EP3660267A1 - Machine à piston - Google Patents

Machine à piston Download PDF

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Publication number
EP3660267A1
EP3660267A1 EP19205086.2A EP19205086A EP3660267A1 EP 3660267 A1 EP3660267 A1 EP 3660267A1 EP 19205086 A EP19205086 A EP 19205086A EP 3660267 A1 EP3660267 A1 EP 3660267A1
Authority
EP
European Patent Office
Prior art keywords
piston
cooling
wall
chamber
opening
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
Application number
EP19205086.2A
Other languages
German (de)
English (en)
Other versions
EP3660267B1 (fr
Inventor
Manfred Rapp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Rapson GmbH
Original Assignee
Rapson GmbH
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
Application filed by Rapson GmbH filed Critical Rapson GmbH
Publication of EP3660267A1 publication Critical patent/EP3660267A1/fr
Application granted granted Critical
Publication of EP3660267B1 publication Critical patent/EP3660267B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/06—Heating; Cooling; Heat insulation
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0096—Heating; Cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C21/00—Oscillating-piston pumps specially adapted for elastic fluids
    • F04C21/002—Oscillating-piston pumps specially adapted for elastic fluids the piston oscillating around a fixed axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C9/00—Oscillating-piston machines or pumps
    • F04C9/002—Oscillating-piston machines or pumps the piston oscillating around a fixed axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the application relates to a piston machine which has a housing with a chamber which has an essentially circular sector-shaped cross section, a pivotable piston which is designed as a pivoting element and is arranged in the housing and has a first working surface, the housing and the piston defining at least one first variable working chamber, has a drive or output connected to the piston and an outlet arranged in the working chamber for discharging a working fluid.
  • Piston machines of the type mentioned at the outset which are used as work machines in the form of piston pumps and piston compressors or as power machines in the form of internal combustion engines, compressed gas motors or hydraulic motors for converting the pressure generated in the work space into motion, are known from the prior art.
  • a piston machine which has a piston designed as a double pivoting plate.
  • the piston which is arranged in an approximately circular sector-shaped housing, is pivotably mounted by means of a rotary cylinder formed thereon and divides the housing into two separate working chambers, each provided with inlet and outlet valves.
  • a piston engine is also disclosed.
  • the piston machine is equipped with two pistons designed as double swivel plates.
  • a housing of the piston engine is formed from two or more housing segments which are each shaped as a circular cylinder segment, but rotated by 180 degrees, integrally joined together, forming a common cavity, with each housing part associated with pistons, each synchronously driven in the opposite direction and arranged in parallel with one another, with the respectively adjacent oblique side wall define an outer working chamber and an inner working chamber between the double piston plates with third and fourth inlet and outlet valves formed in a rear wall at the level of an imaginary dividing line between the adjacent housing parts.
  • the invention is based on the object of further developing a piston machine of the type mentioned at the outset so that it can be operated with greater effectiveness.
  • the object is achieved with a piston machine designed according to the features of the main claim.
  • Appropriate developments of the application are the subject of the subclaims and the exemplary embodiments.
  • the piston machine comprises a housing with a chamber which has an essentially circular sector-shaped cross section, and a piston which is designed as a pivoting element and is arranged in the housing and has a first working surface, the housing and the piston defining at least one first variable working chamber. Furthermore, the piston machine comprises an input or output connected to the piston and an outlet arranged in the working chamber for discharging a working fluid.
  • the housing has a cooling opening to the chamber in at least one housing wall, at least for convective cooling of a side of the piston opposite the first working surface by means of a cooling fluid. A cooling fluid can be introduced into the chamber through the cooling opening, as a result of which the temperature of the piston and / or the working fluid and / or the housing and / or the chamber can be reduced.
  • a working volume of the variable working chamber is typically reduced by the cooling opening.
  • the piston machine can be operated with greater effectiveness by cooling.
  • other surfaces of the piston and one or more housing walls or parts of the chamber can also be intensively cooled.
  • the chamber is delimited by a wall which is circular in cross section.
  • the wall which is circular in cross section is referred to as "circular wall”.
  • the cooling opening can be provided, for example, in the circular wall.
  • the chamber can be flushed by means of a cooling fluid through the opening in the arcuate wall, as a result of which the chamber can be effectively cooled.
  • hot re-expansion gases after compression be removed from the chamber in the chamber by a flushing process using the cooling fluid. In this way, the efficiency of the piston machine can be further increased.
  • a swivel angle (see, for example, angle ⁇ in the Figures 1-6 ) of the piston can define the maximum deflection of a pivoting movement of the piston from one dead center to the next dead center.
