EP0204011B1 - Aggregate with through flow by a fluid - Google Patents

Aggregate with through flow by a fluid Download PDF

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Publication number
EP0204011B1
EP0204011B1 EP85106624A EP85106624A EP0204011B1 EP 0204011 B1 EP0204011 B1 EP 0204011B1 EP 85106624 A EP85106624 A EP 85106624A EP 85106624 A EP85106624 A EP 85106624A EP 0204011 B1 EP0204011 B1 EP 0204011B1
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EP
European Patent Office
Prior art keywords
piston
shaft
cylinder
cover
inlet
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.)
Expired - Lifetime
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EP85106624A
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German (de)
French (fr)
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EP0204011A1 (en
Inventor
Karl Eickmann
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Individual
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Individual
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Priority to DE19833341718 priority Critical patent/DE3341718A1/en
Application filed by Individual filed Critical Individual
Priority to AT85106624T priority patent/ATE57741T1/en
Priority to DE8585106624T priority patent/DE3580271D1/en
Priority to EP85106624A priority patent/EP0204011B1/en
Publication of EP0204011A1 publication Critical patent/EP0204011A1/en
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Publication of EP0204011B1 publication Critical patent/EP0204011B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B11/00—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type
    • F01B11/001—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type in which the movement in the two directions is obtained by one double acting piston motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B17/00—Reciprocating-piston machines or engines characterised by use of uniflow principle
    • F01B17/02—Engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/003—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 free-piston type pumps

