EP2247855B1 - Compresseur à piston à bielle - Google Patents

Compresseur à piston à bielle Download PDF

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Publication number
EP2247855B1
EP2247855B1 EP08869604A EP08869604A EP2247855B1 EP 2247855 B1 EP2247855 B1 EP 2247855B1 EP 08869604 A EP08869604 A EP 08869604A EP 08869604 A EP08869604 A EP 08869604A EP 2247855 B1 EP2247855 B1 EP 2247855B1
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EP
European Patent Office
Prior art keywords
piston
rocking
duct
crankshaft
compression chamber
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Application number
EP08869604A
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German (de)
English (en)
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EP2247855A1 (fr
Inventor
Manfred Wanzke
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Individual
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Individual
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block

Definitions

  • the invention relates to a Pleuelkolbenkompressor for admitting, compressing, moving or expanding and expelling a gaseous or liquid medium consisting of a housing having a compression chamber with a constant in the stroke direction of the piston profile and a connecting rod whose piston in its stroke direction complementary to the profile the compression chamber is shaped and transversely to the stroke direction, in which the compression chamber touching area is kugelsegment- or cylinder segment-shaped and the connecting rod fixed to the piston is pivotally connected to a crankshaft and at least one intake passage and at least one exhaust passage, both in the compression chamber are arranged and both are opened and closed by the piston of the connecting rod in the course of its movement and the profile of the compression chamber contains at least one plane which is aligned perpendicular to the direction of rotation of the crankshaft and all the intake channels and all exhaust channels.
  • Another weakness is the joint between the connecting rod and the piston, which increases the number of parts to be manufactured and assembled and, like all moving parts, is subject to continuous wear.
  • the joint increases the oscillating mass of the piston and thereby increases the load on the crankshaft bearings and deteriorates the concentricity of the engine or the compressor.
  • the object of the invention is to develop a connecting-rod piston compressor whose sealing concept is noticeably simplified in comparison to the reciprocating piston engine.
  • the invention presents that the piston is divided along its longitudinal axis and between the two parts a resilient layer is introduced.
  • An advantage of the connecting rod piston principle is that the piston part of the connecting rod piston in the region in which the compression chamber is in the manner of a cylinder segment, thereby always resting on the cylinder wall such that the cylinder wall forms a tangent to the cylinder segment of the piston.
  • an absolutely inelastic piston and an absolutely inelastic cylinder wall only touch one another, which in practice, however, widens into a surface due to the ever-present elasticity of the material.
  • the key feature of the mark is that, to enhance the sealing effect, the piston is split longitudinally and a spring-elastic layer is introduced between the two parts. This layer presses the parts of the piston against the wall of the compression chamber and can thus also compensate for thermally induced changes in the piston dimensions relative to the cross section of the compression chamber.
  • the invention does not describe how the necessary for operation as a two-stroke engine or for operation as a compressor outlets and inlets could be sealed with such a spherical segment-shaped piston.
  • the invention has set itself the task of developing a piston-rod compressor, which has a simple as possible compression space in which a likewise simple as possible designed connecting rod moves to the cylinder wall and towards the outlet and inlet openings out as large as possible Contact surface has.
  • the profile of the compression chamber contains at least one plane which is oriented perpendicular to the direction of rotation of the crankshaft and which contains all the intake ports and all the exhaust ports.
  • the cylinder of the invention has a plane in which all intake ports and all exhaust ports are arranged and which is swept by a flat surface of the piston and thus reliably sealed.
  • the key advantage of the relatively large surfaces between the piston and cylinder is that in the area of the intake and exhaust ducts of the piston overlaps these openings over a large area, so z. B. also occurs in the thermally highly loaded exhaust duct of a two-stroke engine wear only at the edge of the exhaust duct to the cylinder, but not on a thin, running around the piston seal.
