WO1999022118A1 - Dispositif pour le transport d'un milieu ou pour l'entrainement a travers un milieu - Google Patents

Dispositif pour le transport d'un milieu ou pour l'entrainement a travers un milieu Download PDF

Info

Publication number
WO1999022118A1
WO1999022118A1 PCT/EP1998/006829 EP9806829W WO9922118A1 WO 1999022118 A1 WO1999022118 A1 WO 1999022118A1 EP 9806829 W EP9806829 W EP 9806829W WO 9922118 A1 WO9922118 A1 WO 9922118A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
cylinder
movement
combustion chamber
wall
Prior art date
Application number
PCT/EP1998/006829
Other languages
German (de)
English (en)
Other versions
WO1999022118B1 (fr
Inventor
Ernst Beck
Original Assignee
Ernst Beck
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7846786&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO1999022118(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Ernst Beck filed Critical Ernst Beck
Priority to AT98959808T priority Critical patent/ATE222638T1/de
Priority to EP98959808A priority patent/EP1034356B1/fr
Priority to JP2000518190A priority patent/JP2001521100A/ja
Priority to KR1020007004225A priority patent/KR20010031243A/ko
Priority to CA002308709A priority patent/CA2308709A1/fr
Priority to DE59805259T priority patent/DE59805259D1/de
Publication of WO1999022118A1 publication Critical patent/WO1999022118A1/fr
Publication of WO1999022118B1 publication Critical patent/WO1999022118B1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C9/00—Oscillating-piston machines or engines
    • F01C9/002—Oscillating-piston machines or engines the piston oscillating around a fixed axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C9/00—Oscillating-piston machines or engines