Definitions

  • the present invention relates to an assembly through which fluid flows, as described in the preamble of claim 1.
  • the invention is therefore based on the object to limit the disadvantages of the known technology and to create a reliable unit with particularly high performance with structural simplicity and low weight.
  • Figure 1 shows the simplest exemplary embodiment of the invention in longitudinal section.
  • the piston 4 with its piston rod 7, which extends in the axial direction and which, near its end on the other side, has the control groove 15 which extends around the entire circumference and is open radially outwards and which is ended at the other end by the piston rod extension 777.
  • This arrangement reciprocates in the cylinder and its cover 3, the cylinder being provided with the outlet slots 6 at one end and the cover 3 at the other end, while the cover 3 has an inlet port 9 and an inlet space 315 , as well as a backward closing part 333, which can grip around the piston rod extension 777 or part of the piston rod 7 in a sealing manner.
  • the invention is further developed for special advantageous designs, the corresponding parts in the relevant figure descriptions being given the same reference numerals, but the reference numbers for identifying the special types of design are provided with additional digits, that is to say the single-digit digits are represented by multi-digit digits are added, etc.
  • the invention has been expanded to a double piston in order to be able to achieve twice the power with the same crankshaft.
  • the piston 4 therefore has at its rearward end a central connection 60 which supports or forms the second piston 64 at its other end, from which the second piston rod 67 extends in the axially opposite direction relative to the first piston 4 of the invention the first cylinder 2 has a corresponding axial extension 62.
  • the second parts again have the arrangements of the invention, namely the control groove 45, the cover 3, the closure part 2333, the extension 2777 and so on.
  • FIG. 3 shows how the outlet slots 6, 66 are distributed around the circumference of the cylinder, or how they can end in certain collecting channels 17, 19 as outlets 18, 20.
  • FIG. 4 approximately as in FIG. 2, but the middle connection between the first and the second piston is not effected by the connection 60, but by connection of the individual of the two pistons 4, 64 by means of connecting rod bolts and connecting rods 46 , 55 to the eccentric bearing 54 of a crankshaft 56, 52, 54.
  • the middle connection 60 is hollow, that is, it forms a tube and can receive the openings 160 for the through-flow of fluid. This can also be used to cool the piston parts.
  • inner covers 760 closing the space 560 are arranged in the hollow pipe connection 60 in order to allow fluid flow around the central connection through the windows 160, 660.
  • the outlet slots are designed as slots 666, which lead to seats which close against the collecting space 319 in the housing 316 by the check valves 306 (possibly loaded with springs 406).
  • connection is replaced by pipe parts of larger diameter and provided with brackets 411 which connect the pipe parts 404, 464 nested one inside the other.
  • This design avoids a gap between the cylinder and the connection between the pistons, so that for this reason no (or only a little) fluid can flow back from the outlet collecting space 19 into the interior of the cylinder.
  • this figure has a turbocharger 440, the turbine of which is operated via channel 441 by means of the outflows from outlets 6, 66, while the other of which is via lines 442, 443 to inlets 9, 999 of the first and second cylinder chambers 1, 61 delivers pre-compressed fluid, for example air or fuel-air mixture.
  • FIG. 8 illustrates the short cylinder parts 362 for sealing the piston in one of the axial end positions of the movement, and for the rest this figure clearly shows the parts according to the invention for the first and second pistons.
  • Figures 9 and 10 show different positions of the double pistons.
  • FIG. 11 shows an aggregate for achieving high efficiencies at different loads, etc., the designs according to the invention appearing in the figure, but the otherwise essential and new of this figure can also be arranged on aggregates without the features of the invention.
  • the first and second cylinders 2 and 62 are mounted in an outer housing 161 so as to be displaceable in the axial direction.
  • the cylinders can thereby be moved closer to the central axis of the crankshaft 56 or further away from it. This shift can also take place during operation of the unit in this figure. In this way, one can arbitrarily enlarge and reduce the combustion chamber of an internal combustion engine or the compression ratio of an engine, or compressor or expansion device. This allows the efficiency to be changed and losses of the units with fixed, non-displaceable cylinders to be avoided or restricted.
  • Figure 12 shows the axial end parts of the assembly of the invention and seals that can be used thereon, such as sealing rings 11 in sealing ring chambers 10, pressure lines to the chambers 10 for pressing the sealing rings with their sealing surfaces 97 and sealing surfaces of adjacent parts, as well as structural details without reference numerals since they are only for the production matter.
  • FIG. 707 The illustration of a further embodiment of the invention begins with FIG.
  • the double pistons are not connected to each other by a middle connection, but the piston rods 7 and 207 are connected to each other by a connection 707.
  • the connection 707 forms the extensions 777 of the figures described earlier and replaces them. Accordingly, one has between the piston rods 7 and 207, as prescribed by the invention and claim 1, a control groove 15 and 215, respectively.
  • the cover is arranged here between the two pistons 4 and 44 and must, according to claim 1 of the invention Kol benstangen and their extensions, ie temporarily parts of the piston rods 7, 207 and the extensions, ie the part 707, embrace and seal.
  • the cover 3, 40 therefore has the cover parts 3003 and 4003 sealing these parts, between which the common inlet space 50 is formed and connection 9 is connected to the inlet.
  • connection 9 is connected to the inlet.
  • the common space 50 replaces the individual spaces 315 of the figures described earlier.
  • the control groove 15 When the piston arrangement is reciprocated, the control groove 15 temporarily connects the inlet 9 to the cylinder chamber 1, while the control groove 215 temporarily connects the inlet 9 to the cylinder chamber 61 at another time.
  • the outlet slots 6 are again arranged on the axial end part of the cylinder in question lying opposite the cover, so that the outlets 6 can be seen near the right and left ends of the figure, while in the previously described double-piston units they are located approximately in the middle of the relevant figures were found.
  • FIG. 14 shows a longitudinal section through the center insert 40, which forms the two covers 3003 and 4003 beyond the common inlet chamber 50.
  • the inlets 9 have not yet been incorporated into this figure, since the figure in particular is intended to show the position of the covers relative to the common inlet chamber 50.
  • inlets are drawn in with the valves 112 and their details therein. While only one inlet valve can be seen in FIG. 13, it can be seen from FIG. 21 that instead sea valves from an inlet 9 or from a plurality of inlets 9 can also be arranged and opened to the common inlet chamber 50, or can be closable to it.
  • the middle piston rod part 707 of FIG. 13 is separated into two individual piston rod extensions 507 and 607, a common connection 307 being formed between the extensions 507 and 607.
  • the arrangement of this connection makes it possible for the piston arrangement 4, 44 to work together with further units, for example with the pump (or motor) piston 24.
  • lifting webs 76, 77 with piston stroke guide surfaces 78, 79 can be arranged on the connection 307, which have the task of pushing the additional pistons 24, the axes of which are arranged at an angle to the axis of the piston rod 7, 207, into the cylinders 21 .
  • the pistons 24 can thus convey fluid currents from the cylinders 21 if the piston arrangement according to the invention is in the Cylinders 2, 62 reciprocated.
  • For power transmission can be arranged between the piston 24 and the lifting webs 76, 77, lever 75, rollers 72, shafts 73, pressure plates 71 and piston shoes 70 or other suitable means.
  • the pistons 24 are provided with piston rods 164 (with the piston shoes 70 on them) so that the cylinders 21 can have large diameters.
  • the pistons 24 can then generate and deliver compressed air by drawing air in through intake valves 84 and delivering it out of the cylinder via exhaust valves 84.
  • Channels 165 to the chamber around the piston rod 164 can serve to prevent compression in this chamber.
  • Said inlet and outlet valves can be designed as swiveling or rotating rollers and the pistons 24 can then be provided with recesses to prevent dead space in the remainder of the cylinder chamber, the same radius as the rollers of the valves.
  • FIG. 18 three units of FIG. 13 are assigned with their axes at angles of 60 degrees to a common crankcase 80 with a common crankshaft 54, 56, the pistons 44 being connected to the respective eccentric bearing 54 of the crankshaft by means of connecting rods. Since the double-piston units of FIG. 19 alternately generate power strokes in both axial directions, the connecting rods of FIG. 24 alternately produce compression and tension strokes. Consequently, only three units of FIG. 13 are arranged in FIG. 24, but they generate six power strokes per crankshaft revolution, like a conventional six-cylinder unit. This version is particularly interesting as an aircraft engine, because it offers high performance with low weight and, on the other hand, reduces the large amount of space required by six-piston radial engines to almost half.
  • inlet valves 101 and 102 facing the cylinder chambers 31 and -41 can be arranged in the cover (center piece) 40 of the inlet 9 and the chamber 50.
  • FIGS. 19 and 20 show further details of such additional valves in the middle piece 40. It thus follows from FIGS. 19 and 20 that several can be arranged instead of one valve set.
  • FIGS. 19 and 20 there are four such valve sets 101, 102 with shafts and spring holders 105 in spring tensioners 106 with spring bearings 108. The inlets to the valves are shown through the windows 104.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Curing Cements, Concrete, And Artificial Stone (AREA)
  • Compressor (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Actuator (AREA)

