EP1320660A1 - Motion converter and method for lubricating its sliding surfaces - Google Patents
Motion converter and method for lubricating its sliding surfacesInfo
- Publication number
- EP1320660A1 EP1320660A1 EP00978950A EP00978950A EP1320660A1 EP 1320660 A1 EP1320660 A1 EP 1320660A1 EP 00978950 A EP00978950 A EP 00978950A EP 00978950 A EP00978950 A EP 00978950A EP 1320660 A1 EP1320660 A1 EP 1320660A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- bearing
- sliding
- sliding block
- frame
- gap
- 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.)
- Granted
Links
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
- F02B75/16—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
- 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
- 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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
-
- 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
Definitions
- the invention relates to a method for lubricating the sliding surfaces of a device for converting rectilinear alternating movements into a rotational movement and vice versa, in particular for reciprocating piston machines, and a movement transducer for carrying out the method.
- the reciprocating piston machines mentioned have at least two axially identical, oppositely arranged working cylinders and a converter which is arranged in a crankcase.
- the converter converts the translational movements of the working pistons sliding in the working cylinders into a rotating movement of a crankshaft or vice versa.
- the crankshaft has a crank pin which is mounted in a sliding block (sliding piece). This performs rectilinear alternating movements between inner slideways of a frame-shaped loop, which in turn is firmly connected to the piston rods and is moved linearly within the crankcase by the crank rods.
- Such reciprocating piston engines can be used as a two-stroke internal combustion engine, as a four-stroke engine, as a reciprocating piston compressor or the like.
- DE-A 3433 510 or EP-B 429 918 show such transducers consisting of sliding block and loop frame for such reciprocating piston machines.
- a problem with such transducers is the reliable lubrication in the area between the inner surfaces of the loop frame, which are designed as slideways, and the sliding surfaces of the sliding block that interact with them.
- US-A 4,794,887 it is known to use ball bearings or roller bearings for such a bearing. It is also known to convey lubricating oil from an oil pump assigned to the reciprocating piston engine through bores in existing gaps between the slideways or sliding surfaces. For this purpose, holes extend from the crank pin bearing to the sliding surfaces, which holes open into grooves or other recesses in the sliding surfaces of the sliding block.
- the grooves are arranged in a herringbone pattern on the sliding surface of the sliding block. The grooves start from a central groove that extends in the sliding direction.
- the invention is based on the fact that the opposite sliding surfaces of the sliding block and the sliding surfaces of the frame are alternately loaded or relieved several times during one working cycle of the two piston-cylinder units. These load changes are used to maintain a reliable lubrication of the sliding surfaces mentioned. This is done in that, depending on the linear changes in movement and the associated changes in load of the layers that make it possible to slide in the two bearing gaps, the sliding block can execute corresponding pendulum movements of limited extent relative to the frame in the direction of the linear alternating movements, which are essentially perpendicular to the sliding surface run. With the help of these pendulum movements, lubricant is conducted from the higher-loaded layer into the lower-loaded layer.
- the invention relies on that a game of predetermined minimum size is provided between the closely adjacent surfaces, so that the sliding block depending on the changes in movement relative to the frame a limited movement along the axis - that in the direction of movement the piston rod runs - can execute. This leads to a kind of breathing movement in the area of each gap, whereby this breathing rhythm is out of phase on both sides of the sliding block.
- the bore system in the sliding block is adapted accordingly, so that an internal exchange system for the lubricant is created between the two gaps.
- the bore system must be designed so that the oil can pass from one lubrication gap into the other lubrication gap in very short periods of time without having to leave the lubricated gap too much oil flows out in this short time, so as not to endanger the lubrication in the sense of fluid friction.
- the interacting sliding and guiding surfaces are smooth, that is to say have no grooves and depressions, except for the openings in the bores of the inner lubricant exchange system in the sliding block.
- the mouths of these bores lie directly in the sliding surfaces, specifically in predetermined areas of these sliding surfaces.
- the game between the side flanks (guide surfaces) is significantly smaller than the game designed between the sliding surfaces, which the
- the direct openings of the bores in the sliding surfaces of the sliding block ensure that all of the lubricant escaping into the lubricating gap between the sliding surfaces and inevitably contributes to the lubrication of these surfaces.