  • the piston part of the connecting rod rests on the cylinder wall in the other regions in which it is designed transversely to the stroke direction in the region in contact with the compression chamber, so that the cylinder wall forms a tangent to the cylinder segment of the piston.
  • an absolutely inelastic piston and an absolutely inelastic cylinder wall only touch one another, which in practice, however, widens into a surface due to the ever-present elasticity of the material.
  • this increased sealing effect is further enhanced by the fact that collect in the two crescent-shaped gaps between the cylinder segment-shaped piston and the flat cylinder wall by capillary action, a lubricant and / or combustion residues and / or particles of the medium to be conveyed or by capillary action be held so that the actual sealing effect in practice is even higher than theoretically expected.
  • the piston outside the flat surface which sweeps over the intake and exhaust ducts, designed spherical segment.
  • This is not only a segment of a single ball to understand, but - depending on the profile of the compression chamber also a plurality of spherical segments adjacent to each other perpendicular to the crankshaft planes.
  • the profile of the piston thus consists of a single straight line, which connects with its two ends to an arbitrarily curved line.
  • intake and exhaust ducts are arranged in a common plane and the profile of the piston is exactly complementary to the profile of the compression chamber, so that a sufficient seal is always ensured.
  • the profile of the piston consists of two opposing planes that are parallel to each other. The edges of these two planes are then connected to each other by two surfaces, which in principle can be freely curved.
  • intake duct and exhaust duct are arranged on respectively opposite surfaces, which improves the gas exchange during engine operation.
  • the profile of the piston is a rectangle.
  • the compression chamber of the contacting area of the piston is no longer spherical segment-shaped, ie, for example, barrel-shaped or spherical, designed, but shaped as a cylindrical segment. This form is particularly easy to manufacture and bring with much less effort in the required for a sufficient sealing effect narrow tolerance limit.
  • a further advantage is that, as an additional variant, a seal can be introduced between the piston and the compression chamber and / or, as a further variant, the two surfaces oriented perpendicular to the axis of rotation of the crankshaft can also be equipped with an additional seal.
  • These gaskets can be applied not only as a plate-shaped material but also as a coating.
  • the piston itself can be equipped with seals that are common in the prior art for reciprocating engines. These include one or more sealing strips, which are oriented transversely to the direction of movement.
  • the piston is split in the longitudinal direction to enhance the sealing effect, and a spring-elastic layer is introduced between the two parts.
  • This layer presses the parts of the piston against the wall of the compression chamber and can thus also compensate for thermally induced changes in the piston dimensions relative to the cross section of the compression chamber.
  • the interior of a connecting rod piston compressor according to the invention consists of the compression chamber and the adjacent thereto Crankcase.
  • the production of this shape is particularly simple when the housing around a connecting rod piston consists of two housing parts whose contact surface is oriented perpendicular to the axis of rotation of the crankshaft. Then the mold for a casting and the post-processing of these castings in a single clamping z. B. done on a three-axis CNC processing machine.
  • both housing halves are identical, so can be created with only one change from a common mold or worked out of identical blanks.
  • the housing of a connecting rod piston compressor When used as a compressor also creates heat loss, as when used as a combustion engine.
  • the housing of a connecting rod piston compressor according to the invention can either have cooling fins for air cooling and / or channels for water cooling.
  • intake passage and the exhaust passage can be extended by appropriate continuations in the piston, which are activated when the piston reaches the respective channel.
  • the intake passage in the passage flange is then extended through the piston intake passage in the connecting rod piston and the exhaust passage in the side flange through the piston exhaust passage in the connecting rod piston.
  • Another channel which can be introduced as an additional option in the piston, when used as a two-stroke engine with an overflow channel and an adjoining inlet channel in the housing of the engine as a connection between the crank chamber and the compression chamber, a so-called piston inlet passage in the connecting rod, the - at Activation is opposite the inlet duct.
  • connecting-rod pistons can be combined to form a multi-piston unit.