Abstract

1. A fluid flow facilitating device, an aggregate through which flows fluid, within a cylinder (2) reciprocable piston (4), a from the piston in axial direction extended shaft (7), a the cylinder on one of its axial ends closing and the shaft sealingly guiding cover (3), a by the cylinder (2), piston (4), shaft (7) and cover (3) boardered cylinder-chamber (1, 61), in the wall of the cylinder provided outlet passages (6) for leading fluid out of the cylinder-chamber with the outlet passages periodically openable and closeable during the movement of the piston by a corner of the piston and an in the cover provided inlet passage (9) for leading fluid into the cylinder-chamber with the inlet passage openable and closeable by reciprocating movement of the shaft, while the inlet- and outlet passages are so arranged that fluid flows in a one-way direction, which direction is parallel to the movement of the piston, from the inlet passage to the outlet passage and that the fluid during this one-directional flow is compressed and passed out from the cylinder-chamber or utilized to drive the piston (4), characterized therein, that the piston-shaft (7) is provided with a radially outwardly open, fully along the periphery of the shaft extended, circular control-recess (15, 45) which recess for the control of the inlet passage (9) cooperates with a a portion of the shaft surrounding and in the over (3) provided inlet-space (315), and, that the piston-shaft (7) is in the relative to the piston (4) opposed direction from the control recess (15, 315) provided with an extension (777), which is sealingly guideable in the cover (3).

