GB2340201A - A reciprocating mechanism and an engine including the same - Google Patents
A reciprocating mechanism and an engine including the same Download PDFInfo
- Publication number
- GB2340201A GB2340201A GB9900247A GB9900247A GB2340201A GB 2340201 A GB2340201 A GB 2340201A GB 9900247 A GB9900247 A GB 9900247A GB 9900247 A GB9900247 A GB 9900247A GB 2340201 A GB2340201 A GB 2340201A
- Authority
- GB
- United Kingdom
- Prior art keywords
- reciprocating
- reciprocating member
- coupled
- rotary means
- crank
- 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- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
- F01B9/047—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with rack and pinion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
- F01B9/026—Rigid connections between piston and rod; Oscillating pistons
-
- 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
- F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
- F02B75/246—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type with only one crankshaft of the "pancake" type, e.g. pairs of connecting rods attached to common crankshaft bearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H21/00—Gearings comprising primarily only links or levers, with or without slides
- F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
- F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
- F16H21/18—Crank gearings; Eccentric gearings
- F16H21/34—Crank gearings; Eccentric gearings with two or more connecting-rods to each crank or eccentric
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transmission Devices (AREA)
Description
2340201 A RECIPROCATING MECHANISM AND ENGINE INCLUDING THE SAME.
The present invention relates to a reciprocating mechanism, and more particularly to an engine, such as an internal combustion engine, including such a mechanism.
Known reciprocating mechanisms include crank- mechanisms and io cam mechanisms. Internal combustion engines exclusively use crank mechanisms to translate their linear motion of a piston sliding up and down "in a barrel 'into rotation of an output shaft.
According to one aspect of the present invention, there is provided a reciprocating mechanism comprising of a reciprocating member, movable in a substantially linear reciprocating direction between two ends of travel, rotary means for coupling tangentially to the reciprocating member to translate linear movement of the reciprocating member into rotary motion, and reversing means for reversing the movement of the reciprocating member at the two ends of its travel 'in dependence of said rotary means.
According to a second aspect of the of the present invention, there is provided an engine including the reciprocating mechanism of the first aspect of the invention, in which a piston of the engine is provided on the reciprocating member.
Preferably, the rotary motion is in the same direction of rotation for both reciprocating directions.
The rotary means may comprise at least one gear wheel, the or each gear wheel being engageably coupled to the reciprocating member for only one reciprocating direction.
The rotary means may comprise at least one gear wheel of constant radius.
2 The rotary means may comprise two opposmig gear wheels, coupled to the reciprocating member and to each other for rotation in the same direction.
The rotary means may comprise of a constant breadth Cam and Follower coupled directly to the reciprocating member and to each other for rotation in the same direction.
The Constant breadth Cam and Follower member may be coupled io to a pendulum counter balance.
The reversing means may comprise of a crank mechanism coupled between the reciprocating member and rotary means.
The reversing means may include a cam and follower mechanism.
The cam may be coupled to the rotary means and the follower may be coupled to a rack and piion of the crank mechanism.
The crank mecham'sm may comprise two connecting rods, coupled to the reciprocating member at spaced locations on either side of the region of engagement of the reciprocating member with rotary means.
The coupling between the crank mechanism and the rotary means may be by way of a further crank mechanism.
A piston may be provided at each end of the reciprocating member. The or each piston may be rigidly mounted to the reciprocating member.
Figure 1 shows a front end Nriew, partially sectioned, of the apparatus embodying the first and second aspects of the present Figure 2 shows a plan Nriew of Figure 1.
3 5 Figure 3 shows a rear end view of Figure 1, of the gear mechanism and also the return mechanism.
3 Figure 4 shows an alternative embodiment of the return mechanism of Figure 3.
Figure 5 shows a perspective view of details of the return 5 mechanism of Figure 4.
Figure 6 shows a perspective view of the crank mechanism employed in the apparatus of Figures 1.2.3.
Figure 7 shows a perspective view of the reciprocating member I embodying the gear rack of 11. 12. slioNkm in Figures 1. 2.
Figure 8 shows a plan view of the Constant Breadth Cam member, coupled directly to the reciprocating member 1.
Figure 9 shows a plan view of a lightened constant breadth cam and its surface bearings Figure 10 shows a bearing which supports the cams surface bearings to the Follower member.
Figure 11 shows a perspective view of the Follower member with an alternative arrangement for bearing guides.
Figure 12 shows a pendulum counter balance.