  • the swivel angle is preferably 90 90 °, typically ⁇ 60 °. However, the swivel angle is preferably greater than 40 °. Depending on the pressure conditions, different swivel angles can be used. Smaller swivel angles can also be used, in particular for metering pumps, for example ⁇ 10 °.
  • a center point angle in a circle is typically specified by the ratio of an arc to the radius r of the associated circle. It can be provided that the opening in the arcuate wall by a first center angle (see, for example, angle ⁇ in the Fig. 2 ) is defined, which is at most as large as the swivel angle (a) of the piston. In a further development, the arcuate wall defines a second center angle (see, for example, angle ⁇ in the Fig. 6 ), which is, for example, at most as large as the swivel angle. The second center point angle is preferably less than 50% of the swivel angle.
  • a piston side facing the arcuate wall is preferably arcuate in cross section and can have a third center angle (see, for example, angle ⁇ in the Fig. 10 ) define.
  • the second center angle ( ⁇ ) of the arcuate wall is, for example, exactly the same size as the third center angle ( ⁇ ) of the piston side. However, the second center angle can also be smaller or larger than the third center angle.
  • the first center angle ( ⁇ ) can be larger or smaller than or as large as the second ( ⁇ ) and / or third center angle ( ⁇ ) mentioned.
  • the dimensions of the above-mentioned circular arc-shaped piston side, the circular arc-shaped wall and the opening in the circular-arc-shaped wall can thus be varied and coordinated, depending on how much cooling is required or depending on how large a delivery or working volume of the piston machine should be.
  • the piston is typically pivotable about a pivot axis.
  • the pivot axis can define an axial direction.
  • a radial direction can be defined perpendicular to the axial direction and perpendicular to the swivel direction.
  • the opening in the arcuate wall extends over an entire axial extent of the arcuate wall.
  • a pivoting movement of the piston defines a pivoting plane.
  • the chamber is preferably delimited by a front wall and a rear wall, wherein the front wall and the rear wall can be formed parallel to the pivot plane.
  • the cooling opening is formed in the front wall and / or in the rear wall. With this design, cooling can be achieved in a manner similar to that for the above-described design of the cooling opening in the circular wall.
  • the cooling opening in the rear wall and / or front wall extends, for example, over an entire radial extent of the rear wall and / or the front wall.
  • the drive or output typically comprises at least one crankshaft with a crank pin.
  • the crank pin engages, for example, in a connecting rod eye of a connecting rod connected to the piston or in a guide groove of a connecting rod loop fixedly connected to the piston.
  • a person skilled in the art is familiar with the fact that there are many possibilities for the design of the drive or the output.
  • a speed of the crankshaft is typically more than 1500 min -1 . The speed can even be up to 8000 min -1 or more.
  • the piston working area is typically the area of the piston through which or at work. It can further be provided that the piston has a second working surface on a side opposite the first working surface and the piston and the housing define a second variable working chamber with a second outlet valve arranged therein, the cooling opening separating the first working chamber from the second working chamber or lies at least on a dividing line between the first working chamber and the second working chamber. Work can then be performed alternately from the first work surface and from the second work surface, depending on which variable work chamber is just closed and open. The convective cooling by means of the cooling fluid then usually takes place at least on the opposite side of the working surface of the piston.
  • the cooling opening is preferably in the circular wall, for example in the middle of the circular wall, and / or in the front wall and / or in the rear wall.
  • the two working chambers are typically opened and closed alternately during a complete swivel movement or a rotation of the crankshaft of 360 °.
  • the open working chamber is rinsed, for example, by means of the cooling fluid, while a working fluid can be conveyed or compressed in the closed working chamber. With this configuration of the piston machine, the flushing and cooling process mentioned can thus be carried out particularly effectively.
  • the working chamber is opened or closed depending on the pivoting position of the piston.
  • the cooling fluid preferably flows into the working chamber and at least convectively cools the side of the piston opposite the working surface and / or rinses the working chamber.
  • the chamber can further be delimited by a first side wall facing away from the first working surface, the cooling opening being provided in the first side wall.
  • the chamber is typically delimited by a second side wall facing the first working surface.
  • the variable working chamber can be delimited by the piston, the second side wall, the arcuate, the front wall and the rear wall. If the cooling opening is only provided in the first side wall facing away from the working surface, the working chamber is therefore usually not flushed by means of the cooling fluid. Instead, this design allows permanent convective cooling of the side of the piston opposite the working surface.
  • the cooling opening in the first side wall can extend over an entire radial and / or axial extension of the side wall.
  • the cooling opening preferably even extends over the entire first side wall, ie the first side wall is omitted. This can further increase the cooling effect.
  • one or more housing walls can be removed in whole or in part, whereby a working volume of the chamber is reduced, but overall the working quality of the piston machine can be improved.