  • Each connecting rod each has its own compression chamber and a separate crankcase and is connected to the crank pin of a common crankshaft.
  • crankshaft with its numerous, compared to the axis of rotation cranked crank pin by a straight main shaft replaced, are arranged on the gears, each meshing with another gear, which is integrated in a separate crankshaft for each connecting rod. It makes sense to integrate at least one crank arm of this small crankshaft, which is provided separately for each individual connecting rod piston, into a toothed wheel.
  • the advantage of this arrangement is that the elaborate production of the connecting rod is eliminated. They are replaced by gears.
  • connecting rod piston compressor As already mentioned several times, a very interesting use of the connecting rod piston compressor according to the invention is the operation as a two-stroke engine.
  • a typical feature of any two-stroke operation is that the aspiration of fresh gas in the crankcase occurs simultaneously with the compression of pre-compressed and pre-compressed gas in the compression chamber.
  • a so-called overflow channel is required for forwarding the pre-compressed fresh gas from the crank chamber into the compression chamber.
  • This overflow can z. B. be realized by a bore in a housing part, which is closed by a plug to the outside again. At one end of the overflow then another hole is introduced, which establishes the connection to the compression chamber as Flanscheinlasskanal. In the vicinity of the sealing plug, at least one further bore connects to the overflow channel, which connects the overflow channel with the crank chamber as a connecting channel. Through these two additional holes - the Flanscheinlasskanal and the connecting channel - the overflow is extended to a U-shaped cavity, which connects the crank chamber with the compression chamber.
  • a connecting rod piston compressor according to the invention is in principle ready for use as a two-stroke engine: A fuel-air mixture is introduced via the intake passage and precompressed in the crankcase. It flows into the compression chamber via the connection channels, the overflow channel and the flange outlet channel, where it is further compressed during the upward movement of the piston and ignited approximately at the top dead center of the piston. With the downward movement of the piston, the remaining exhaust gas is expelled.
  • operation in the four-stroke process is also possible. And that is when a single piston connecting rod via a gear on its own crankshaft meshes with another gear to output the torque. If a disc is arranged on this further toothed wheel, within which runs a channel which is connected at the moment of the intake of fuel-air mixture with the intake passage within the passage flange, then the intake passage sucks a fuel-air passage only every second revolution. Mixture. In the intervening revolutions of the oscillating piston sucks no fuel-air mixture but pure fresh air.
  • the medium When such a previously described engine operates on the Otto principle, the medium must be ignited by a spark plug. When operating as an engine according to the diesel principle, the medium ignites itself from reaching a minimum compression itself.
  • an inventive motor is suitable because the profile of its compression space, in contrast to many other oscillating piston engines over the stroke is constant , Then the motor may be e.g. work in partial-load operation with auto-ignition over the entire volume and thus more efficient combustion. Only at very low and extremely high load, the compression is reduced and ignited the mixture through a spark plug.
  • multi-cylinder engines When designed as an internal combustion engine multi-cylinder engines can be constructed, which can be configured as a series engine, V-engine, boxer engine, radial engine, W-motor or H-motor. It is a particular, principal advantage of the invention that each compression chamber in the longitudinal direction of the crankshaft relatively narrow and transverse to the crankshaft can be made relatively wide, so that a Center for the crankshaft can be made relatively wide, so that a Center for the crankshaft can be made relatively wide, so that a Centerless crankshaft, or H-motor. It is a particular, principal advantage of the invention that each compression chamber in the longitudinal direction of the crankshaft relatively narrow and transverse to the crankshaft can be made relatively wide, so that a Lazylindriger engine builds much shorter than is possible for the usual, circular piston , As a result, a significant gain in uniformity and harmonic freedom of the torque output is achieved.
  • the two-stroke diesel engine is the engine principle with the highest efficiency at relatively low speeds and relatively large engine capacities.
  • efficiencies of up to 55% are achieved in this configuration, outclassing fast-running four-stroke turbodiesel with an efficiency of at best approximately 40%.
  • the connecting rod piston compressor according to the invention is the operation as a steam engine or compressed air motor.