Description

Die vorliegende Erfindung betrifft ein von Fluid durchstroemtes Aggregat, wie es im Oberbegriff von Anspruch 1 beschrieben ist.The present invention relates to an assembly through which fluid flows, as described in the preamble of claim 1.

Aus der US-PS-3 340 857, BROWN, ist ein derartiges Aggregat bekannt, das mehrere Einlass-Schlitze im Kolben, der Kolbenstange oder in Zylinderteilen verwendet. Dieses bekannte Aggregat ist zum einen mit einem doppelt wirkendem Kolben versehen und zum anderen verhindern die mehreren Schlitze die Durchstroemung mit einer grossen Fluidmenge fuer hohe Leistung pro gegebenen Abmessungen des Aggregates. Schliesslich kommt dieser Motor nicht ohne Kreuzkopf aus, weil seine Kolbenstange jenseits der Steuernut keinen dichtenden Fortsatz hat.Such an assembly is known from US Pat. No. 3,340,857, BROWN, which uses a plurality of inlet slots in the piston, the piston rod or in cylinder parts. This known unit is provided on the one hand with a double-acting piston and on the other hand the multiple slots prevent the flow with a large amount of fluid for high performance per given dimensions of the unit. After all, this engine cannot do without a crosshead because its piston rod has no sealing extension beyond the control groove.

Dieses Aggregat der bekannten Technik ist daher noch mit Maengeln behaftet, die noch ueberwunden werden muessen, wenn man sie zuverlaessiger gestalten oder ihre Leistung bei gegebenen baulichen Abmessungen erhoehen will.This unit of the known technology is therefore still defective, which must still be overcome if you want to make it more reliable or to increase its performance given the structural dimensions.

Der Erfindung liegt daher die Aufgabe zugrunde, die Nachteile der bekannten Technik einzuschraenken und ein zuverlaessiges Aggregat mit besonders hoher Leistung bei baulicher Einfachheit und geringem Gewicht zu schaffen.The invention is therefore based on the object to limit the disadvantages of the known technology and to create a reliable unit with particularly high performance with structural simplicity and low weight.

Diese Aufgabe wird im Gebiet des Gattungsbegriffs des Patentanspruchs 1 nach dem kennzeichnendem Teil des Patentanspruchs 1 geloest. Weitere vorteilhafte Ausfuehrungen der Erfindung sind in den Unteranspruechen 2 bis 8 beschrieben.

  • Figuren 1 bis 14 zeigen Laengsschnitte durch Ausfuehrungsbeispiele der Erfindung.
  • Figur 15 ist ein Querschnitt durch Figur 14.
  • Figuren 16 bis 19 zeigen Laengsschnitte durch Aggregate der Erfindung.
  • Figur 20 ist ein Querschnitt durch Figur 19.
This object is achieved in the area of the generic term of patent claim 1 according to the characterizing part of patent claim 1. Further advantageous embodiments of the invention are described in subclaims 2 to 8.
  • Figures 1 to 14 show longitudinal sections through exemplary embodiments of the invention.
  • Figure 15 is a cross section through Figure 14.
  • FIGS. 16 to 19 show longitudinal sections through units of the invention.
  • Figure 20 is a cross section through Figure 19.

Figur 1 zeigt das einfachste Ausfuehrungsbeispiel der Erfindung im Laengsschnitt. Man sieht den Kolben 4 mit seiner in achsialer Richtung erstreckten Kolbenstange 7, die nahe ihrem jenseitigem Ende mit der rund um den ganzen Umfang erstreckten und radial nach aussen offenen Steuernut 15, die am jenseitigem Ende durch den Kolbenstangen - Fortsatz 777 beendet ist. Diese Anordnung reziprokiert (laeuft hin- und her-) im Zylinder und dessen Deckel 3, wobei derZylinder am einem Ende mit den AuslassSchlitzen 6 und am anderem Ende mit dem Deckel 3 versehen ist, waehrend der Deckel 3 einen Einlass Anschluss 9 und einen Einlassraum 315, sowie einen rueckwaertigen Verschlussteil 333 hat, der den Kolbenstangen Fortsatz 777 oder einen Teil der Kolbenstange 7 dichtend umgreifen kann. Bei einer der achsialen Endlagen der Bewegung der Kolbenanordnung, oder nahe dieser achsialen Endlage, stroemt Fluid vom Anschluss 9 durch den Einlassraum 315 und durch die Steuernut 15 in den Innenraum 1 des Zylinders 2 ein, waehrend ein anderer Fluidteil durch die Auslaesse 6 aus dem Zylinder ausstroemt.Figure 1 shows the simplest exemplary embodiment of the invention in longitudinal section. One sees the piston 4 with its piston rod 7, which extends in the axial direction and which, near its end on the other side, has the control groove 15 which extends around the entire circumference and is open radially outwards and which is ended at the other end by the piston rod extension 777. This arrangement reciprocates in the cylinder and its cover 3, the cylinder being provided with the outlet slots 6 at one end and the cover 3 at the other end, while the cover 3 has an inlet port 9 and an inlet space 315 , as well as a backward closing part 333, which can grip around the piston rod extension 777 or part of the piston rod 7 in a sealing manner. At one of the axial end positions of the movement of the piston arrangement, or near this axial end position, fluid flows from the connection 9 through the inlet space 315 and through the control groove 15 into the interior 1 of the cylinder 2, while another fluid part flows through the outlets 6 from the cylinder streams out.

Damit ist die wesentliche konstruktive Ausfuehrung der Erfindung beschrieben. Es ergibt sich daraus, dass der Zylinder eine bestimmte achsiale Laenge und die Kolbenstange eine bestimmte achsiale Laenge haben muessen, um die Stroemungsbedingung erfuellen zu koennen. Ebenso muessen die Steuernut, der Fortsatz und der Endverschlussteil 333 des Deckels 3 geometrische Abmessungen und Lagen zu benachbarten Teilen erfuellen, um die beschriebene Wirkungsweise der Erfindung zu erreichen. Sind diese Bedingungen erfuellt, dann ist auch die Aufgabe der Erfindung erfuellt.This describes the essential constructive embodiment of the invention. It follows from this that the cylinder must have a certain axial length and the piston rod must have a certain axial length in order to be able to meet the flow condition. Likewise, the control groove, the extension and the end closure part 333 of the cover 3 must meet geometrical dimensions and positions in relation to neighboring parts in order to achieve the described mode of operation of the invention. If these conditions are met, then the object of the invention is also met.

In den Folgefiguren wird die Erfindung noch weiter fuer spezielle vorteilhafte Ausfuehrungen ausgebildet, wobei in den betreffenden Figurenbeschreibungen die entsprechenden Teile mit gleichen Bezugsziffern benannt, die Bezugsziffern fuer die Kennzeichnung der besonderen Ausfuehrungsarten jedoch mit weiteren zusaetzlichen Ziffern versehen sind, die einstelligen Ziffern also durch mehrstellige Ziffern ergaenzt sind, usw.In the subsequent figures, the invention is further developed for special advantageous designs, the corresponding parts in the relevant figure descriptions being given the same reference numerals, but the reference numbers for identifying the special types of design are provided with additional digits, that is to say the single-digit digits are represented by multi-digit digits are added, etc.