  • the arcuate wall and / or the front wall and / or the rear wall and / or the said side wall is / are divided into two by the cooling opening.
  • the cooling opening can in particular be provided in a housing wall, where there is space and a good flow of cooling fluid is ensured.
  • the cooling opening can be formed by various shapes in the housing wall, e.g. a groove, a sector of a circle or a circle or another shape.
  • Several cooling openings can also be provided in different walls, e.g. in the arcuate wall and / or the front wall and / or the rear wall and / or the side wall. The cooling openings mentioned can be combined with one another.
  • one cooling opening can be designed as a cooling fluid inlet and the other cooling opening as a cooling fluid outlet.
  • a cooling opening is formed in the rear wall and in the front wall.
  • the cooling fluid can e.g. be let into the chamber through the cooling opening of the rear wall or the front wall and be discharged through the cooling opening of the front wall or the rear wall.
  • the cooling opening can also be provided in the arcuate wall and in the rear wall and / or in the front wall. In this configuration, the cooling fluid can e.g. be let into the chamber through the cooling opening in the arcuate wall and be left out through the cooling opening in the rear wall and / or in the front wall.
  • cooling openings in different housing walls are also conceivable, in which the cooling fluid is let into the chamber through a cooling opening and is let out of the chamber through the other cooling opening.
  • the chamber can be flushed particularly well by means of the cooling fluid.
  • cooling openings can have different sizes or even be shared.
  • the cooling openings can be designed differently in width and length.
  • cooling fluid air, CO 2 or other gases or a liquid such as water
  • the piston machine can be operated, for example, as a pump, vacuum pump, compressor or motor.
  • a second wall with a circular arc in cross-section can be fastened to the piston, which is arranged on a smaller radius than a maximum radial extension of the piston and engages in a passage of a side wall at least in a pivoted position of the piston, the cooling opening preferably likewise is provided in this side wall.
  • the cooling opening forms the inlet for the second wall which is circular in cross section.
  • the cooling opening provided in the side wall can be provided, viewed from the pivot axis, above or below the second arcuate wall.
  • the second arcuate wall is preferably also cooled by the cooling fluid.
  • a second variable working chamber can then be defined at least by the second arcuate wall, the piston and the side wall.
  • an inlet valve is arranged in the working chamber, at least for admitting the working fluid into the working chamber.
  • the cooling opening differs from the inlet valve.
  • the outlet is designed as an outlet valve.
  • the cooling opening differs from the exhaust valve.
  • An inlet and an outlet valve can thus be arranged in the working chamber, for example in the rear wall, front wall, side wall and / or in the circular wall. Alternatively, the inlet valve can also be dispensed with.
  • the piston has cooling fins for convective cooling.
  • the cooling fins are preferably on the side of the piston opposite the working surface.
  • the piston can also be designed as a hollow body. The cooling of the piston can be further improved by the cooling fins and / or the design as a hollow body.
  • a size of the cooling opening can be variably controlled or adjusted, preferably by means of a control element arranged in a housing wall, or a slide or throttle valve.
  • a size of the opening can be controlled or reduced or enlarged in order to influence or regulate a cooling air throughput.
  • the piston machine can thus be adapted to different performance requirements, and the cooling effect can be controlled during operation.
  • the variably controllable cooling opening can be opened or closed mechanically more or less as required, for example by moving a camshaft.
  • the variably controllable cooling opening can also be controlled by an electronic control device in order to vary a size of the cooling opening as required during the operation of the piston machine.
  • a pressure sensor and / or a temperature sensor are provided in the chamber and / or in the piston, which can be connected to the control device and / or an evaluation device.
  • the cooling opening can be opened or closed more or less or its size can be enlarged or reduced. If the measured temperature e.g. is less than a certain threshold value, the cooling opening can be closed in order to increase a delivery volume of the piston machine.
  • the delivery volume of the piston machine, cooling fluid throughput, pressure and temperature can be influenced by means of the variably controllable cooling opening in order to increase the efficiency of the piston machine.
  • the cooling fluid can move through the piston through the cooling opening be sucked.
  • a cooling device preferably a blower or a pump, can be provided for conveying the cooling fluid through the opening of the housing and into the chamber. This makes cooling even more efficient.
  • a venturi tube can be provided at the cooling opening, which can increase the throughput considerably.
  • the housing can have two or more housing parts which are each shaped as a sector of a circle but joined together by 180 degrees and form a common cavity, a piston being assigned to each housing part. Two adjacent housing parts then define, together with their pistons, at least one variable working chamber. Further details can be found, for example, in the publication DE 10 2010 036 977 B3 .
  • a cooling opening can be provided in at least one chamber.
  • several or all of the chambers can also have cooling openings.
  • piston machine designed as a compressor, e.g. compression to 10 bar and higher, e.g. up to 20 bar, possible with single-stage compression. Furthermore, the piston machine allows an oil-free mode of operation, which is particularly desirable for use as a vacuum pump, compressor or expansion motor.
  • Fig. 10 is a piston machine according to the prior art DE 10 2008 040 574 A1 shown, which is made part of the present application.
  • the piston machine comprises a housing 1, which includes a chamber 2, a bearing housing 3 and a crankcase 4.
  • the chamber 2 has a circular sector-shaped cross section and is in accordance with the shape of a cylinder sector by two side walls 5, 6 arranged at an angle ⁇ of approximately 53 ° to one another, a front end wall (not shown) and a rear end wall 7 and a wall 8 and limited a rotary cylinder 9.
  • a bearing housing 3 formed by two opposing bearing shells adjoins the ends of the side walls 5, 6 opposite the circular wall 8.
  • a crankcase 4 partially filled with an oil sump 12 is provided.
  • the rotary cylinder 9, which is rotatable about an axis of rotation 14, is mounted in the bearing housing 3.
  • the chamber 2 is hermetically sealed with respect to the crankcase 4, for example with sealing strips 13 integrated into the bearing housing 3.
  • a piston 15 designed as a swivel plate and a connecting rod 16 are rigidly fastened or integrally formed on the rotating cylinder 9 diametrically opposite one another.
  • the connecting rod 16 has a guide groove 17 extending over its entire length, into which a crank pin 18 of a crankshaft 19 rotatably mounted in the crankcase 4 engages.
  • the piston 15, which is typically designed as a hollow body, is located in the working chamber 2 and has a sealing edge with an upper edge 28 on an inner surface of the curved circular wall 8.
  • the upper edge 28 of the piston 15 is circular in cross-section and is defined by a central angle ⁇ of approximately 8 °.
  • Inlet walls 22, 24 and outlet valves 23, 25 are formed in each of the two side walls 5, 6 of chamber 2.
  • a pivoting movement of the piston 15 defines a swivel plane, the rear end wall 7 and the front end wall being parallel to the swivel plane.
  • the angles ⁇ and ⁇ mentioned can also be larger or smaller than in the example shown.
  • the piston machine described above can operate as a piston pump or as a piston compressor as follows, but can also function as an internal combustion engine with internal or external combustion that is not described in the function here: during a rotary movement of a crankshaft 19, a crank pin 18 sliding on a crank radius 11 slides in a guide groove 17 a connecting rod 16. This transmits a pivoting movement to the piston 15. With a pivoting movement of the piston 15 from the in the Fig. 10 position shown on the left side wall 5 of the chamber 2 to the right side wall 6, the left inlet valve 22 and the right outlet valve 25 are open, while the left outlet valve 23 and the right inlet valve 24 are closed. A previously sucked-in fluid is thus expelled from the chamber 2 via the right outlet valve 25.
  • the piston 15 thus works as a double piston with two working surfaces 29 and 30, which performs two pivoting movements when the crankshaft 19 rotates, that is to say from the left dead center on the left side wall 5 to the right dead center on the right side wall 6 and back.
  • the oil sump 12 takes over the lubrication of the crank mechanism, that is, the guide groove 17 and the crank pin 18 sliding in it, which can also be formed with roller bearings and sliding blocks.
  • the guide groove 17 can also be arranged in the piston 15. This enables a very compact design.
  • crank pin 18 of the crankshaft 19 is connected to the piston 15 in an articulated eye Connecting rod engages.
  • the drive or output of the piston machine is therefore not limited to the illustrated embodiments.
  • the Fig. 1 differs from that Fig. 10 by the fact that the housing 1 has a cooling opening 51 to the chamber 2 in the circular wall 8. Also, in contrast to the execution of the Fig. 10 no inlet and outlet valves are provided in the side wall 6. A cooling fluid, in the example shown air, flows through the cooling opening 51 into the chamber 2 and cools it. In addition, the piston 15 is convectively cooled by the air on at least one side 32 opposite the working surface 30.
  • the piston engine of the Fig. 1 is designed as a compressor, for example, and cooling by means of the cooling opening can increase the efficiency of the compressor.
  • a second cooling opening 51 ' can be provided in the side wall 6.
  • the second cooling opening is designed, for example, as a cooling fluid outlet through which the cooling fluid can flow out.
  • a flow direction of the cooling fluid is indicated in the figure by means of arrows.
  • the piston engine of the Fig. 2 differs from the embodiment of the Fig. 10 in that a cooling opening 52 is provided in the center of the circular wall 8. While in the execution of the Fig. 1 in one revolution of the crankshaft 19, two work cycles, namely suction and compression, are possible, in the embodiment of FIG Fig. 2 four work cycles. Due to the central design of the cooling opening 52, the working chamber 2 can be flushed alternately on the left and right with cooling fluid. Depending on the pivoting position of the piston 15, the working chamber 2 opens or the working chamber 2 closes.
  • the cooling opening 52 in the circular wall 8 is both in the Fig. 1 as well in the Fig. 2 defined by a center angle ⁇ , which is smaller than a pivot angle ⁇ of the piston 15. In the Fig.
  • the openings 51 and 52 in the circular wall 8 extend over an entire axial extent of the circular wall 8. That is, the openings 51 and 52 are formed as an elongated groove in the circular wall and extend from the front end wall to the rear end wall 7. Alternatively, the cooling opening 51 and 52 can also have a smaller axial extent.