Figure 13 shows an exploded perspective view of the reciprocating member and the Constant Breadth Cam member.
Figure 14 shows perspective front and rear views of the combined reciprocating member and Constant Breadth Cam member.
Figures 1.2.3 and 8 shoAA, a reciprocating mechanism embodying the first aspect of the present invention employed in an combustion engine and including a reciprocating member 1, connected to two pistons 2, one at each end, rotary means 3 and reversing means 4.
4 The reciprocating member I is a shaft embodying a rack, of gears 11.12 provided partially along its length on opposing longitudinal sides. Regions 13 which do not have any gear teeth are provided at each set of gear teeth. The reciprocating member I also includes means 15, such as a transverse hole or axle for attaching the gear rack 11.12, and also for attaching a connecting rod of an adjacently disposed crank mechanism thereto. Bearing blocks 16 are provided on both sides of gears 11.12 to mount reciprocating member I slidably in a fixed linear path for movement between two ends of travel. The reciprocating member I is io preferably made from a light alloy material and the rack from a high strength material, the member I shall be made as light as possible. The pistons 2 are preferably connected rigidly to the reciprocating member 1, one at each end, and this may be by way of a screw thread or pin and clip.
The rotary means 3 comprises two gear wheels 31 which are coupled to each other to rotate in the same direction at substantially the same rate, that is, at substantially the same angular velocity. These gears may be Sprag Clutch, Ramp and Roller type gears, which rotate in one direction and free wheel 'in the opposite direction, or they may be Segmented gears. In the case of segmented gears, having a gear portion 32 and a non-geared portion 33. The geared portion 32 are arranged engageably to couple the gear teeth IL 12 of the reciprocating member 1, whilst the non-geared portions 33 are arranged not to engage with these gear teeth 11. 12 at any time. Each gear wheel may have a bearing 16 1. As shown in Figure 2, on the same axis of each gear wheel 3 1, behind or in front of each gear portions 32.33. gears 34 are provided which engage with each other via an intermediate gear disposed therebetween.
The geared and non-geared portions 32.33 of each gear wheel 31 to engage the reciprocating member I in one of its two directions of travel and to enable the other gear wheel 31 to engage the reciprocating member 1 'in the opposite direction, whilst both gear wheels rotate together in the same sense.
Therefore, whilst one gear wheel 31 is arranged to engage its teeth 32 with teeth 11, for example, of the reciprocating member 1, the other io wheel 31 rotates without engagement, with the non-geared portions 33' passing over the teeth 12. At the two ends of travel of the reciprocating member, the gear wheels 31 are both disengaged from teeth 11,12. This disengagement is necessary if the gear wheels 31 are to be able to rotate at constant angular velocity, whilst reciprocating member I almost I instantaneously stops and reverses at each of its ends of travel. The Sprag Clutch and Ramp and Roller gears 3 1, may stay in engaged with gears 11. 12 of the reciprocating members I travel, as they will rotate in one direction of travel and free wheel around their axis on the return opposite direction of travel.
The intermediate gear wheel 35 provides an output for the mechanism and this may lead to a gear box (not shown "). It may allso be desirable to take the drive output from either of gear wheels 31; gear wheel 35 acting as an idler coupling gear wheel. desirably, the intermediate gear wheel 35 and the gear wheels 31 rotate with substantially constant angular velocity. This may require the reciprocating member I to move with constant speed between substantially both ends of its travel, whilst changing very quickly its direction of travel, and speed at each end. To give the reciprocating member I more time to stop an-d- accelerate at a lesser rate in the opposite direction at each end of travel to match the speed of the rotating gear wheels 31, the gear wheels 31 may both be out of engagement with teeth 11,12 for a short distance of travel of the reciprocating member I at each end. To allow the reciprocating member I to have a non-constant speed whilst giving a constant angular velocity output at gear wheel 3 5, the gear wheel I I may have varying radii which co-operate with teeth 11. 12 which are configured accordingly. A larger radius, with constant gear wheel ang gular velocity, will allow the reciprocating member I arrange tangentially to the gear wheel travel faster. This is preferably near the middle of each stroke. Conversely, a 6 smaller radius will allow the reciprocating member I to travel slower. This is preferably near the ends of its travel. The gear wheels employed in all cases, may of course, be helical gears which have high contact ratios.