Definitions

  • the invention relates to a device for conveying a liquid or gaseous medium or for driving through a medium according to the preamble of claim 1.
  • Such devices are known for example as compressors.
  • the known compressor has a piston-X cylinder unit, in which the piston is moved up and down by means of a piston rod and a crank mechanism.
  • a valve arrangement which consists of two check valves, which are assigned to the cylinder unit, ensures that ambient air is sucked into the cylinder chamber when the piston U moves downward and that the suctioned-in air is expelled as conveying air during the subsequent upward movement of the piston.
  • One valve operates during the suction process and the other valve functions during the exhaust process.
  • the up and down movement of the piston is realized by driving the crank mechanism by means of a drive unit, for example an electric motor.
  • the invention has for its object to provide a device of the type mentioned, which does not have these disadvantages.
  • This object is achieved in that the movement of the piston is guided by means of a bearing and that the bearing is located outside the cylinder. Due to this construction, it is possible to optimally guide the piston in the bearing so that it runs through a precisely defined and exact path of movement.
  • the bearing can be designed in any way. It is not a problem if the bearing contains a lubricant, for example bearing grease or the like, since it is arranged outside the cylinder and consequently no residues of the lubricant or the like can get into the cylinder and thus into the pumped medium. Since the piston thus has a separate bearing, unlike in the prior art, it does not have to guide itself in the cylinder, so that friction of the piston on the inner wall of the Cylinder is completely avoided.
  • the piston can be guided so precisely that it runs without lubricant in the cylinder and maintains an extremely small distance from the inner wall of the cylinder, the distance being so small that leakage losses are largely avoided.
  • Additional sealing means for example disks made of metal, as are used in known conveying devices and which are arranged in the gap between the piston and the inner wall of the cylinder, can be dispensed with.
  • the piston performs a partial circular movement about a pivot point.
  • the piston is formed on a rotating part so that it can carry out the above-mentioned partial circular movement.
  • the mentioned rotating part has the bearing, the piston being radially offset from the pivot point.
  • the rotary part therefore carries out an oscillating movement for the reciprocating movement of the piston, the piston, which is offset radially outward relative to the pivot point of the rotary part, runs through a partial circular path. Since the rotating part is precisely guided by means of the bearing arranged outside the cylinder, the piston moves along an exact, defined path, which prevents inadmissible frictional forces from occurring against the inner wall of the cylinder.
  • a first cylinder wall facing a first end face of the piston is penetrated by at least one check valve.
  • a first cylinder wall facing a first end face of the piston it is also possible for a first cylinder wall facing a first end face of the piston to be penetrated by at least two non-return valves which have opposite flow directions.
  • the check valve ensures that this allows the medium to be sucked into the cylinder space by opening the piston by means of a corresponding piston movement.
  • the piston is then moved back, preferably having at least one check valve passing through it, so that the pumped medium flows through the piston and then - with a further piston stroke - exits through a further check valve.
  • this further check valve passes through a second cylinder wall facing the other, second end face of the piston.
  • a device for driving through a medium in particular a two-stroke internal combustion engine, is also proposed with the features of claim 13.
  • This is characterized in that the movement of the piston is guided by means of a bearing and that the bearing is arranged outside the combustion chamber. Due to this construction, it is possible to optimally guide the piston in the bearing so that it runs through a precisely defined and exact path of movement.
  • the bearing can be designed in any way. It is not a problem if the bearing contains a lubricant, for example bearing grease or the like, since it is arranged outside the combustion chamber and consequently no residues of the lubricant or the like can get into the combustion chamber and thus into the exhaust gases of the internal combustion engine.
  • the piston thus has a separate bearing, unlike in the known internal combustion engines, it does not have to lead itself in the combustion chamber formed by a recess, bore or the like, so that friction of the piston on the combustion chamber wall is preferably complete, but at least largely is avoided. Due to the bearing, the piston can be guided so precisely that it runs in the combustion chamber without lubricant and thereby an extremely small NEN distance to the combustion chamber wall, the distance is so small that leakage losses are largely avoided.
  • An embodiment of the internal combustion engine is particularly preferred, which is characterized in that the piston is guided in the combustion chamber without a seal relative to the combustion chamber wall. Additional sealants, for example sealing rings, such as are provided in the known internal combustion engines for sealing the gap between the piston and the combustion chamber wall, are not required.
  • the gap between the side surface of the piston and the combustion chamber wall is extremely thin, so that leakage losses alone and / or due to a relatively large length of the side surface of the piston can be avoided.
  • FIG. 1 shows a perspective view (obliquely from above) of a conveyor device
  • FIG. 2 shows a perspective view obliquely on the underside of the conveyor
  • FIG. 3 shows a side view of the conveyor device (partly in section)
  • FIG. 10 shows a side view of an exemplary embodiment of an internal combustion engine (partly in section),
  • FIG. 11 each shows a plan view of a piston component arranged in and 12 a combustion chamber in different piston positions
  • FIG. 13 shows a plan view of an exemplary embodiment of a first printing plate
  • Figure 14 is a side view of an embodiment of a connection plate.
  • FIG. 1 shows a conveyor device 1 which, in accordance with the exemplary embodiment here, is designed as a compressor. It has a housing 2 and a piston / cylinder unit 3.