  • the Fig. 3 differs from that Fig. 10 in that a cooling opening 53 is arranged in the rear end wall 7. Also, in contrast to the execution of the Fig. 10 no inlet and outlet valves are provided in the side wall 6. Furthermore, the piston 15 has only one working surface 30.
  • the embodiment of the Fig. 4 differs from the embodiment of Fig. 10 in that a cooling opening 54 is arranged centrally in the rear end wall 7. Like in the Fig. 2 here too the opening 54 is arranged in the center.
  • the opening 53 of the Fig. 3 when the piston 15 closes on the right side wall 6, the piston 15 closes the opening 54 when the piston 15 is in the central position Fig. 4 .
  • Both the opening 53 of the Fig. 3 as well as the opening 54 of the Fig. 4 extends over an entire radial extent of the end wall 7 from the bearing housing 3 to the wall 8 in the form of a circular arc.
  • the opening 53 and 54 is also provided in the front end wall (not shown). It is also possible to provide only one opening 53 and 54 in the front end wall or in the rear end wall 7.
  • the piston 15 of the Fig. 1 and 3rd has only one working surface 30, the piston 15 comprises Fig. 2nd and 4th In addition to a first work surface 30, a second work surface 29.
  • the cooling opening 52 and 54 of the Fig. 2nd and 4th separates a first working chamber from a second working chamber.
  • the arcuate wall 8 are the Figure 2 and the end wall 7 of the Figure 4 divided in two by the cooling opening 52 or cooling opening 54.
  • the piston engine of the Fig. 5 differs from the embodiment of Fig. 10 in that a cooling opening 55 is provided in the side wall 6. Also, in contrast to the execution of the Fig. 10 no inlet and outlet valves are provided in the side wall 6. As a result, the piston 15 has only one working surface 30.
  • the cooling opening 55 in the side wall 6 extends over an entire radial and axial extension of the side wall 6. That is, in the embodiment of FIG Fig. 5 the entire side wall 6 was dispensed with. This enables a constant convective cooling of the piston 15 on a side 32 opposite the working surface.
  • the variable working chamber of the Fig. 5 completed in each pivot position of the piston 15.
  • the execution of the Fig. 6a differs from the execution of the Fig. 10 in that the side wall 6 is completely omitted and in addition that an opening 51 is provided in the arcuate wall 8. Also, in contrast to the execution of the Fig. 10 no inlet and outlet valves are provided in the side wall 6 and the piston 15 has only one working surface 30.
  • the execution of the Fig. 6a thus represents a mixed form of Fig. 5 and 1
  • the circular arc-shaped wall 8 of the Fig. 6a defines a second center angle ⁇ of approximately 25 °, which is smaller than the previously described pivot angle ⁇ of the piston 15.
  • the opening 51 in the arcuate wall 8 is defined by the center angle ⁇ .
  • the angles ⁇ and ⁇ are equal. However, they can also differ from one another in other embodiments.
  • the central angle ⁇ can be larger or smaller than the central angle ⁇ .
  • a cooling opening 52 and 54 is provided in the arcuate wall 8 and in the rear end wall 7.
  • the execution of the Fig. 6b is thus a mixed form of training Fig. 2nd and 4th .
  • the cooling opening 54 of the rear end wall 7 does not extend over an entire radial extent of the end wall 7, but rather up to a third of the radial extent of the end wall 7.
  • the cooling fluid is circulated in a circular shape by means of a fan 60 through the cooling opening 52 designed as a cooling fluid inlet Wall 8 let into chamber 2.
  • the cooling fluid is then discharged from the chamber 2 through the cooling opening 54 in the form of a cooling fluid outlet in the rear end wall 7.
  • the direction of flow of the cooling fluid is indicated by arrows.
  • the chamber 2 can thus be flushed particularly well by means of the cooling fluid.
  • a cooling opening can be provided in the front end wall (not shown).
  • a cooling opening 54 and 54 ' is provided in the rear end wall 7 and in the front end wall.
  • a projection of the cooling opening 54 'of the front end wall onto the rear end wall 7 is shown in FIG Figure 6c indicated by dashed lines.
  • cooling fluid is admitted into the chamber 2 by means of an optional blower (not shown) through the cooling opening 54 in the form of a cooling fluid inlet in the front end wall.
  • the cooling fluid is then discharged from the chamber 2 through the cooling opening 54 ′ in the form of a cooling fluid outlet in the rear end wall 7.
  • the direction of flow of the cooling fluid is indicated by an arrow.
  • the chamber 2 can thus be flushed particularly well by means of the cooling fluid.
  • the direction of flow can also be reversed.
  • a blower blows the cooling fluid into the chamber 2 through the cooling opening 54 of the rear end wall.
  • the cooling fluid leaves the chamber 2 after flushing the chamber 2 through the cooling opening 54 'of the front end wall.
  • variable working chamber is closed or opened depending on the swivel position of the piston.
  • the piston engine of the Fig. 6d differs from the embodiment of Fig. 10 in that a cooling opening 55 is provided in the side wall 5.
  • a second wall 70 with a circular arc in cross section is fastened to the piston 15, which is arranged on a smaller radius than a maximum radial extension of the piston 15 and engages in the cooling opening 55 of the side wall 5. This results in a constant convex cooling of the second arcuate wall.
  • the cooling opening 55 which is likewise designed as a passage for the second circular wall 70, is provided above the second circular wall 70 as seen from the pivot axis 14. It can of course also be arranged below the second circular wall 70.
  • a second variable working chamber is defined by the second arcuate wall 70, the piston 15, the side wall 5, the front wall and the rear wall 7 and is sealed off by these walls.
  • the piston 15 the side wall 5, the front wall and the rear wall 7 and is sealed off by these walls.
  • the Figures 1-6d also differ from the Figure 10 in that a size of the cooling openings 51, 51 ', 52, 53, 54 and 55 each by means of a slide 61, 61' arranged in a corresponding housing wall, 62, 63, 64 and 65 is variably controllable or adjustable.
  • the slide 61, 61 ', 62, 63, 64 and 65 is able to close the chamber 2 flush and is in each case connected to an electronic control device, not shown, which is further connected to a pressure sensor and temperature sensor, not shown, arranged in the piston 15.
  • the control device is configured to control the slide 61, 61 ', 62, 63, 64 and 65 in order to regulate the size of the cooling opening 51, 51', 52, 53, 54 and 55 during the operation of the piston engine or as required enlarge or reduce. From reaching a threshold value of a temperature and / or a pressure in the chamber 2, the cooling opening 51, 51 ', 52, 53, 54 and 55 for cooling the piston 15 and / or the chamber 2 can be opened or closed or their size can be increased or be reduced. If the temperature measured on the piston 15 is, for example, less or more than a certain threshold value, the cooling opening 51, 51 ', 52, 53, 54 and 55 can be closed or opened in order to increase a delivery volume of the piston machine.
  • the slide 61, 61 ', 62, 63, 64 and 65 can alternatively also be actuated by means of a mechanical control device, for example a camshaft, in order to close the cooling opening 51, 51', 52, 53, 54, 55 more or less to open.
  • a mechanical control device for example a camshaft
  • a throttle valve or another control device can also be provided.
  • Cooling fins 31 are provided on a side 32 of piston 15 opposite working surface 30 to increase cooling.
  • an optional blower 60 or cooling device is provided (in Figs Figures 3 , 4th , 6c , 7 , 8th and 9 not shown), which blows air or another cooling fluid into the cooling opening 51, 52, 53, 54 and 55 as required.
  • the blower 60 is also connected to the control device mentioned.
  • the blower 60 is controlled by the control device in particular when the slide 61, 62, 63, 64 and 65 opens or closes the respective opening 51, 52, 53, 54 and 55. If no cooling device is provided, the cooling fluid can move of the piston are sucked through the cooling opening 51, 52, 53, 54 and 55.
  • a venturi tube can be provided at the cooling air inlet opening shown in the figures.
  • cooling fins can be provided on the outside of the housing.
  • FIG. 11A, 11B and 12 are views of cross sections of a piston engine according to the prior art of DE 10 2010 036 977 B3 shown, which are also made part of the present application.
  • Pistons 101 and 102 are connected to a rotary cylinder 106 which is rotatably mounted in the housing 103 about an axis of rotation 104 via a bearing 105 and each have a guide groove 107 on one end face, into which a crankshaft journal 108 of a crankshaft 110 connected to a drive shaft 109 engages.
  • the guide groove 107 functions as a connecting rod loop or piston loop, which is thus an integral part of the pistons 101 and 102.
  • the two crankshafts 110 that are operatively connected to the respective pistons 101 and 102 are like the ones Fig.
  • the housing 103 formed in one piece - indicated by a dashed line X - comprises two housing parts 103a, 103b, but rotated by 180 °, each with an essentially circular sector cross-section, in which the one on the upper housing wall 111 and one on the lower housing wall 112 Rotary cylinders 106 of pistons 101 and 102 are mounted.
  • a chamber A1 and A2 enclosed by the housing thus has the shape of two equal circular sectors lying opposite one another.
  • the housing 103 further comprises a housing rear wall 114 and a housing cover 113 as well as a first side wall 115 and a second side wall 116.
  • the two double pistons 101, 102 which are aligned parallel to each other in each position, are in a starting position, as in FIG Figure 11A shown on the respective side wall 115, 116 and in the disfigurement at the dividing line X almost meet with a defined gap.
  • inlet valves 18a, 18b and 18c and outlet valves 19a, 19b and 19c are arranged in the two side walls 115 and 116 and in the rear wall 114 at the level of the dividing line X.
  • the two pistons 101 and 102 are moved towards one another close to the dividing line X and moved away from one another up to the side walls 115 and 116 by a synchronous but oppositely directed rotational movement of the two crankshaft pins 108 according to arrows 17a, 17b. It is also possible to use only one crankshaft, the pistons 101 and 102 being synchronized, for example, via a gearwheel.
  • the piston machine designed in accordance with the Fig. 11 can be operated, for example, as a compressor, pump or as a motor.
  • a conveying medium located in the inner large working chamber A3 between the two double piston plates 101 and 102 and previously sucked in via the inlet valve 18c is expelled again from the working chamber A3 during the pivoting movement of the double piston plates 101 and 102 in the direction of the separating line X. .
  • a conveying medium is simultaneously sucked into the two outer (small) working chambers A1 and A2, which are formed between the double piston plates 101 and 102 and the side walls 115 and 116, via the inlet valves 18a and 18b.
  • the delivery medium previously sucked into the working chambers A1, A2 is expelled through the outlet valves 19a, 19b and at the same time delivery medium is sucked into the large working chamber A3 via the inlet valve 18c.
  • the maximum volume of the two small outer working chambers A1 and A2 corresponds to the maximum volume of the large, inner working chamber A3.
  • the middle - large - working chamber A3 can work as an expansion motor, while the two outer - small - working chambers A1 and A2 can work as a compressor or as a pump and are driven by the expansion motor.
  • the inner working chamber A3 and an outer (left) working chamber A1 could be operated as the first compressor stage and the other outer working chamber A2 as the second compressor stage.
  • the working chambers A1, A2 and A3 can each perform different functions as a compressor, pump or motor.
  • the embodiment of the 7A-7C differs from the embodiment of Fig. 11 in that cooling openings 151 are provided in the side walls 15 and 16, the cooling openings 151 in the side walls 115 and 116 extending over an entire radial and axial extent of the side walls 115 and 116.
  • the cooling openings 151 allow the pistons 101 and 102 to be at least convectively cooled on each side of the piston opposite the working surface of the piston by means of a cooling fluid.
  • the embodiments of the Fig. 7a to 7c are otherwise similar to the embodiment of FIG Fig. 5 .
  • a cooling opening 151 can also be provided in only one of the side walls 115 and 116. In this case, only one piston 101, 102 is cooled.
  • the embodiment of the 8A-8C differs from the embodiment of Fig. 11 in that two cooling openings 152 are provided in the arcuate wall. Like in the Fig. 11 includes the embodiment of FIG Fig. 8 also three working chambers A1, A2 and A3. A particularly good cooling effect can be achieved in the working chamber A3, since the cooling openings 152 are arranged opposite one another. A cooling fluid, for example air, can thus flow in and out from one side to the other, which is in the Figure 8 is indicated by arrows 130 and 131. The working chambers A1, A2 and A3 and the pistons 101 and 102 can thus be cooled at least convectively by means of a cooling fluid through the cooling openings 152.
  • a cooling fluid for example air
  • the cooling opening 152 is of the same size as an upper edge 140 of the pistons 101 and 102. However, the cooling opening 152 can also be smaller or larger than the upper edge 140 of the pistons 101 and 102. Like in the Fig. 8b It can be seen that there is a swivel position in which all working chambers A1, A2 and A3 are closed. In the swivel position of the Fig. 8c Working chambers A1 and A2 are open, while in the swivel position of the Fig. 8a the working chamber A3 is largely open.
  • the arrangement of the cooling openings 152 in the Fig. 8 is similar to the execution of the Fig. 2 . Alternatively, only one cooling opening 152 can be provided here instead of two cooling openings 152.
  • FIG. 9a the wall, which is circular in cross section, is formed by two parts 111 'and 111 "or 112' and 112", which are located radially at different positions.
  • the radial gap 140 extends in the pivoting direction over a central angle ⁇ and in the axial direction from the housing cover 113 to the rear wall 114 of the housing.
  • the dimensions of the gap 140 can be varied in the radial direction, in the axial direction or in the pivoting direction, depending on the embodiment.
  • the arcuate wall 111 "and 112" is only as large as the upper edge 140 of the piston 101 and 102.
  • the dimensions of the arcuate wall 111 "and 112" can be smaller or larger.
  • the pistons 101 and 102 can be convectively cooled from several sides. A loss of chamber volume is therefore in the Fig. 9a and 9b compensated by an increased cooling effect.
  • the Figures 7-9 also differ from the Figure 11 in that the size of the cooling openings 151 and 152 can be variably controlled or set by means of a slide, not shown, arranged in a corresponding housing wall.
  • the slide is able to close the chamber flush and is each connected to an electronic control device, not shown, which is further connected to a pressure sensor and temperature sensor, not shown, arranged in the pistons 101 and 102.
  • the control device is designed to control the slide in order to regulate or change the size of the cooling opening during the operation of the piston engine. From reaching a threshold value of a temperature and / or a pressure in the chamber, the cooling opening 151 and 152 can be used to cool the piston 101 and 102 and / or the chamber be opened or closed more or less.
  • the cooling opening 151 and 152 can be closed or opened in order to increase a delivery volume of the piston machine.
  • delivery volume, cooling fluid throughput, pressure and temperature can be influenced in order to increase the efficiency of the piston machine.
  • the slide can also be actuated by means of a mechanical control device, for example a camshaft, in order to close or open the cooling opening 151 and 152 to a greater or lesser extent.
  • a throttle valve or another control device can also be provided, for example.
  • an optional fan or cooling device is provided (in the Figures 7 , 8th and 9 not shown in each case), which blows air or another cooling fluid into the cooling opening 151 and 152 as required.
  • the blower is also connected to the control device mentioned. The blower is controlled in particular by the control device when the slide opens or closes the respective openings 151 and 152. If no cooling device is provided, the cooling fluid can be drawn in through the cooling opening 151 and 152 by the movement of the piston.
  • a venturi tube can be provided at the cooling air inlet opening shown in the figures.
  • cooling fins can be provided on the outside of the housing.
  • the drive or output of the piston machine is not based on the illustrated embodiments of the Fig. 1 to 9B limited. It can be provided, for example, that the crank pin of the crankshaft engages in a connecting rod eye of a connecting rod that is articulated to the piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP19205086.2A 2014-05-12 2015-05-12 Machine à piston Active EP3660267B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102014208939.5A DE102014208939A1 (de) 2014-05-12 2014-05-12 Kolbenmaschine
EP15726873.1A EP3143258B1 (fr) 2014-05-12 2015-05-12 Machine à piston à refroidissement
PCT/EP2015/060500 WO2015173255A1 (fr) 2014-05-12 2015-05-12 Machine à piston à refroidissement