Reversing means 4 are shown in Figures I to 3 as one arrangement or in Figures 1 to 4 as an alternative arrangement. In each case, the reversing means 4 'includes two connecting rods 41, a central crank 44 with two crank arms, and a reciprocating mechanism 38,39 which is coupled to the central crank 44. Refening additionally to Figure io 6, the connecting rods 41 are rotably mounted at one of their ends 42 to the reciprocating member I at the said two locations 15. Referring additionally to Figure 7, thereon and rotabably mounted to the crank 44 at their other ends 43. The crank arms are preferably arranged when the reciprocating member I is at either end of its travel as shown in Figure 1, such that a respective connecting rod 41 extends between the centre of the crank axis and the locations 15 on the reciprocating member 1. In this way, the crank 44 and connecting rods 41 prevent the piston 2 and reciprocating member I from moving further than beyond the desired ends of travel and colliding with the cylinder head 2 1 (only one shown) for each piston. The Reversing means 4 is operable to stop and reverse the reciprocatmig member I at each of its ends of travel. This is achieved by rotating the crank 44 from the position shown in Figure 1, clockwise, to draw the reciprocating member I to the left so that the distance between the connecting rod and crank axis is made to reduce, at the same time as the reciprocating member I reaches its limit of travel.
Figure 3 shows a mechamism 38 which causes the crank 44 to return when the reciprocating member I nears the ends of its travel. The mechanism 38 comprises a displacement cam 45 (constant breadth carn shown), rack and follower member 46, which is coupled to the crank 44 via a rack and pinion Joint 44 and 46. The cam surface 45 which is driven by coupled gear wheel 31 acts to displace the rack and constant breadth follower member 46, the displacement motion rotates crank piion 44 'into the desired synchronous rotation of the crank at each of the ends of travel of reciprocating member 1. Contact point between cam surfaces 45 and the rack and follower member 46 may have a roller bearing between them.
7 Figure 4 shows an alternative reciprocating mechanism, the mechanism 39 includes a further crank mechanism which couples the gear wheel 31 to the crank 44. As the gear wheel 31 rotate, reciprocating motion is imparted to a connecting rod member 47 which is provided with gear teeth 50. The thus generated reciprocal motion is synchronous with the desired rotation of the crank at each ends of travel of reciprocating member 1. The connecting rod member 47 is coupled to the crank via rack and pinion joint 44,47.
Figures 8-14 shows an alternative reciprocating mechanism 40 (omitting gears). The reciprocating mechanism 40 includes reciprocating member 1, wherein the geared section is replaced by shoulders 58 (refer to figures 8 and 13) which connect and couple against 57 of the Constant Breadth Follower member 51 (refer to figures 8.11.13 and 14). The Constant Breadth Follower member 51 transfers the linear motion of the reciprocating member I through to the surface bearings 53, which are supported by fitilher bearings 54 (fig 10) housed in the Constant Breadth Follower 51. The transferred motion along the surface bearings 53 against the Constant Breadth Cam 52 will displace against the Cams profile creating rotation and reciprocation of the follower as in (Rotary and reversing means 3 and 4). Rotary output may taken ftom the Cam shaft 59 (not shown in longitude). The Constant Breadth Follower 51 ma", be provided with bearing guides 55 w1iich can slide in a bearing mount (not shown), alternatively circular bearings may be attached 56 which slide on shafts (not shown). A counter balance pendulum 60 may be connected to the Constant Breadth Follower 51. As the mass ftom 53 moves to the right so the pendulum pivots around 61 and 62 moves to die left moving an = amount of mass 64 along a shaft 63, thus creating a counter balance (bearings and guides not sho-,Nm).
An internal combustion engine employing the above reciprocating mechanism may function 1Aith two or four stroke engine technology. Referring to Figure I as a starting position, a two stroke embodiment of an englMe functions as follows:
(1) both gear wheels 31 are rotating clockwise, combustion and explosion of fuel-air mixture causes the piston 2 and the reciprocating member I to accelerate to the left, aided by the clockwise rotation of the crank 44 and anti-clock-wise rotation of the right-hand-side connecting rod 41 from top dead-centre position, both sets of gears 31,11,12 are disengaged from each other; (11) the lower gear wheel 31 rotates with its non-geared portion moving under the leftwardly-moving teeth 12 of the reciprocating member 1, the upper gear wheel 31 now engages the teeth I I of the reciprocating member 1, as it matches the tangential speed of its geared portion 32, the crank mechanism 41, 44 moves freely to allow the reciprocating member I io to displace and ensures the teeth I I mesh with gear teeth 32 of the upper gear wheel 3 1; (111) the right-hand side piston is driven to the left, down its barrel, as the fuel-air mixture burns and escapes via an exhaust outlet, as the upper gear wheel is driven by teeth 11, the mixture in the left-hand side barrel starts to become compressed; (IV) the left-hand-side mixture is ftirther compressed and its respective connecting rod 41 and crank 44 approaches a top-dead-centre configuration, the geared portion 32 of the upper gear wheel 31 loses its engagement with teeth I I and the non-geared portion 33 of the lower gear wheel 31 nears its engagement with teeth 12, ignition of the compressed mixture takes place; and (N the crank mechanism 41, 44 reaches top-dead-centre and the reciprocating member I is brought to rest, both gear wheels 3 1 are disengaged from the teeth 11,12, the crank 44 is started to be rotated anti clockwise to return reciprocating member 1, ignition of mixture develops into combustion and explosion.