  • a drive shaft 4 is rotatably mounted in the housing 2, to which a drive unit (not shown), for example an electric motor, can be coupled.
  • a crank disc 5 is rotatably arranged so that an eccentric 6 ( Figure 2) is formed.
  • a fork piece 8 is pivotally mounted in an eccentrically located receiving recess 7, the fork arms 9 of which are pivotably connected to a block piece 11 about an axis 10 which runs horizontally in FIG.
  • the block piece 11 is rotatably connected to a piston shaft 12.
  • the piston / cylinder unit 3 has a cylinder 14 which has a circular-hollow cylindrical lower part 15 and a cylinder cover 16.
  • the cylinder cover 16 is designed as a circular plate which is screwed to the pot-shaped lower part 15 using suitable means, for example with machine screws.
  • a precision bearing 17 (FIG. 3) is arranged in the housing 2 and rotates the piston shaft 12 exactly and also in the exact axial position.
  • the piston component 18 of the piston / cylinder unit 3 is rotatably guided around the piston shaft 12 along a partial circular movement.
  • the piston component 18 has a first piston 19 and a second piston 20, both of which are offset radially outward from the pivot point 21 of the piston component 18.
  • the fulcrum 21 lies on the axis of rotation of the piston shaft 12.
  • the piston component 18 has a circular central part 22, from which the first and the second pistons 19, 20 extend radially outward in a wing-like manner, the respective pistons 19, 20 extending to the inside 23 of the cylinder 14 extends.
  • the side surface 24 of the respective piston 19, 20 is therefore convexly curved in accordance with the inner curvature of the inside 23.
  • the inside 23 faces the side surface 24 without contact with extremely little play, such that a seal is created there.
  • no separate sealing means are provided in this area because they are not required.
  • the sealing of the gap between the side tenflache 24 of the respective piston 19, 20 and the inner wall of the cylinder 14 takes place exclusively with the help of the small play between the two components and the relatively large arc length of the side surface 24, which is formed in a circular section in this embodiment.
  • Inside the piston / cylinder unit 3 there are cylinder walls 25, 26, 27 and 28 which are arranged in a stationary manner.
  • the cylinder walls 25 to 28 are pressure-tightly connected to the bottom 29 of the lower part 15 and also pressure-tight to the inside 23.
  • each piston 19, 20 is arranged opposite to the inside of the bottom 29 and the inside of the cylinder cover 16 with only very little play, so that overall the situation arises that the two pistons 19 and 20 due to the bearing of the piston component 18 by means of of the precision bearing 17 can be moved in a contact-free but sealing manner in the respective cylinder space 32, 33.
  • the cylinder space 32 lies between the cylinder walls 25 and 26; the cylinder space 33 is located between the cylinder walls 27 and 28. Due to the extremely thin gap between the side surface 24 of the respective piston 19, 20 and the outer periphery 31 of the central part 22, the cylinder derraum 32, 33 separated by the pistons 19 and 20 from each other.
  • FIGS. 4 to 6 It can also be seen from FIGS. 4 to 6 that the cylinder walls 25 to 28 are penetrated by bores 34 in which there are check valves 35, 36, 37 and 38 provided with helical springs. As an alternative, tongue or diaphragm valves or the like can also be used. Furthermore, the two pistons 19 and 20 are penetrated by through holes 39 in which check valves 40, 41, 42 and 43 are arranged. According to FIG. 1, the cylinder cover 16 is penetrated by a medium inlet opening 44 and by a medium outlet opening 45. For the sake of clarity, these two openings can also be seen with a broken line in FIGS. 4 to 6.
  • the medium inlet opening 44 is located between the two cylinder walls 25 and 27 and the medium outlet opening 45 between the two cylinder walls 26 and 28 and in each case between the outer periphery 31 and the inside 23 of the circular-hollow cylindrical lower part 15. Chambers are therefore formed in these areas, the chamber associated with the medium inlet opening 44 forming a suction chamber 46 and the chamber associated with the medium outlet opening 45 forming an ejection chamber 47.
  • the fork piece 8 also acts as an eccentric, whereby the block piece 11 is set into an oscillating back-and-forth movement, that is, the piston component 18 carries out an oscillating movement around the piston shaft 12, that is to say about the pivot point 21 .
  • the respective piston 19 or 20 is displaced within the cylinder space 32 or 33 such that, starting from FIG. 4-, for example, the piston 19 first lies opposite the cylinder wall 25, then moves in the direction of the cylinder wall 26 (FIG. 5 ) and finally opposite the cylinder wall 26 with only a very small distance (FIG. 6). The further movement then takes place in the reverse manner, that is to say the piston 19 moves back in the direction of the cylinder wall 25.
  • the suction phase is complete and the piston 19 moves back in such a way that the intake air located in the cylinder chamber 32 is slightly compressed, in such a way that the two check valves 40 and 41 in the piston 19 open automatically due to the inertia, which essentially moves the air volume to the other side of the piston, that is, it flows through the through-hole tion 39. If the piston 19 is moved again in the direction of the cylinder wall 26 during the next piston stroke, the air volume is conveyed into the discharge chamber 47 by opening the check valve 36 and from there to the medium outlet opening 45. In the case of the latter conveying movement, a suction process takes place simultaneously on the other side of the piston 19.
  • check valves 40, 41 in the piston also automatically close again with the aid of inertia.
  • the conveyor device 1 is able to deliver a high delivery rate due to the two pistons 19 and 20.
  • FIGS. 7 to 9 show a further exemplary embodiment of a conveying device which differs from the above-mentioned exemplary embodiment only in terms of the arrangement of the check valves, so that only this change will be discussed below.
  • the cylinder walls 25 to 28 are each penetrated by two bores 34, in which check valves 51, 52, 53, 54, 55, 56, 57 and 58 are arranged.
  • the check valves 51 and 52 or 53 and 54 or 55 and 56 or 57 and 58 lie with opposite flow directions to one another, so that the one check valve forms an intake valve and the other check valve forms a pressure valve.
  • the same parts - as far as can be seen - as in Figures 1 to 6 with the same Provide reference numerals. In this respect, reference can be made to their description.