  • the admitted medium is a pressurized gas.
  • the piston opens the intake passage and closes the exhaust passage, maintaining this configuration as it approaches the crankshaft until just before reaching bottom dead center.
  • the penetrating gas drives the piston down.
  • the piston closes the intake passage and opens the exhaust passage, maintaining this configuration as it moves back to top dead center.
  • the piston closes the intake passage and opens the exhaust passage, maintaining this configuration as it moves back to top dead center.
  • FIGS. 1 to 6 is shown as an embodiment of an open rod piston engine whose housing 9 consists of two parts whose contact surface is perpendicular to the crankshaft 11. The one housing part is removed and gives the view of the contact surface of the remaining housing part, the side flange 16 free. In the side flange 16 of the crank chamber 18 and the adjoining compression chamber 19 are embedded. Because their side walls perpendicular to the in the Figures 1-6 are visible, arranged approximately keyhole-shaped base, they are in the Figures 1-6 only visible as a line.
  • FIGS. 1 to 6 Dashed is in the FIGS. 1 to 6
  • the piston exhaust duct 4 located, which is embedded in the non-visible surface of the connecting rod 8.
  • the exhaust passage 5 in the side flange 16 dashed is the exhaust passage 5 in the side flange 16, because it is covered by the connecting rod 8 - and thereby also closed, with the exception of in FIG. 2 shown position of the connecting rod 8 in the piston exhaust passage 4th is connected to the exhaust passage 5, so that the exhaust gases can escape from the compression chamber 19.
  • the - in its side view about pear-shaped - connecting rod 8 is pivotally connected with its connecting rod with the crank pin 10 of the crankshaft 11, which is mounted in the center of the circular crank chamber 18.
  • crank pin 10 is the only element in the FIGS. 1 to 6 drafts cut and therefore hatched.
  • the short pin 10 connects the connecting rod 8 with the other - not visible in this section plane - part of the crankshaft eleventh
  • the geomembranes 12 and 13 are located on the - in the Figures 1-6 invisible - face of the piston slides. Also on the lateral plane of the piston additional seals 17 are located. In the simplest variant of a connecting rod compressor, however, the sealing sheets 12 and 13 and the seal 17 are not required.
  • FIG. 7 shows a section across the contact surface of the two parts of the housing 9, with the Figures 1-6 corresponds. With these FIGS. 1 to 6 Various, characteristic positions of the connecting rod 8 will be explained.
  • FIG. 1 the connecting rod 8 is shown in its position at top dead center. Good to see that the compression chamber 19 has shrunk to its minimum volume between the connecting rod 8 and the motor housing 9.
  • the connecting rod piston at top dead center ignited to its maximum value in the combustion chamber 19 ignitable mixture - the diesel process by self-ignition at very high compression, the Otto process by a - not shown here - spark plug.
  • FIG. 1 is very nicely illustrated that the connecting rod piston in this position with its side surface the exhaust passage 5 and the intake passage 7 closes. So it neither enters new mixture, nor is something lost from the compressed mixture.
  • the exhaust passage 5 in the side flange 16 is covered by the connecting rod 8 and thereby shut off. Since it is arranged in an invisible plane, it is shown in dashed lines.
  • the intake channel 7, which is arranged in the - actually drafts dismantled - channel flange 15 and thus also is arranged in a plane which in FIG. 1 is not visible.
  • FIG. 2 has expanded the fuel-air mixture after its ignition and pushed the connecting rod 8 so far down that he has opened the exhaust passage 5 via the piston exhaust passage 4 in the connecting rod 8 and extended into the compression chamber 19 into it.
  • the piston exhaust passage 4 located in the connecting rod 8 extends parallel to the plane of the drawing, the exhaust passage 5 perpendicular to it in the side flange 16, a part of the housing 9, into it.
  • the engine principle according to the invention thus provides, in contrast to hitherto known two-stroke engines with slot control, a significantly better separation of fresh gas and exhaust gases, as a result of which a serious disadvantage is virtually eliminated.
  • FIG. 3 has the crankshaft 11 opposite FIG. 2 rotated a little further, so that the connecting rod 8 connects between the crank chamber 18 and the combustion chamber 19 produces.
  • This connection is made via two connection channels 2, which are in FIG. 3 from the crank chamber 18 out approximately perpendicular to the viewer to run into the overflow 14, which runs parallel to the image plane in - graphically removed - channel flange 15, which is why these elements are shown in dashed lines.
  • the already pre-compressed air-fuel mixture in the crank chamber 18 flows into the combustion chamber 19 at the upper end of the overflow channel 14 through the inlet channel 1 and the piston inlet channel 3 in the connecting-rod piston.
  • the inlet channel 1 is just like the connecting channels 2 aligned perpendicular to the viewer and therefore in the Figures 1-6 only recognizable as a dashed circle.
  • FIG. 3 shown part of the two-stroke process "fill combustion chamber with air fuel mixture” has already begun earlier.
  • a characteristic feature of a two-stroke engine is that always two processes from “intake - compression - ignition - ejection” take place in the engine, which fundamentally differs from the four-stroke process.
  • FIG. 4 has faced the connecting rod FIG. 3 moved so far that the exhaust passage 5 and the intake passage 7 is closed as well as the connection between the overflow channel 14, the inlet channel 1 connected thereto and the connected thereto Kolbenanlasskanal 3 to the combustion chamber 19th
  • FIG. 4 So shows a position of the connecting rod 8, in which he closes all channels.
  • FIG. 5 this has happened in the piston position FIG. 3 already precompressed and discharged via the overflow 14 in the compression space air fuel mixture for the most part removed from the crank chamber 18.
  • the connecting rod 8 via its Kolbenansaugkanal 6 connects to the intake passage 7 ago.
  • the intake duct 7 extends in the drawing - dismantled - channel flange 15 perpendicular to the viewer and in the plane parallel to the plane extending Kolbenansaugkanal 6 inside. About these two channels, the crank chamber 18 is filled with fresh air fuel mixture.
  • FIG. 6 shows as well as the FIG. 4 a position of the connecting rod 8, in which it shuts off all switching openings.
  • FIG. 7 corresponds to the Figures 1-6 with different positions of the connecting rod 8 in the same engine and shows the section through the motor housing in the two different sectional planes AA parallel to the crankshaft 11 and AB through the crankshaft eleventh
  • the housing 9 consists of two parts, the channel flange 15 on the left side and the side flange 16 on the right side.
  • the side flange 16 includes the exhaust passage 5 and the channel flange 15, the intake passage 7.
  • As a further channel connection of the overflow channel 14 is installed in the channel flange 15. It is connected by two connecting channels 2 with the crank chamber 18 and through the inlet channel 1 with the compression chamber 19th
  • the sectional area AA of the left half of the picture and the sectional plane AB are in FIG. 1 entered.
  • the sectional area AA runs in the lower part through the overflow 14 through and kinks in the upper part and is then identical to the sectional plane AB of the right half of FIG. 1 ,
  • the sectional plane AB extends on the axis of symmetry of the compression chamber 19 and the crank chamber 18 through the crankshaft 11.
  • the kinked cut surface AA of the left half of the picture cuts the connecting rod 8, the crank chamber 18 and the disk-shaped parts of the crankshaft 11 on a different cutting line than in the right half of the picture, which explains the difference between the two halves of the picture: in the right half of FIG. 7 the cutting plane passes through the center of the disc, which connects the crankshaft 11 with the pin 10. Therefore, the section through this disc is a much larger rectangle than in the left half of the picture in section AA, which only cuts the same size, second disc on the crankshaft 11 outside its center.
  • FIG. 8 In FIG. 8 are two connecting rods 8 each shown without cylinders in their basic arrangement as a V-engine. The axes of rotation of their own, small crankshaft 11 point to the viewer. Two connecting rod 8 or two rows of connecting rod 8 are arranged at an angle V to each other.
  • a first gearwheel 23 is arranged for each connecting-rod piston 8, each with a second gearwheel 22 on the main shaft 21 meshes.
  • the main shaft 21 collects the torques generated in the individual connecting rod 8 and performs them together. A through the entire engine through going, expensive community crankshaft is spared. Instead, numerous gears are used.
  • FIG. 8 is a gear ratio between the small gears 23 on the respective own crankshaft 11 of each connecting rod 8 and the large gears 22 on the main shaft 21 of 1: 2 located.
  • - in FIG. 8 not shown - channels in the large gear 22 only at every other revolution with a corresponding opening in the crank chamber of each connecting rod 8 in connection. This can be achieved, for example, that only every second revolution of the crankshafts 11 ignitable fuel-air mixture reaches each connecting rod 8.
  • Such a work rhythm corresponds to a four-stroke engine. It is advantageous after ejecting the exhaust, the good flushing of each compression chamber with fresh air. As a result, considerable advantages are achieved in the exhaust gas purification.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Catalysts (AREA)
  • Electromagnets (AREA)

Claims (20)

  1. Compresseur de piston de bielle destiné à alimenter, compresser, déplacer ou expanser et à rejeter un fluide en phase gazeuse ou liquide consistant en
    • un boîtier (9) avec un
    • une chambre de compression (19) ayant un profil constant dans le sens de levage du piston et
    • un piston de bielle (8) dont le piston
    • est formé de façon complémentaire par rapport au profil de la chambre de compression (19) dans le sens de son levage et
    • perpendiculairement au sens du levage en ce que la zone touchant la chambre de compression (19) a une forme de segment de sphère ou de segment de cylindre,
    • la bielle fixée sur le piston étant reliée de façon articulée avec un vilebrequin (11),
    • chacun au moins à un chaque canal d'admission (7) et
    • chacun au moins à un canal d'échappement (5),
    qui sont tous deux disposés dans la chambre de compression (19) et qui sont tous deux ouverts et fermés par le piston de la bielle (8) au cours de leur déplacement,
    le profil de la chambre de compression (19) contenant au moins un niveau
    • qui est orienté à la verticale par rapport au sens de rotation du vilebrequin et
    • qui contient tous les canaux d'aspiration (7) et tous les canaux d'échappement (5)
    caractérisé par le fait
    que le piston est subdivisé le long de son axe longitudinal et est disposé entre les deux parties d'une couche amortissante élastique.
  2. Compresseur de piston de bielle selon la revendication précédente 1, caractérisé par le fait que le profil de la chambre de compression (19) et du piston est un carré.
  3. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait qu'au moins un joint à grande surface étanchéifie le profil de la chambre de compression (19) et le profil du piston l'un par rapport à l'autre.
  4. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que, parmi les quatre parois latérales de la chambre de compression (19), les deux parois qui sont orientées parallèlement à l'axe de rotation du vilebrequin (11) sont chacune recouverte d'une bande d'étanchéité (12, 13).
  5. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que les surfaces latérales du piston orientées perpendiculairement à l'axe rotatif du vilebrequin (11) sont équipées de joints (17).
  6. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que les bandes d'étanchéité (12, 13) et/ou les joints (17) sont fixées de façon à pouvoir être détachées.
  7. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que le boîtier (9) consiste en deux parties de boîtier dont la surface de contact est orientée verticalement par rapport à l'axe de rotation du vilebrequin (11).
  8. Compresseur de piston de bielle selon la revendication 7, caractérisé par le fait que les deux parties du boîtier sont identiques entre elles au niveau de la chambre de compression (19), l'espace du vilebrequin (18), le palier du vilebrequin (11) et la liaison entre les deux moitiés.
  9. Compresseur de piston de bielle selon la revendication 8, caractérisé par le fait qu'une partie du boîtier- la bride latérale (16)
    - contient le canal d'échappement (5), l'autre partie du boîtier - la bride de canal - (15) - contenant le canal d'aspiration (7).
  10. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que le boîtier (9) présente des anneaux de refroidissement destinés au refroidissement de l'air et/ou des canaux pour un refroidissement à l'eau.
  11. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que
    • le canal d'aspiration (7) est prolongé par le canal d'aspiration du piston (6) dans le piston de la bielle (8) et/ou
    • le canal d'échappement (5) par le canal d'échappement du piston (4) dans le piston de la bielle (8) et/ou
    • le canal d'admission (1) par le canal d'admission du piston (3) dans le piston de la bielle (8).
  12. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que
    • plusieurs pistons de bielle (8), ayant chacun sa propre chambre de compression (19) et
    • son propre espace de vilebrequin (18)
    • sont reliés aux manetons de vilebrequin (10) d'un vilebrequin commun (11).
  13. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que
    • plusieurs pistons de bielle (8), chacun avec sa propre chambre de compression (19) et
    • son propre espace de vilebrequin (18)
    • son propre vilebrequin (11)
    • présente chacun un premier pignon (23) sur leur vilebrequin (11),
    • tous les premiers pignons (23) ayant chacun un second pignon (22) venant s'engrener sur un arbre principal (21).
  14. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que le profil de la chambre de compression (19) et du piston est un ovale.
  15. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que, pour le fonctionnement en tant que moteur à deux temps,
    • l'espace du vilebrequin (18) est relié par l'intermédiaire du canal de liaison (2), du canal de décharge (14) et du canal d'admission à bride (1), dans certaines positions d'angle du piston à bielle (8), avec la chambre de compression (19),
    • le fluide admis par aspiration étant un mélange combustible-air,
    • qui est préalablement compressé dans l'espace du vilebrequin (18), et
    • est dirigé dans la chambre de compression (19) par l'intermédiaire du canal de liaison (2), du canal de décharge (14) et du canal d'admission à bride (1),
    • continue à y être compressé pendant le mouvement en avant du piston et
    • est à peu près allumé dans le point mort supérieur du piston en
    • étant éjecté avec le mouvement en arrière du piston.
  16. Compresseur de piston de bielle selon les revendications précédentes 13 et 15, caractérisé par le fait que le second pignon (22) présente deux fois plus de dents que le premier pignon (23), le canal d'aspiration (7) à l'intérieur de la bride de canal (15) étant conduit à un autre canal dans une rondelle sur le second pignon (23), sachant cet autre canal a, à chaque seconde rotation du vilebrequin (11), une liaison avec le canal d'aspiration (7) qui est relié à ce moment avec le canal d'aspiration du piston (6).
  17. Compresseur de piston de bielle selon la revendication précédente 15, caractérisé par le fait que, lors du fonctionnement en tant que moteur à combustion, le fluide est allumé par une bougie d'allumage.
  18. Compresseur de piston de bielle selon la revendication précédente 15, caractérisé par le fait que, lors du fonctionnement en tant que moteur à combustion, le fluide est allumé par une compression minimale.
  19. Compresseur de piston de bielle selon au moins une des revendications précédentes 15 à 18, caractérisé par le fait que plusieurs pistons de bielle (8) sont disposées en tant que
    • moteur en série ou
    • moteur en V ou
    • moteur boxer ou
    • moteur en W ou
    • moteur en H.
  20. Compresseur de piston de bielle selon une des revendications précédentes, caractérisé par le fait que
    • pour le fonctionnement en tant que moteur à vapeur ou que moteur à air comprimé, le fluide admis est un gaz sous pression et
    • que le piston ouvre le canal d'aspiration (7) et ferme le canal d'échappement (5) au ou immédiatement après le point mort supérieur, cette configuration étant conservée pendant l'approche du vilebrequin (11) par le piston jusqu'à presque atteindre le point mort inférieur et
    • que le piston ferme le canal d'aspiration (7) et ouvre le canal d'échappement (5) au ou immédiatement après le point mort inférieur, cette configuration étant conservée pendant le mouvement de retour du vilebrequin vers le point mort supérieur.
EP08869604A 2008-01-10 2008-12-24 Compresseur à piston à bielle Active EP2247855B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008003891 2008-01-10
DE102008045580A DE102008045580B3 (de) 2008-01-10 2008-09-03 Pleuelkolbenkompressor
PCT/DE2008/002157 WO2009086809A1 (fr) 2008-01-10 2008-12-24 Compresseur à piston à bielle