9
Claims (16)
1. A reciprocating mechamism comprising a reciprocating member, movable in a substantially linear reciprocating direction between two ends of travel, rotary means for coupling tangentially to the reciprocating member to translate linear movement of the reciprocating member into rotary motion, and reversing means for reversing the movement of the reciprocating member at the two ends of its travel in dependence upon the io rotation of said rotary means.
2. A mechanism as claimed in claim 1, wherein the rotary motion is in the same direction of rotation for both reciprocating directions.
3. A mechanism as claimed in claim I or 2, wherein the rotary means comprise at least one gear wheel, the or each gear wheel being engageably coupled to the reciprocating member for only one reciprocating direction.
4. A mechanism as claimed in 1,2 or 3, wherein the rotary means comprises at least one gear wheel of constant radius.
5. A mechanism as claimed in any preceding claim, wherein the rotary means comprises two opposing gear wheels, engageably coupled to the reciprocating member and to each other for rotation in the same di.rection,
6. A mechanism as claimed in any precedig claim, wherein the reversing means includes a cam and follower mechanism.
7. A mechanism as claimed in any preceding claim, wherein the reversing means comprise a crank mechanism coupled between the reciprocating member and then rotary means.
8. A mechanism according to claim 6, wherein the cam is coupled to the rotary means and the follower is coupled to a rack member and pinion of the crank mechanism.
9 A mechanism according to claim 6 to 8, wherein a constant breadth cam and follower be directly connected to the reciprocating member.
10. The mechanism as claimed in any one claims 6 to 8, wherein the crank mechanism comprises two connecting rods which are coupled to the reciprocating member at spaced locations on either side of the region of engagement of the reciprocating mernber with rotary means.
11. A mechanism as claimed in 6 or 10, wherein the coupling between the crank mechanism and the rotary means is by way of a ftu-ther crank mechanism.
12. An engine including the reciprocating mechanism of any preceding claim, in which a piston of the engine is provided on the reciprocating member.
13. An engine as claimed in 12, wherein a piston is provided at each end of the reciprocating member.
14. An engine as claimed in claim 12 or 13, wherein the or each io piston is rigidly mounted to the reciprocating member.
15. An internal combustion engine substantially as hereibefore described with reference to Figure I to 14 of the accompanying drawings.
16. A reciprocating mecharuism substantially as hereinbefore described with reference to Fioure I to 14 of the accompanying drawings.