  • the check valve 51 opens, so that air is sucked into the cylinder chamber 32 from the suction chamber 46. If the piston 19 then moves clockwise, the sucked-in air is fed through the non-return valve 52 to a pressure line 59 connected there, indicated only by dashed lines, which leads to the medium outlet opening 45.
  • the respective suction takes place via the medium inlet opening 44 and the respective discharge to the medium outlet opening 45, corresponding suction or pressure lines not shown in the figures being used.
  • each piston 19 and 20 with its associated cylinder space each form a separate unit.
  • the respective cylinder spaces 32 and 33 are then each assigned a medium inlet opening 44 and a medium outlet opening 45. It is also easily possible to provide more than two pistons. Overall, depending on the number of pistons, the same Number of media to be funded.
  • the conveying device in which it has a plurality of pistons, it is provided that the amount of medium conveyed by pivoting the individual pistons is of the same size.
  • the conveying device can advantageously also be used as a metering pump, for example for filling liquid foods, for example milk.
  • the through holes 39 also serve to cool the pistons. If a medium flows from the suction chamber 46 through the through bores, the respective piston 19 or 20 is cooled by this medium sucked in.
  • FIGS. 4 and 6 it can also be seen that between the pistons 19 and 20 and its associated cylinder walls 26 to 28, provided that the pistons 19 and 20 are in their end positions, there is no so-called harmful space. This means that the piston is in its end position at a very short distance from the respective cylinder wall. This ensures that the conveyed medium is completely pushed out of the conveying device 1 or during the suction process a volume of a medium is sucked in which corresponds to the volume of the space which is formed between an end face of the piston and the opposite cylinder wall.
  • the delivery device 1 can be used particularly advantageously for liquids without self-lubrication, such as gasoline, which is known to have essentially no lubrication properties.
  • pistons 19 and / or 20 and the associated cylinder walls are also possible to design the pistons 19 and / or 20 and the associated cylinder walls to run obliquely. This means that when the piston is viewed from above, it has a parallelogram or diamond-shaped contour. The end faces of the piston are thus enlarged, so that there are larger through bores in cross section and thus larger check valves can be used.
  • crank disk 5, fork piece 8 and block piece 11 it should also be mentioned that it is also possible to drive the drive, consisting of crank disk 5, fork piece 8 and block piece 11, by a known crank drive, as used, for example, in the case of a windshield wiper drive. is used to replace.
  • a known crank drive as used, for example, in the case of a windshield wiper drive. is used to replace.
  • at least two piston / cylinder units 3 are arranged one above the other. They are driven jointly via the drive shaft 4.
  • the piston shaft 12 of the two piston / cylinder units 3 is designed to be continuous. A piston shaft 12 is therefore provided, on which two piston components are arranged one above the other.
  • the conveyor 1 it is also easily possible to operate the conveyor 1 as a motor. It is preferably provided that the cylinder spaces 32 and 33 each comprise an ignition device, so that an internal combustion engine is formed, the driving force generated can be tapped off on the drive shaft 4.
  • the medium to be conveyed is sucked into the cylinder spaces 32, 33 with a corresponding piston movement via at least one medium inlet opening in each case.
  • the medium inlet openings can either be made in the pot-shaped lower part 15 of the cylinder 14 or in the cylinder cover 16 and open into the respective cylinder space.
  • at least one medium outlet opening is assigned to each cylinder chamber, the medium outlet openings likewise are arranged either in the lower part 15 or in the cylinder cover 16 of the cylinder 14.
  • a check valve is provided in each of the medium inlet and outlet openings in order to determine the direction of flow of the medium in one direction.
  • the arrangement of the medium inlet and outlet openings in the side walls of the cylinder, i.e. in the lower part and in the cylinder cover, is particularly advantageous when using the conveying device described in FIGS. 1 to 9 in a modified form as an internal combustion engine, since valves can be dispensed with because here the piston clears the inlet and outlet opening (s) in the cylinder cover or in the lower part of the cylinder during its back and forth movement.
  • the respective outlet opening through which the medium is expressed from the cylinder space by a corresponding piston movement can be connected to a pressure line leading directly to the consumer.
  • All embodiments of the conveyor device have in common that due to the extremely small distances between the side surface of the respective piston and the inner wall of the cylinder and between the outer periphery of the central part, to which the at least one piston is connected, and the inside 30 of the respective cylinder wall 25 to 28 a seal is created without the need to use separate sealants.
  • the precise movement of the piston with the aid of the precision bearing 17 can ensure that the piston or the pistons do not touch the inner wall of the cylinder and / or the inside of the respective cylinder wall during operation of the conveying device, so that lubrication of these areas can be dispensed with .
  • the medium is conveyed by the piston and only one valve has to be installed per surface, so that large valve surfaces can be realized, which in turn reduces the flow losses of the conveying device can. Since the direction of flow of the medium in the working space in which the respective piston is moving does not have to be reversed, this also has an advantageous effect on resonance charging.
  • FIG. 10 shows a side view of an exemplary embodiment of a device for driving through a medium, hereinafter referred to as internal combustion engine 101, which has a housing 102 and a working unit 103.
  • An output shaft 104 is rotatably mounted in the housing 102, on which a torque generated by the working unit 103 can be tapped.
  • a crank disk 105 is connected to the output shaft in a rotationally fixed manner.
  • a fork piece 107 is pivotally mounted in a recessed recess, not shown in FIG.
  • the working unit 103 comprises a pot-shaped lower part 113 and a cover 115 which is designed as a circular plate which is screwed to the lower part 113 using suitable fastening means, for example with machine screws.
  • a precision bearing 117 is arranged in the housing 102 and rotates the piston shaft 112 exactly and also in the exact axial position.
  • In the interior of the circular hollow cylindrical lower part 113 of the working unit 103 are a pressure plate 119, a Housing block 121 and a connecting plate 123 are arranged which are stacked on top of one another, the housing block 121 being arranged between the pressure plate 119 arranged on the bottom of the pot-shaped lower part 113 and the connecting plate 123.
  • FIG. 11 shows a plan view of a schematic diagram of an exemplary embodiment of a housing block 121, in which an edge-open recess 125 is made, in which a piston component 127 is rotatably guided about the longitudinal central axis of the piston shaft 112 along a partial circular movement.
  • the piston component 127 which is non-rotatably connected to the piston shaft 112, has a first piston 129 and a second piston 131, both of which are offset radially outward from the pivot point 133 of the piston component 127.
  • the fulcrum 133 lies on the axis of rotation (longitudinal center axis) of the piston shaft 112.
  • the piston component 127 has a circular middle part 135, from which the first and the second pistons 129, 131 extend radially outward in a wing-like manner, the respective pistons 129, 131 to extends to a side wall 137 of the recess 125.
  • the side wall 137 is curved, the curvature corresponding to that of an imaginary circle with the pivot point 133 as the center and the radius r.
  • the side surface 139 of the respective piston 129, 131 is designed in accordance with the inner curvature of the side wall 137 and is therefore convexly curved.
  • the side wall 137 of the recess 125 faces the side surface 139 of the piston without contact with extremely little play, such that there quasi a seal is created. Because of the very thin gap between the side surface 124 of the piston 129, 131 and the side wall 137 of the recess 125 and the relatively long length of the side surface 139, as seen in the direction of movement of the pistons, separate sealing means, for example sealing washers, rings or the like, are not here required.
  • the side walls 141 of the recess 125 which face the central part 135 of the piston component 127 at an extremely short distance, are adapted to the outer periphery 143 of the central part 135, so that movement of the piston component 127 about the pivot point 133 can occur, but between the mentioned Surfaces a seal is formed. Due to the very small gap height, additional seals or sealants can also be dispensed with here.
  • the regions of the recess 125 in which the pistons 129 and 131 are moved back and forth are designed in the manner of a circular cutout.
  • These working areas in the form of a circular section, in each of which one of the pistons 129, 131 is located, are divided by the pistons 129, 131 into a suction chamber 144 or 146 and into a combustion chamber 145 or 147, respectively.
  • the combustion chamber 145 is reduced by a displacement of the piston 129 and at the same time the suction chamber 144 is enlarged, while the combustion chamber 147 is enlarged by the displacement of the piston 131 and the suction chamber interacting with the combustion chamber 147 146 can be reduced.
  • an intake duct 151 and an exhaust duct 153 leading to the exhaust pipe are each introduced in the area of the working spaces for the pistons 129, 131.
  • the intake channels 151 are circular in their mouth area and the outlet channels 153 are square.
  • the outlet ducts 153 can be kidney-shaped in their area opening into the combustion chambers 145, 147.
  • the internal combustion engine 101 also has an ignition device 155, which in each case comprises a spark plug 157 for each of the combustion chambers 145, 147.
  • the spark plugs 157 arranged in the blind bores 159 in the housing block 121 are screwed into threaded bores and protrude into the respective combustion chamber 145 or 147, so that a compressed fuel-air mixture located in the combustion chambers 15, 147 can be ignited.
  • the structure and function of an ignition device for an internal combustion engine is generally known, so that its structure is not described in detail.
  • FIG. 14 shows a side view of the connection plate 123 described with reference to FIG. 10, in which intake ducts 151 'and outlet ducts 153' are introduced, which open into an intake chamber 161 or discharge chamber 163 shown with a broken line.
  • the suction chamber 161 is provided with a fuel or fuel-air mixture supply line, not shown, and the exhaust valve 163 comes with an exhaust pipe (exhaust). connected.
  • the connection plate 123 rests with its flat contact surface 165 on the flat rear side of the housing block 121, i.e.
  • a check valve not shown in the figures, which allows passage from the intake chamber 161 into the intake chamber 144 or 146 and a backflow of the fuel-air mixture drawn from the intake chamber 161 prevented from the suction chamber 144 or 146 into the suction chamber 161.
  • FIG. 13 shows a plan view of an exemplary embodiment of a pressure plate 119 of the working unit 103, which is formed by a flat plate.
  • a through hole 167 is provided in the center of the pressure plate 119, through which the piston shaft 112 is inserted.
  • two overflow channels 169 and 171, respectively are arranged radially offset to the center of the pressure plate 119, depending on their function will be discussed in more detail below.
  • the arrangement and configuration of the overflow channels 169, 171 which are open at the edge in this exemplary embodiment and which are formed here by elongated depressions can be varied.
  • the overflow channels 169, 171 are designed as through openings which at least partially penetrate the pressure plate 119.
  • the through openings In the assembled state of the pressure plate 119, the through openings must be closed on their side facing away from the front of the housing block.
  • a cover plate can be attached to the pressure plate, for example screwed on.
  • FIG. 12 shows a plan view of the exemplary embodiment of the housing block 121 described with reference to FIG. 11.
  • the piston component 127 is arranged here in an end position, which it assumes by rotating clockwise around the pivot point 133. In the position of the piston component 127 shown in FIG. 11, it is in its other end position, which it assumes by rotating it counterclockwise.
  • the internal combustion engine 101 described with reference to FIGS. 10 to 14 is a two-stroke internal combustion engine for, for example, gasoline and / or diesel operation.
  • the internal combustion engine 101 can also be operated with other fuels, for example methane.
  • the piston shaft 112 and thus the block piece 111 attached to it in a rotationally fixed manner is caused by an oscillating back and forth movement of the piston part 127 vibrated. Characterized the fork piece 107 is moved in a corresponding manner, whereby a rotation of the crank disk 105 is initiated.
  • the torque transmitted in the process can, as said, be taken off on the rotating output shaft 104.
  • it is provided that it operates in four-stroke mode and accordingly has a correspondingly modified construction.
  • the first cycle of the piston 129 begins by an oscillating movement of the piston component 127 about the pivot point 133 in a clockwise direction.
  • a fuel-air mixture is drawn from the suction chamber 161 into the suction chamber 144 assigned to the combustion chamber 145 via the suction channels 151, 151 '.
  • the fuel-air mixture located in the combustion chamber 145 is compressed from the moment in which the piston 129 has passed over the outlet channel 153 and has thus been covered, that is to say closed.
  • the piston 129 has reached a certain position, for example the position shown in FIG.
  • the fuel-air mixture in the combustion chamber 145 is ignited with the aid of the ignition device 155.
  • the further movement of the piston 129, that is to say the second cycle, then takes place in the reverse manner, that is to say the piston 129 now moves counterclockwise back into the position shown in FIG. 11.
  • the outlet channel 153 is first opened before the fuel-air mixture compressed in the suction chamber 144 by pivoting the piston 129 counterclockwise through the overflow channel 169 can get into the combustion chamber 145.
  • the internal combustion engine 101 can also comprise only one piston or more than two pistons, for example three or four pistons. It remains to be noted that the pistons 129, 131 in their end positions shown in FIGS. 11 and 12 do not rest on a side surface of the recess 25, but are preferably located at a very short distance from the latter.
  • the drive of piston component 127 is designed in such a way that output shaft 104 rotates through 90 ° when pistons 129, 131 each pass half the piston path. A sinusoidal drive is therefore provided here, as a result of which the internal combustion engine can run smoothly.
  • crank drive As is used, for example, in a windshield wiper drive.
  • crank drive a known crank drive
  • at least two working units 103 are arranged one above the other. They are driven together via the output shaft 104.
  • the piston shaft 112 of the two working units 103 is designed to be continuous.
  • only one piston shaft 112 is provided, on which two piston components, each having at least one piston, are arranged one above the other.
  • the internal combustion engine can advantageously be used in combination with a delivery device for a liquid or gaseous medium.
  • the conveying device comprises at least one piston component which can be pivoted about an axis and has at least one piston attached to it, the piston component of the conveying device being connected in a rotationally fixed manner to the piston shaft 112 of the internal combustion engine.
  • the internal combustion engine and conveyor unit formed is characterized by a simple, compact and inexpensive structure. It is also advantageous that the swiveling movement of the piston shaft 112 generated by the internal combustion engine does not have to be converted into a rotary movement in order to drive the conveying device, but that the drive torque introduced into the piston shaft 112 can thus be used directly by us with little loss.
  • the output shaft 104 shown in FIG. 10 is preferably only required as a pacemaker and as a stroke limiter for the piston component of the internal combustion engine and that of the delivery device. Because the internal combustion engine and the conveying device are arranged to the left and right of the block piece 111 and the crank disk 105, the influence of the heat radiated by both devices on the remaining parts is reduced to an innocuous degree.
  • the defined guidance of the piston movement outside the combustion chamber with the aid of at least one bearing enables the movement path of the at least one piston of the internal combustion engine to be guided so precisely that contact with the piston with one of the walls delimiting the combustion chamber can be ruled out.
  • Sealing the combustion chamber, in particular the gap between the side surface 139 of the piston and the side wall 137 (combustion chamber wall) of the respective combustion chamber is possible solely because of the small distance between these two surfaces. This means that there are no separate seals such as those known from the prior art Internal combustion engines are needed. Furthermore, there is no need to lubricate the piston since it does not slide on the combustion chamber wall.
  • the internal combustion engine 1 is also characterized by a simple and therefore inexpensive construction. Due to the configuration described above, sliding friction between the piston or pistons of the internal combustion engine and the combustion chamber wall is avoided, so that the internal combustion engine can be started with low forces, preferably even in the cold.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Finger-Pressure Massage (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un dispositif pour le transport d'un milieu, en particulier d'un gaz ou d'un liquide, comprenant une unité piston/cylindre telle que le milieu soit aspiré par un déplacement du piston et soit refoulé, à la fois, par déplacement du piston en sens contraire, et par actionnement d'un système de vanne, caractérisé en ce que le déplacement du piston est guidé au moyen d'une portée (palier de précision) et en ce que la portée (palier de précision) se trouve à l'extérieur du cylindre (chambre du cylindre, chambre d'explosion).
PCT/EP1998/006829 1997-10-28 1998-10-28 Dispositif pour le transport d'un milieu ou pour l'entrainement a travers un milieu WO1999022118A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
AT98959808T ATE222638T1 (de) 1997-10-28 1998-10-28 Vorrichtung für die förderung eines mediums oder zum antrieb durch ein medium
EP98959808A EP1034356B1 (fr) 1997-10-28 1998-10-28 Dispositif pour le transport d'un milieu ou pour l'entrainement a travers un milieu
JP2000518190A JP2001521100A (ja) 1997-10-28 1998-10-28 媒質の搬送又は媒質による駆動のための装置
KR1020007004225A KR20010031243A (ko) 1997-10-28 1998-10-28 매체를 이송하거나 그 매체를 통해서 구동시키는 장치
CA002308709A CA2308709A1 (fr) 1997-10-28 1998-10-28 Dispositif pour le transport d'un milieu ou pour l'entrainement a travers un milieu
DE59805259T DE59805259D1 (de) 1997-10-28 1998-10-28 Vorrichtung für die förderung eines mediums oder zum antrieb durch ein medium

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19747445.4 1997-10-28
DE19747445A DE19747445A1 (de) 1997-10-28 1997-10-28 Fördereinrichtung für ein Medium

Publications (2)

Publication Number Publication Date
WO1999022118A1 true WO1999022118A1 (fr) 1999-05-06
WO1999022118B1 WO1999022118B1 (fr) 1999-06-10

Family

ID=7846786

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1998/006829 WO1999022118A1 (fr) 1997-10-28 1998-10-28 Dispositif pour le transport d'un milieu ou pour l'entrainement a travers un milieu

Country Status (8)

Country Link
EP (1) EP1034356B1 (fr)
JP (1) JP2001521100A (fr)
KR (1) KR20010031243A (fr)
CN (1) CN1276848A (fr)
AT (1) ATE222638T1 (fr)
CA (1) CA2308709A1 (fr)
DE (2) DE19747445A1 (fr)
WO (1) WO1999022118A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10232388A1 (de) * 2002-07-17 2004-02-05 Bernt Renner Vorrichtung zum Fördern eines Fluids

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003067033A1 (fr) * 2002-02-06 2003-08-14 Huettlin Herbert Moteur a pistons oscillants
DE10208586A1 (de) 2002-02-22 2003-09-11 Reinhard Sorg Antriebseinrichtung für eine Maschine, insbesondere Pumpe oder Motor
DE102005010775B3 (de) 2005-02-25 2006-04-20 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102010019122B4 (de) 2010-04-30 2012-06-21 Ernst Beck Schwenkkolbenmaschine mit einem um eine Schwenkachse oszillierenden Schwenkkolben