Publications (2)

Publication Number Publication Date
EP2247855A1 EP2247855A1 (fr) 2010-11-10
EP2247855B1 true EP2247855B1 (fr) 2012-02-01

Family

ID=40514689

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08869604A Active EP2247855B1 (fr) 2008-01-10 2008-12-24 Compresseur à piston à bielle

Country Status (4)

Country Link
EP (1) EP2247855B1 (fr)
AT (1) ATE544006T1 (fr)
DE (2) DE102008045580B3 (fr)
WO (1) WO2009086809A1 (fr)

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1775892A (en) * 1929-03-07 1930-09-16 Salardi Albert Bernhard De Pinless piston
DE1133388B (de) * 1959-02-04 1962-07-19 Ciba Geigy Verfahren zur Herstellung von 3, 4-Dihydro-1, 2, 4-benzothiadiazin-1, 1-dioxyden
CA916112A (en) * 1970-03-09 1972-12-05 D. Guenther William Direct drive ball piston compressor
IT950019B (it) * 1971-03-11 1973-06-20 Salzmann W Macchina a pistone particolarmen te motore a combustione interna
FR2342395A1 (fr) * 1976-02-27 1977-09-23 Salzmann Willi Machine a piston du type oscillant
US4610606A (en) 1984-08-06 1986-09-09 Hch Development, Inc. Gas refrigerant compressor including ported walls and a piston of unitary construction having a domed top
DE3818927A1 (de) * 1988-02-03 1989-12-14 Klaue Hermann Hubkolben-brennkraftmaschine
AU4075489A (en) * 1988-09-07 1990-04-02 Willi Ernst Salzmann Reciprocating piston engine
DE3904716C2 (de) * 1989-02-16 1994-01-05 Heinrich Schiller Hubkolbenverdichter oder -verbrennungsmotor mit Exzenterantrieb
DE4226185A1 (de) * 1991-09-26 1993-04-01 Franz Rossbaum Gmbh & Co Kg Kolben-/zylinderanordnung fuer eine brennkraftmaschine
CA2208550A1 (fr) * 1994-12-24 1996-07-04 Willy Ernst Salzmann Moteur et compresseur a piston oscillant
GB2372781A (en) * 2000-11-03 2002-09-04 Bryan Nigel Victor Parsons Balancing of rocking piston reciprocating machines
US20070264141A1 (en) * 2006-05-09 2007-11-15 Chou Wen S Air compressor having improved valve device

Also Published As

Publication number Publication date
WO2009086809A1 (fr) 2009-07-16
ATE544006T1 (de) 2012-02-15
EP2247855A1 (fr) 2010-11-10
DE112008003770A5 (de) 2010-12-09
DE102008045580B3 (de) 2009-05-07

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