$5
Priority Applications (11)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| ES99929515T ES2181452T3 (en) | 1998-06-26 | 1999-06-28 | MECHANISM OF ALTERNATIVE MOVEMENT AND ENGINE THAT UNDERSTANDS THE SAME. |
| CN99807884A CN1114054C (en) | 1998-06-26 | 1999-06-28 | Reciprocating machanism and engine including the same |
| EP99929515A EP1090236B1 (en) | 1998-06-26 | 1999-06-28 | A reciprocating mechanism and engine including the same |
| AU46307/99A AU4630799A (en) | 1998-06-26 | 1999-06-28 | A reciprocating mechanism and engine including the same |
| KR1020007014837A KR20010053224A (en) | 1998-06-26 | 1999-06-28 | A reciprocating mechanism and engine including the same |
| JP2000557091A JP2002519601A (en) | 1998-06-26 | 1999-06-28 | Reciprocating mechanism and engine including reciprocating mechanism |
| US09/720,387 US6349694B1 (en) | 1998-06-26 | 1999-06-28 | Reciprocating mechanism and engine including the same |
| EA200100077A EA002555B1 (en) | 1998-06-26 | 1999-06-28 | A reciprocating mechanism and engine including the same |
| PCT/GB1999/002027 WO2000000757A1 (en) | 1998-06-26 | 1999-06-28 | A reciprocating mechanism and engine including the same |
| DE69902912T DE69902912T2 (en) | 1998-06-26 | 1999-06-28 | WALKING MECHANISM FOR AN INTERNAL COMBUSTION ENGINE |
| US10/015,827 US6474287B2 (en) | 1998-06-26 | 2001-12-10 | Reciprocating mechanism and engine including the same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GBGB9813710.2A GB9813710D0 (en) | 1997-06-30 | 1998-06-26 | A reciprocating mechanism and engine including the same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB9900247D0 GB9900247D0 (en) | 1999-02-24 |
| GB2340201A true GB2340201A (en) | 2000-02-16 |
Family
ID=10834356
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB9900247A Withdrawn GB2340201A (en) | 1998-06-26 | 1999-01-08 | A reciprocating mechanism and an engine including the same |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2340201A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102061983A (en) * | 2010-11-30 | 2011-05-18 | 徐广平 | Two-stroke explosive direct injection engine |
| IT202100003185A1 (en) * | 2021-02-12 | 2022-08-12 | Scalco Maurizio | STRUCTURE OF INTERNAL INTERNAL ENGINE OF VOLUMETRIC TYPE WITH RECIPROCATING MOVEMENT |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996016282A1 (en) * | 1994-11-23 | 1996-05-30 | Mouton William J Jr | Geared reciprocating piston engine with spherical rotary valve |
| US5673665A (en) * | 1995-11-11 | 1997-10-07 | Kia Motors Corporation | Engine with rack gear-type piston rod |
-
1999
- 1999-01-08 GB GB9900247A patent/GB2340201A/en not_active Withdrawn
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1996016282A1 (en) * | 1994-11-23 | 1996-05-30 | Mouton William J Jr | Geared reciprocating piston engine with spherical rotary valve |
| US5673665A (en) * | 1995-11-11 | 1997-10-07 | Kia Motors Corporation | Engine with rack gear-type piston rod |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102061983A (en) * | 2010-11-30 | 2011-05-18 | 徐广平 | Two-stroke explosive direct injection engine |
| IT202100003185A1 (en) * | 2021-02-12 | 2022-08-12 | Scalco Maurizio | STRUCTURE OF INTERNAL INTERNAL ENGINE OF VOLUMETRIC TYPE WITH RECIPROCATING MOVEMENT |
Also Published As
| Publication number | Publication date |
|---|---|
| GB9900247D0 (en) | 1999-02-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6349694B1 (en) | Reciprocating mechanism and engine including the same | |
| US5595147A (en) | Contra-rotating twin crankshaft internal combustion engine | |
| US5943987A (en) | Reciprocating piston engine with adjacent cylinders in the crankshaft direction in an engine case | |
| EP0851130A1 (en) | Twin crankshaft mechanism with arced connecting rods | |
| US5727513A (en) | Hypocycloidal crank transmission for piston engines, particularly internal-combustion engines | |
| WO1997022785A9 (en) | Counter-rotating twin crankshaft internal combustion engine | |
| CN101454539B (en) | Internal combustion engine | |
| DE4336982A1 (en) | Power generation facility | |
| US4375792A (en) | Asymmetrical internal combustion engine | |
| US5755195A (en) | Internal combustion engine with a gear arrangement on a connection between the piston and the crankshaft and a method of operation thereof | |
| GB2340201A (en) | A reciprocating mechanism and an engine including the same | |
| WO1999011906A1 (en) | Coupling arrangement for reciprocating piston engine | |
| CA2433166A1 (en) | Reciprocating machine | |
| US20190145507A1 (en) | Slider-crank mechanism for eliminating side forces | |
| DE3232974A1 (en) | Drive mechanism for converting rotary motion into linear motion | |
| US11268437B2 (en) | Eccentric shaft speed change mechanism | |
| RU2134795C1 (en) | Method of and volumetric expansion (displacement) machine for conversion of motion | |
| KR970004671B1 (en) | Oldham drive engine | |
| RU2178085C2 (en) | Twin slider-crank-shackle engine | |
| SU1701959A1 (en) | Piston engine | |
| FI111409B (en) | Internal Combustion structure | |
| RU2013606C1 (en) | Internal combustion engine | |
| RU2049919C1 (en) | Piston machine | |
| WO2001059328A1 (en) | Device for interconverting rotary reciprocating movement | |
| RU2059830C1 (en) | Piston engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |