constructive a motorului propus spre brevetare. Excepție face mecanismul de distribuție, la care închiderea și deschiderea supapelor de admișie și evacuare este comandată în cazul motorului în patru timpi de două came, așezate pe un ax cuplat coaxial cu arborele motor 9, în partea opusă volantei, cu un raport de transmisie de 1/2. în varianta motorului în doi timpi cu o singura supapă, pe cilindru se poate utiliza o singura cama dispusă direct pe arborele motor.depending on the type of ignition - by spark or compression - and by the number of working times, the other components of the engine, as well as auxiliary equipment are similar to those of the current engines, with the specific adaptations to the constructive structure of the proposed engine for patenting. Exception is the distribution mechanism, in which the closing and opening of the inlet and outlet valves is controlled in the case of the four-stroke engine of two cams, located on a shaft coupled coaxially with the motor shaft 9, on the opposite side of the flywheel, with a transmission ratio of 1/2. In the two-stroke engine version with a single valve, a single cam disposed directly on the motor shaft can be used on the cylinder.
Funcționarea motorului cu ardere internă, cu preluare centralizată a forței de presiune de la pistoane, pre zinta următoarele particularități: prin arderea amestecului carburant în camerele dc ardere, presiunea exercitată pe suprafața activă a pistoanelor 3 determină o forță de presiune care, prin intermediul boburilor de piston 5, sc transmite, de la pistoanele fără bielă prin intermediul punților de legătură 6 la bolțul pistonului cu bielă, iar de aici, prin intermediul bielei 10, la arborele cotit 9, iar de la pistonul cu bielă se transmite direct prin biela 10 la arborele cotit 9.The operation of the internal combustion engine, with centralized take-over of the pressure force from the pistons, presents the following particularities: by burning the fuel mixture in the combustion chambers, the pressure exerted on the active surface of the pistons 3 determines a pressure force that, through the coils of piston 5, sc transmits, from the pistons without connecting rod through the connecting axles 6 to the bolt of the connecting rod piston, and from here, through the connecting rod 10, to the crankshaft 9, and from the connecting rod piston is transmitted directly through the connecting rod 10 to crankshaft 9.
în ambele cazuri, prin biela 10 se transmite Ia arborele cotit 9, selectiv, numai acea parte a forței de presiune care se transformă în moment de rotație util la arborele motor, iar partea necesară creării timpilor pasivi de lucru - admisie, compresie, evacuare - se transmite direct prin intermediul punților de legătură 6, de la pistonul activ la pistoanele care realizează astfel de timpi. Componența forței de presiune care împinge pistonul 3 pe suprafața interioară a cilindrului 2 dispare complet la pistoanele fără bielă, iar de la pistonul cu bielă, prin punțile dc legătură 6, aceasta se divide concomitent la toți cei patru cilindri, reprezentînd numai circa o pătrime din forța similară care apare la motoarele echipate cu bielă individuale. De asemenea, datorită faptului că toate cursele la bielă sînt. active, dar cu schimbare de sens, locul de acțiune al forței normale la cilindru nu mai este același, reprezentînd succesiv doua zone opuse pe suprafața laterală a cilindrilor.In both cases, through the connecting rod 10 is transmitted to the crankshaft 9, selectively, only that part of the pressure force that turns into a useful moment of rotation at the motor shaft, and the part necessary to create the passive working times - intake, compression, evacuation - it is transmitted directly through the connecting axles 6, from the active piston to the pistons that perform such times. The component of the pressure force that pushes the piston 3 on the inner surface of the cylinder 2 completely disappears at the pistons without connecting rod, and from the piston with connecting rod, through the axles dc connection 6, it is divided simultaneously to all the four cylinders, representing only about a quarter of the similar force that appears in the engines equipped with individual connecting rods. Also, due to the fact that all connecting rod races are. active, but with a change of meaning, the place of action of the normal force on the cylinder is no longer the same, successively representing two opposing areas on the lateral surface of the cylinders.
Invenția prezintă următoarele avan taje:The invention has the following advantages:
- asigură creșterea eficienței transformării mișcării de translație a pistoanelor în mișcare de rotație a arborelui cotit;- it ensures the efficiency of transforming the translation movement of the pistons into rotational movement of the crankshaft;
- creează condiții optime pentru trecerea la volume de lucru joase, cu raporturi cursă piston/diametru cilindru subunitate;- creates optimal conditions for switching to low working volumes, with piston stroke / cylinder diameter subunit ratios;
- permite diminuarea efectelor componentei forței de presiune care împinge pistonul pe suprafața interioară a cilindrului;- it allows to diminish the effects of the component of the pressure force that pushes the piston on the inner surface of the cylinder;
- mărește durata de funcționare a motorului pînă la apariția uzurilor maxime admisibile.- Increases engine life until maximum permissible wear occurs.
Claims (2)
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| RO14718991A RO104187B1 (en) | 1991-03-20 | 1991-03-20 | Internal combustion engine |
| PCT/RO1992/000006 WO1992016730A1 (en) | 1991-03-20 | 1992-03-19 | Internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| RO14718991A RO104187B1 (en) | 1991-03-20 | 1991-03-20 | Internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| RO104187B1 true RO104187B1 (en) | 1993-12-22 |
Family
ID=20128249
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| RO14718991A RO104187B1 (en) | 1991-03-20 | 1991-03-20 | Internal combustion engine |
Country Status (2)
| Country | Link |
|---|---|
| RO (1) | RO104187B1 (en) |
| WO (1) | WO1992016730A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5682844A (en) * | 1996-12-30 | 1997-11-04 | Wittner; John A. | Twin crankshaft mechanism with arced connecting rods |
| US8746206B2 (en) * | 2010-06-29 | 2014-06-10 | Matthew Byrne Diggs | Double-Acting Scotch Yoke assembly for X-engines |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1594045A (en) * | 1924-03-31 | 1926-07-27 | Caminez Harold | Cam engine |
| FR866060A (en) * | 1940-02-29 | 1941-06-16 | Four-sided detent motor | |
| US3274982A (en) * | 1964-09-23 | 1966-09-27 | To Yota Motors Company | Two-cycle two-cylinder internal combustion engine |
| US4093405A (en) * | 1977-02-02 | 1978-06-06 | William Stanley Brian | Fuel-operated device |
| DE2720357A1 (en) * | 1977-05-06 | 1978-11-16 | Werner Zink | Balanced IC engine with opposed pistons - has connection to crank by parallelogram linkage pivoted to pistons at diagonally opposite points |
-
1991
- 1991-03-20 RO RO14718991A patent/RO104187B1/en unknown
-
1992
- 1992-03-19 WO PCT/RO1992/000006 patent/WO1992016730A1/en not_active Ceased
Also Published As
| Publication number | Publication date |
|---|---|
| WO1992016730A1 (en) | 1992-10-01 |
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