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB865223A (en) * 1958-10-28 1961-04-12 Girling Ltd Improvements in hydraulic devices of the vane type
FR1556723A (fr) * 1967-03-15 1969-02-07
FR2004816A1 (fr) * 1968-03-27 1969-12-05 Lysaght Ltd John
EP0394720A1 (fr) * 1989-04-28 1990-10-31 Balzers-Pfeiffer GmbH Pompe pour refoulement des gaz et pour génération de pression différentielle

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2413636A (en) * 1946-08-30 1946-12-31 James M Long Compressor unit
DE4233990C2 (de) * 1992-10-09 1995-01-05 Kaercher Gmbh & Co Alfred Hochdruckreinigungsgerät

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB865223A (en) * 1958-10-28 1961-04-12 Girling Ltd Improvements in hydraulic devices of the vane type
FR1556723A (fr) * 1967-03-15 1969-02-07
FR2004816A1 (fr) * 1968-03-27 1969-12-05 Lysaght Ltd John
EP0394720A1 (fr) * 1989-04-28 1990-10-31 Balzers-Pfeiffer GmbH Pompe pour refoulement des gaz et pour génération de pression différentielle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10232388A1 (de) * 2002-07-17 2004-02-05 Bernt Renner Vorrichtung zum Fördern eines Fluids

Also Published As

Publication number Publication date
WO1999022118B1 (fr) 1999-06-10
JP2001521100A (ja) 2001-11-06
KR20010031243A (ko) 2001-04-16
DE59805259D1 (de) 2002-09-26
ATE222638T1 (de) 2002-09-15
CA2308709A1 (fr) 1999-05-06
DE19747445A1 (de) 1999-05-06
EP1034356B1 (fr) 2002-08-21
EP1034356A1 (fr) 2000-09-13
CN1276848A (zh) 2000-12-13

Similar Documents

Publication Publication Date Title
EP2318662A2 (fr) Moteur à piston
DE60215467T2 (de) Kolbenschmiersystem für einen hubkolbenverdichter mit einem linearmotor
WO2017063751A1 (fr) Moteur à combustion interne à double manivelle et à compression variable
DE4326408C2 (de) Vielfach-Axialkolbenverdichter
DE3150654C2 (de) Rotationskolben-Brennkraftmaschine
EP1034356B1 (fr) Dispositif pour le transport d'un milieu ou pour l'entrainement a travers un milieu
EP0136565A2 (fr) Dispositif comprenant un moteur à pistons et un mécanisme d'entraînement
DE19954728A1 (de) Drehkolbenvorrichtung
DE60203777T2 (de) Kraftstoffeinspritzpumpe
EP2356317B1 (fr) Moteur à piston rotatif, unité avec système de commande et procédé pour le fonctionnement synchronisé d'un moteur à piston rotatif
WO2017016644A1 (fr) Système de compression
DE3624382C2 (fr)
DE102010006466B4 (de) Rotationskolbenmotor
DE2909715A1 (de) Verbrennungsmotor mit scheibenfoermigen kolben
DE2652228A1 (de) Rotationsmotor
DE3401790A1 (de) Hubkolbenverdichter
DE3820632C2 (fr)
DE3313611A1 (de) Motor-/pumpen-aggregat
DE19849165A1 (de) Brennkraftmaschine
EP2247855B1 (fr) Compresseur à piston à bielle
DE2308310A1 (de) Kraft- und arbeitsmaschine, insbesondere verbrennungsmotor
EP0292680A2 (fr) Machine à piston rotatif avec deux cylindres disposés en paralléle l'un par rapport à l'autre
DE2431209A1 (de) Verbrennungskraftmaschine
EP0065520A1 (fr) Machine pouvant travailler comme moteur, compresseur ou pompe
DE3502862A1 (de) Pumpe

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 98810418.0

Country of ref document: CN

AK Designated states

Kind code of ref document: A1

Designated state(s): CA CN JP KR US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE

AK Designated states

Kind code of ref document: B1

Designated state(s): CA CN JP KR US

AL Designated countries for regional patents

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 1998959808

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 1020007004225

Country of ref document: KR

ENP Entry into the national phase

Ref document number: 2308709

Country of ref document: CA

Ref document number: 2308709

Country of ref document: CA

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 09530333

Country of ref document: US

WWP Wipo information: published in national office

Ref document number: 1998959808

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 1020007004225

Country of ref document: KR

WWG Wipo information: grant in national office

Ref document number: 1998959808

Country of ref document: EP

WWW Wipo information: withdrawn in national office

Ref document number: 1020007004225

Country of ref document: KR

WWW Wipo information: withdrawn in national office

Ref document number: 1998959808

Country of ref document: EP