- Such a "closed" internal oil circuit has only minimal leakage oil losses in the lubrication gaps and, in conjunction with the pumping or guiding effect, ensures a safe interception of striking load changes (change of the loaded gap) due to the slag play for the pendulum movement of the sliding block.
- Another advantage is that the pump only needs to be designed so that the lubricating oil it supplies is just sufficient to replace the low losses in the internal lubrication system.
- crank loop frame which is open at the sides and at the ends, so that air and leakage oil displaced by the sliding block can be conveyed out of the interior of the loop frame.
- the bearing surfaces of the sliding block do not have any internal grooves for guiding the lubricant.
- the opposite slideway in the frame is not grooved, without oil flow-conducting inner grooves or tracks.
- this flat design does not mean that the sliding surface of the sliding block (also referred to as a sliding piece) has to be completely flat, rather it can also be designed slightly spherically so that it forms a slightly larger gap towards the end faces than in the middle, with respect to the slide of the frame. It is avoided that the sliding block, which is slightly tilted during the alternating movements at the reversal points, causes an increased pumping action by forming bow waves of lubricant, which would result in an increase in leakage losses.
- the slightly elastic, resilient design of the front ends of the slider contributes to reducing this effect, which give way to the reversal points causing tilting of the movement under greatly increased pressure, to avoid excessive gap reduction, which leads to the increased bow wave and the conveyance of lubricant which would lead to the pressure-bearing gap.
- Figure 1 in a sectional view perpendicular to the crankshaft a four-cylinder two-stroke internal combustion engine
- Figure 3a is a diagram showing load changes during one revolution
- Figure 3b is a diagram showing the positions of the shaft to Figure 3a;
- Figure 11 further examples of the execution of the inner or closed lubrication system.
- Figure 1 shows the structure z.
- B. a four-cylinder two-stroke internal combustion engine with a section through the plane of a pair of cylinders 1, 2nd
- the second, identically constructed pair of working cylinders 11, 12 lies behind the first pair of cylinders in the illustration and is not covered by the section.
- the two working cylinders 1, 2 are axially aligned and opposite one another, with a central axis 18a, which is designated by x.
- the working pistons 3, 4 are rigidly attached to piston rods 5, 6.
- the piston rods 5, 6 are connected to a movement transducer device.
- the piston rods are fixedly arranged on a crank loop frame 7, in which a sliding block 8 is received.
- a crank pin 9 of a crankshaft sits centrally in the sliding block 8 as a polygonal piece.
- the converter is arranged in a crankcase 13, the interior of each of which is provided by a gas exchange chamber 14 of the respective cylinder 1 or 2 provided below the piston 3, 4 through a partition wall bearing 15 is sealed liquid and gas tight.
- a combustion chamber 17 is provided above the piston.
- the converter is shown in FIG.
- the converter consists of the crankshaft 10 with at least one crank pin 9, which is rotatably supported in the sliding block 8 by means of slide bearing shells 43a, 43b, and the frame 7, consisting of the frame halves 7a, 7b, in which the sliding block 8 can slide in a straight line is.
- crankshaft 10 is constructed in one piece as a single crank crankshaft. Depending on the type and / or size of the machine, it can also be constructed in several parts as a so-called built crankshaft. It has disc-shaped cheeks 22 as a means of swing or compensation, which are arranged on both sides of the crank pin 9.
- a bore 45 to the center of the crank pin 9 opens there into a transverse bore 46 penetrating the crank pin 9.
- the outer end of the bore is connected to a lubricating oil pressure source of the machine via a suitable system.
- the sliding block 8 has a bearing bore 93 for receiving the crank pin 9.
- Two plain bearing shell halves 43a, 43b are provided for storage.
- the slide bearing shells 43a, 43b are thin-walled half-cylinder shells.
- the diameter of the inner surface of the slide bearing shell is such that it surrounds the peripheral surface of the crank pin 9 with little play in the assembled state.
- a circumferential groove 71 is provided in the center of its inner surface, in which passage bores 73 are made, distributed over the circumference. The position of the groove 71 is selected so that the transverse bore 46 of the crank pin 9 ends in the groove 71 at the end.
- the sliding block 8 can be made from a sliding bearing material, so that the sliding bearing shells 43a, 43b could be dispensed with.