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP15726873.1A Division EP3143258B1 (fr) 2014-05-12 2015-05-12 Machine à piston à refroidissement

Publications (2)

Publication Number Publication Date
EP3660267A1 true EP3660267A1 (fr) 2020-06-03
EP3660267B1 EP3660267B1 (fr) 2023-04-26

Family

ID=53284203

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EP15726873.1A Active EP3143258B1 (fr) 2014-05-12 2015-05-12 Machine à piston à refroidissement
EP19205086.2A Active EP3660267B1 (fr) 2014-05-12 2015-05-12 Machine à piston

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EP15726873.1A Active EP3143258B1 (fr) 2014-05-12 2015-05-12 Machine à piston à refroidissement

Country Status (6)

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US (1) US10221850B2 (fr)
EP (2) EP3143258B1 (fr)
CN (1) CN106536856B (fr)
DE (1) DE102014208939A1 (fr)
ES (2) ES2950131T3 (fr)
WO (1) WO2015173255A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016119985B3 (de) * 2016-10-20 2018-05-17 Nidec Gpm Gmbh Pendelkolben-Vakuumpumpe
RU2700108C1 (ru) * 2018-06-01 2019-09-12 Федеральное государственное автономное образовательное учреждение высшего образования "Южно-Уральский государственный университет (национальный исследовательский университет)" ФГАОУ ВО "ЮУрГУ (НИУ)" Лопастной двигатель
DE102018123409A1 (de) 2018-09-24 2020-03-26 Manfred Max Rapp Kolbenmaschine, modulares Baukastenystem für eine Kolbenmaschine sowie Verfahren zur Herstellung einer Kolbenmaschine
US20250389237A1 (en) 2022-05-31 2025-12-25 Manfred Rapp Air/steam engine and use thereof
DE102022122759B4 (de) 2022-05-31 2026-02-12 Max Rapp Motorenbau GmbH & Co. KG Luft-dampf-motor und dessen verwendung

Citations (10)

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GB331545A (en) * 1930-03-04 1930-07-04 Paul Polizzi Improvements in internal combustion engines of the oscillating vane type
GB486745A (en) * 1937-02-23 1938-06-09 Johann Haragsin Improvements relating to internal combustion engines
US3408991A (en) * 1967-07-12 1968-11-05 William B Pritchett Jr Oscillating machine
DE2353008A1 (de) * 1973-10-23 1975-04-24 Heinrich Menge Schwingkolbenmaschine
DE3705313A1 (de) * 1987-02-19 1987-10-08 Franz Josef Knott Pendelkolbenmaschine
US5228414A (en) * 1992-09-10 1993-07-20 Robert D. Hall Valveless two-stroke-cycle oscillating engine
WO1995008055A1 (fr) * 1993-09-16 1995-03-23 Pivotal Engineering Limited Moteur a combustion interne
US5979163A (en) * 1997-12-29 1999-11-09 Circular Motion Controls, Inc. Rotationally pivotal motion controller
DE102008040574A1 (de) 2008-07-21 2010-01-28 Manfred Max Rapp Kolbenmaschine
DE102010036977B3 (de) 2010-08-13 2011-11-10 Manfred Max Rapp Kolbenmaschine

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US1363423A (en) * 1919-11-10 1920-12-28 Pierre Auguste Marie Le Rotary gas-engine
AU2182299A (en) * 1999-01-25 2000-08-07 Klein, Benny Expansion-compression engine with angularly reciprocating piston
DE10254162A1 (de) * 2002-11-20 2004-06-03 Renner, Bernt Vorrichtung zum Fördern eines Fluids
DE102005010775B3 (de) * 2005-02-25 2006-04-20 Hüttlin, Herbert, Dr. h.c. Schwenkkolbenmaschine
DE102006024321A1 (de) * 2006-05-24 2007-11-29 Mehdi Nabhani Verbrennungsmotor

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB331545A (en) * 1930-03-04 1930-07-04 Paul Polizzi Improvements in internal combustion engines of the oscillating vane type
GB486745A (en) * 1937-02-23 1938-06-09 Johann Haragsin Improvements relating to internal combustion engines
US3408991A (en) * 1967-07-12 1968-11-05 William B Pritchett Jr Oscillating machine
DE2353008A1 (de) * 1973-10-23 1975-04-24 Heinrich Menge Schwingkolbenmaschine
DE3705313A1 (de) * 1987-02-19 1987-10-08 Franz Josef Knott Pendelkolbenmaschine
US5228414A (en) * 1992-09-10 1993-07-20 Robert D. Hall Valveless two-stroke-cycle oscillating engine
WO1995008055A1 (fr) * 1993-09-16 1995-03-23 Pivotal Engineering Limited Moteur a combustion interne
US5979163A (en) * 1997-12-29 1999-11-09 Circular Motion Controls, Inc. Rotationally pivotal motion controller
DE102008040574A1 (de) 2008-07-21 2010-01-28 Manfred Max Rapp Kolbenmaschine
DE102010036977B3 (de) 2010-08-13 2011-11-10 Manfred Max Rapp Kolbenmaschine

Also Published As

Publication number Publication date
CN106536856A (zh) 2017-03-22
WO2015173255A1 (fr) 2015-11-19
ES2766473T3 (es) 2020-06-12
EP3143258B1 (fr) 2019-10-30
CN106536856B (zh) 2019-06-21
DE102014208939A1 (de) 2015-11-12
ES2950131T3 (es) 2023-10-05
US20170138359A1 (en) 2017-05-18
US10221850B2 (en) 2019-03-05
EP3143258A1 (fr) 2017-03-22
EP3660267B1 (fr) 2023-04-26

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