- the sliding block 8 consisting of two halves 8a, 8b, clamps the bearing shells. It has a first sliding surface 82 and a second sliding surface 83 on opposite outer sides. These are flat, if necessary slightly spherical in the middle.
- the areas adjacent to the sliding surfaces 82, 83 of the sliding block each form guide sliding surfaces (cheeks) 80, 81 (later 84a, 85a) and have a smooth surface.
- the sliding surfaces 82, 83 and / or the guide surfaces can, for example, be hardened and ground or have a coating made of sliding bearing material or can be covered with a sliding bearing plate. They preferably have no depressions, pockets or grooves.
- the sliding surfaces 82, 83 of the sliding block each form boundary edges 90 and 91 with the guide surfaces, which are preferably burr-free and sharp-edged or have a transition radius or a corresponding chamfer, which is explained in more detail below, cf. Figures 6 ff.
- a crank pin bore 93 is provided with an inner surface 94, the inside diameter of which is slightly smaller than the outside diameter of the sliding shells 43a, 43b.
- the anti-rotation device can also be positively locked.
- a radially circumferential groove 95 which is approximately rectangular in cross section.
- the sliding block 8 has at least two, preferably four bores 97 distributed over the circumference, which run radially to the bore and at the other end approximately in the middle of the third of the sliding surfaces 82, 83 of the sliding block, which are outer with respect to the sliding direction, and open directly into these sliding surfaces 82.83. From the bores 97, bores 98 branch off approximately at right angles, which open directly into these near the outer ends of the middle third of the sliding surfaces 82 and 83, cf. Figure 4.5.
- the sliding block is recessed on the end faces and forms tongues 88, 89 tapering towards the shaft 10 at the ends of the sliding surfaces. These are designed and dimensioned so that they can yield slightly elastically when a predetermined loading pressure is exceeded. This is in the situations in which due to a predetermined game the sliding block in Sliding gap in a tilting position inclined in the sliding direction, achieved that the resulting wedge shape of the gap in the sliding direction does not exceed a predetermined wedge angle. In this way, the possible leakage losses of the lubricant can be kept within narrow limits and direct contact of the sliding surfaces with one another can be avoided.
- the bore 97 can also be designed as a blind bore into which the branch bore 98 opens in such a way that an angled supply channel is formed. However, it is also possible to provide only the bores 97, which extend in a straight line (FIG. 11).
- the sliding block 8 is preferably formed in two parts. If a built crankshaft is used, the sliding block 8 can also be in one piece. Connection means are provided for connecting the sliding block halves 8a, 8b.
- the fasteners are not shown for reasons of clarity, they are also e.g. known from DE-A 3435 501.
- the lubricating oil (as an example of lubricant), which is supplied by an external pressure source of the machine, is in the inner groove 71 of the bearing shells 43.
- the lubricating oil supplied by this pump is adjusted in terms of pressure and quantity in such a way that essentially only unavoidable, but low losses are replaced due to the design of the converter, and the pressure is sufficient to allow the externally supplied lubricating oil to flow into the less loaded bearing gap.
- the sliding block 8 is essentially form-fitting in the frame 7 in the axial direction y and in the sliding direction z, which is perpendicular to the axial direction and perpendicular to
- crank loop frame 7 is preferably made in two parts, 7a, 7b. In the case of an engine with a built-in crankshaft, the frame 7 can optionally also be made in one piece.
- the frame halves 7a, 7b are formed symmetrically in the same way. They each have a web 110, the inside of which forms a sliding surface 112.
- the sliding surface or slideway 112 can be hardened and ground, have a coating of plain bearing material or be coated with a plain bearing plate, it should be noted that a surface-hard sliding surface interacts with a surface-soft slideway.
- the longitudinal extent of the bearing surface 112 is selected such that the sliding surfaces 82, 83 are completely covered by the bearing surfaces 112 in the extreme position of the sliding block 8 in the sliding direction. Laterally in the frame are perpendicular to Slideway 112 leg webs 115, 116 formed in one piece in such a way that the frame halves 7a, 7b have an H-shaped cross section. At the ends pointing in the sliding direction, the frame halves 7a, 7b are each designed to be open in accordance with EP-A 429 918.
- the piston rods 5 and 6 are attached, preferably in one piece, between the leg webs 115, 116.
- Bushes 121 are formed on the leg webs 115, 116 and are used to accommodate e.g. Expansion screws are used, with which the frame halves 7a, 7b can be firmly connected.
- the leg webs 115, 116 have guide surfaces 127, 128 on the inside. These guide surfaces directly adjoin the sliding surfaces 112.
- the guide surfaces run parallel to one another and perpendicular to the slideway 112 and they collide with the slideway along a boundary edge 131.
- These areas, where guide surfaces and sliding surfaces meet, are preferably free of cuts or provided with a small transition radius or a small transition phase, as will be explained in more detail below.
- transition or corner areas 131 or 132 it is provided that they are made as small as possible in cross-section in order to keep the amounts of lubricating oil (leaks) which inevitably escape at the open ends as small as possible.
- FIGS. 6, 7, 8 and 9 each show the sliding block 8 in a starting position with a distance S1 from the sliding surfaces 112 and a distance S2 from the guide surfaces 127, 128.
- the gap thus formed is filled with lubricating oil.
- An extremely deflected position of the sliding block 8 is shown in dashed lines. In this position, the boundary edges 90, 91 have the reference symbols 90 ', 91'.
- FIGS. 6 to 9 are not to scale, but only illustrate fundamentally different configurations of the corner regions 132 between sliding surfaces and guide surfaces of sliding block 8 and frame 7. If the sliding block 8 is in its theoretical extreme position, in all embodiments according to FIGS 9, a residual corner channel 132 'is present. The cross-sectional area of this residual corner duct must be minimized.
- the sliding block 8 is sharp-edged on its boundary edge 90, 91 or has only a broken edge.
- the boundary edge 131 of the frame 7 is a free cut, but its dimensions are as small as possible. This version is particularly expedient if the guide surfaces 127, 128 and the sliding surface 112 have a ground surface is provided.
- the boundary edges 90, 91 of the sliding block 8 and the limiting edges 131 of the frame 7 are designed as outer or inner phases and are adapted in such a way that a residual plug channel 132 'remains when the sliding block 8 comes to rest in its theoretical extreme position.
- the residual corner channel is trapezoidal in cross section. According to FIG.
- the sliding block 8 and the frame 7 are each chamfered in the area of their boundary edges 90, 91 and 131, the planes of extension of the phase surfaces enclosing an angle to one another, so that the channel 132 'converges in cross section towards the guide surfaces 127, 128 and is thus wedge-shaped.
- the boundary edges 90, 91 and the edge 131 of the sliding block 8 and the frame 7 are each provided with a radius, the radii being coordinated such that a sickle-gap-shaped channel 132 'remains.
- the choice of the design of the corner channel 132 essentially depends on the size and type of the piston machine, the materials used for the individual parts and the manufacturing process.
- the embodiments according to FIGS. 7, 8 and 9 of the frame 7 are particularly suitable for machining the frame 7.
- the guide surfaces 127, 128 and the sliding surface 112 can be provided with surface coatings or treatments analogous to the sliding block 8 in order to further improve the sliding properties his.
- the guide surfaces 127, 128 are at a distance from one another in the axial direction which is greater than the distance between the guide sliding surfaces 84a, 85a of the sliding block 8, so that the sliding block 8 is guided in the axial direction with a predetermined play S2.
- the game S2 is selected to be significantly smaller than the game S1 in the area of the sliding surfaces 112.
- the oil that emerges from the openings 97, 98 and passes from the sliding surfaces 82, 83 via the boundary edge 90, 91 into this gap serves to lubricate the gaps formed between the guide surfaces 127, 128.
- the leg webs 115, 116 are cut out in a U-shape, see 130.
- the cutouts extend into the vicinity of the sliding surfaces 127, 128.
- the load on the sliding surfaces and layers of lubricating oil between them can vary during operation of a converter depending on the change of direction of the frame 7.
- the load essentially results from a superimposition of the gas pressure forces arising on the working pistons 2, 3 and the direction of their action opposite mass forces of the moving parts of the transducer.
- the resulting sliding block forces F G are plotted on the ordinate and the crank angle 0 ⁇ 180 180 ° is plotted on the abscissa.
- the sliding block 8 Due to the forces F G acting on it, the sliding block 8 performs a pendulum movement between the slideways 112 of the frame 7, which takes place at least once per revolution, depending on the speed and operating mode of the machine, as an internal combustion engine or as a reciprocating piston compressor. At certain speeds at which the gas and mass forces overlap so that the resulting load on the sliding block intersects the zero load line several times, this pendulum movement can also take place more than once per crankshaft revolution.
- a sufficiently thick layer 141 is thus built up on the respective relieved side of the sliding block 8 before the loading, which ensures defined hydroplaning between the sliding loaded surfaces during the entire subsequent loading phase, in particular for the striking start of the loading.
- the pump effect produced by the pendulum movement interacts with the lubricating oil supplied by the mother oil pump, which is fed into the annular groove 71 through the bore 45, 46.
- the pumping action is made up of the displacement pressure in the bearing gap that is subject to higher loads and the negative pressure in the bearing gap that is subject to even less stress.
- the bores 97, 98 are dimensioned in such a way that a sufficient amount of oil from the loaded lubricating film can get into the bore 97, 98 from the loaded lubricating film to achieve the pumping effect and to build up the barrier pressure. however, it is ensured that the loaded oil film 140 always has a minimum dimension required to maintain a sufficiently thick oil film during the entire loading phase. This can be achieved in that the oil feed bores opening into the sliding block surfaces, e.g.
- the bores 97 in the mouth area have a smaller diameter than the bores 98 further away from the edge, since the leakage oil losses which, although reduced according to the invention but not completely preventable, can make it necessary to reduce the partial quantity flowing back. This can be reliably counteracted by narrowing the holes near the edge in the mouth area.
- the oil film 141 becomes the loaded one and the oil film 140 the relieved one.
- the oil is now displaced from the gap S b with the lubricant layer 141 and at least partially reaches the bores 97, 98, which open into and cause the now loaded sliding stone sliding surface 83 now pump back there and a barrier pressure.
- the oil pumped by the oil pump for building up the oil film 140 flows from the bores 45 and 46 via the grooves 71 and 95, in the direction of the sliding surface 82 of the sliding block to the gap S a . This changes when the load direction changes due to the resulting pressure conditions in the
- Damping layers 141, 140 change the direction of flow of the oil in the bores 97, 98 of the two sliding block halves 8a, 8b.
- the pumping effect is noticeably dependent on the size of the play gap S between the sliding block 8 and the frame 7, since, for example, play gaps which are too large can adversely affect the leaks emerging at the edge and thus the thickness and the pressure conditions in the sliding film. This is to be avoided especially at the reversal point of the sliding block, in that the sliding speed briefly assumes the value "zero" and the hydrodynamic load-bearing effect of the oil film is briefly absent. In this operating state, it must therefore be ensured that the loaded film between the sliding block 8 and the frame 7 is not weakened too much by edge leakage losses.
- the converter In the described configuration of the converter, utilizing the pump effect and / or the guiding effect between the loaded and unloaded sides of the sliding block (the opposite columns S a , S b ) in conjunction with minimizing the leakage oil losses in the pressure oil circuit, the converter is reliably achieved in critical operating conditions are reliably and permanently supplied with sufficient lubricating oil and a defined hydroplaning is ensured during operation. This means that there are always optimal sliding conditions between the sliding block and crank loop frame in any operating situation, and striking load changes cannot penetrate the increased buffer layer.
- FIGS. 4 and 5 each show a “bow wave” 140a, 141a at the gap S b , which is currently taking over the load, by a striking alternating movement of the sliding block from the previously loaded opposite bearing gap to the bearing gap now to be loaded.
- This indicated increased flow rate of a lubricant should be avoided as much as possible in order to assign the smallest possible leakages to the gap.
- a slight elastic compliance of the tongue 89, 88 is advantageous for this, which is achieved by the recesses 81 according to FIG. 2, which become clearer in the cross section of FIGS.
- a special form of the bearing surface 82, 83, which leads to a slightly increased edge area of the gap, is also advantageous for this purpose, in order to reduce the leakage losses.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT00978950T ATE332437T1 (en) | 2000-09-25 | 2000-09-25 | MOTION TRANSDUCER AND METHOD FOR LUBRICATION OF ITS SLIDING SURFACES |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE1999113889 DE19913889B4 (en) | 1999-03-26 | 1999-03-26 | reciprocating engine |
PCT/DE2000/003325 WO2002027143A1 (en) | 1999-03-26 | 2000-09-25 | Motion converter and method for lubricating its sliding surfaces |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1320660A1 true EP1320660A1 (en) | 2003-06-25 |
EP1320660B1 EP1320660B1 (en) | 2006-07-05 |
Family
ID=7902609
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00978950A Expired - Lifetime EP1320660B1 (en) | 1999-03-26 | 2000-09-25 | Motion converter and method for lubricating its sliding surfaces |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1320660B1 (en) |
DE (3) | DE19913889B4 (en) |
WO (1) | WO2002027143A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8746206B2 (en) | 2010-06-29 | 2014-06-10 | Matthew Byrne Diggs | Double-Acting Scotch Yoke assembly for X-engines |
GB201013837D0 (en) * | 2010-08-18 | 2010-09-29 | Weatherstone Paul | Linear-rotational motion converter |
CN103321742A (en) * | 2012-03-20 | 2013-09-25 | 钟守军 | Four-stroke opposed engine |
GB2503488A (en) | 2012-06-28 | 2014-01-01 | Oliver Jukes | A Piston to Shaft Coupling |
DE102013106755A1 (en) | 2013-06-27 | 2014-12-31 | Bertwin R. Geist | Sliding block for a crank-type reciprocating engine |
EP3904637A4 (en) * | 2019-07-05 | 2022-01-26 | Galetskij, Anatolij Jurevich | Engine with slider-crank mechanism |
WO2021081591A1 (en) * | 2019-10-29 | 2021-05-06 | ASF Technologies (Australia) Pty Ltd | Internal combustion engine having targeted engine lubrication |
WO2023165686A1 (en) * | 2022-03-01 | 2023-09-07 | LVS Motors OÜ | A composite piston for an engine-generator with slotted link mechanism |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4013048A (en) * | 1975-12-12 | 1977-03-22 | Reitz Daniel M | Bourke type engine |
US4345797A (en) * | 1978-11-20 | 1982-08-24 | Caterpillar Tractor Co. | Lubrication system for an engine |
US4598672A (en) * | 1984-05-29 | 1986-07-08 | R P & M Engines | Apparatus for stabilizing the position of a yoke in an internal combustion engine |
DE3433510A1 (en) * | 1984-09-12 | 1986-03-20 | Ficht GmbH, 8011 Kirchseeon | Sliding block for a slider crank interacting with a crankshaft, in particular for an internal combustion engine with at least one cylinder |
GB8608237D0 (en) * | 1986-04-04 | 1986-05-08 | Collins Motor Corp Ltd | Reciprocatory positive displacement machines |
GB8712645D0 (en) * | 1987-05-29 | 1987-07-01 | Collins Motor Corp Ltd | Interconnecting rotary & reciprocatory motion |
DE8913971U1 (en) * | 1989-11-27 | 1991-03-28 | Ficht GmbH, 8011 Kirchseeon | Crank slider frame for a crank slider drive of an internal combustion engine |
GB9117975D0 (en) * | 1991-08-20 | 1991-10-09 | Collins Motor Corp Ltd | Interconnecting rotary and reciprocating motion |
US5494135A (en) * | 1993-11-08 | 1996-02-27 | Brackett; Douglas C. | Lubrication system for a conjugate drive mechanism |
-
1999
- 1999-03-26 DE DE1999113889 patent/DE19913889B4/en not_active Expired - Lifetime
-
2000
- 2000-09-25 EP EP00978950A patent/EP1320660B1/en not_active Expired - Lifetime
- 2000-09-25 DE DE50013136T patent/DE50013136D1/en not_active Expired - Lifetime
- 2000-09-25 DE DE10085207T patent/DE10085207B4/en not_active Expired - Lifetime
- 2000-09-25 WO PCT/DE2000/003325 patent/WO2002027143A1/en active IP Right Grant
Non-Patent Citations (1)
Title |
---|
See references of WO0227143A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE10085207D2 (en) | 2003-09-04 |
DE19913889A1 (en) | 2000-09-28 |
DE50013136D1 (en) | 2006-08-17 |
WO2002027143A1 (en) | 2002-04-04 |
DE10085207B4 (en) | 2009-06-25 |
EP1320660B1 (en) | 2006-07-05 |
DE19913889B4 (en) | 2010-01-21 |
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