In Figur 2 ist die Erfindung zu einem Doppelkolben erweitert, um doppelte Leistung bei gleicher Kurbelwelle erreichen zu koennen. Der Kolben 4 hat daher an seinem rueckwaertigem Ende eine mittlere Verbindung 60, die an ihrem jenseitigem Ende den zweiten Kolben 64traegt oder bildet, von dem aus in - relativ zum erstem Kolben 4 der Erfindung - in achsial entgegengesetzter Richtung die zweite Kolbenstange 67 erstreckt ist waehrend der erste Zylinder 2 einen entsprechenden achsialen Fortsatz 62 hat.In Figure 2, the invention has been expanded to a double piston in order to be able to achieve twice the power with the same crankshaft. The piston 4 therefore has at its rearward end a central connection 60 which supports or forms the second piston 64 at its other end, from which the second piston rod 67 extends in the axially opposite direction relative to the first piston 4 of the invention the first cylinder 2 has a corresponding axial extension 62.

Die zweiten Teile haben dabei wieder die Anordnungen der Erfindung, naemlich die Steuernut 45, den Deckel 3, den Verschlussteil 2333, den Fortsatz 2777 undsoweiter.The second parts again have the arrangements of the invention, namely the control groove 45, the cover 3, the closure part 2333, the extension 2777 and so on.

In Figur 3 sieht man, wie die Auslass-Schlitze 6, 66 um den Umfang des Zylinders verteilt sind, oder wie sie in bestimmte Sammelkaenaele 17,19 als Auslaesse 18, 20 muenden koennen.FIG. 3 shows how the outlet slots 6, 66 are distributed around the circumference of the cylinder, or how they can end in certain collecting channels 17, 19 as outlets 18, 20.

In Figur 4 sind die Anordnungen der Erfindung etwa wie in Figur 2 vorhanden, doch ist die mittlere Verbindung zwischen dem erstem und dem zeiten Kolben nicht durch die Verbindung 60 bewirkt, sondern durch Verbindung der einzelnen der beiden Kolben 4, 64 mittels Pleuelbolzen und Pleuel 46, 55 zum exzentrischem Lager 54 einer Kurbelwelle 56, 52, 54.The arrangements of the invention are present in FIG. 4 approximately as in FIG. 2, but the middle connection between the first and the second piston is not effected by the connection 60, but by connection of the individual of the two pistons 4, 64 by means of connecting rod bolts and connecting rods 46 , 55 to the eccentric bearing 54 of a crankshaft 56, 52, 54.

In Figur 5 ist die mittlere Verbindung 60 hohl ausgebildet, formt also ein Rohr und kann die Oeffnungen 160 zur Durchstroemung mit Fluid erhalten. Das kann auch der Kuehlung der Kolbenteile dienen.In FIG. 5, the middle connection 60 is hollow, that is, it forms a tube and can receive the openings 160 for the through-flow of fluid. This can also be used to cool the piston parts.

In Figur 6 sind in der hohlen Rohrverbindung 60 den Raum 560 verschliessende Innendeckel 760 angeordnet, um eine Fluidstroemung um die mittlere Verbindung herum durch die Fenster 160, 660 zu ermoeglichen. Ferner sind in dieser Figur die Auslass-Schlitze als Schlitze 666 ausgebildet, die zu Sitzen fuehren, die durch die Rueckschlagventile 306 (ggf. belastet mit Federn 406) gegen den Sammelraum 319 im Gehaeuse 316 verschliessen. Wenn das Fluid aus dem Zylinder ausgestroemt ist, damit aus dem Sammelraum 319 dann kein Fluid mehr in den Zylinder-Innenraum 1 oder 61 zurueck stroemen kann.In FIG. 6, inner covers 760 closing the space 560 are arranged in the hollow pipe connection 60 in order to allow fluid flow around the central connection through the windows 160, 660. Furthermore, in this figure, the outlet slots are designed as slots 666, which lead to seats which close against the collecting space 319 in the housing 316 by the check valves 306 (possibly loaded with springs 406). When the fluid has flowed out of the cylinder, so that no more fluid can flow back into the cylinder interior 1 or 61 from the collecting space 319.

In Figur 7 ist die Verbindung durch Rohrteile groesseren Durchmessers erstzt und mit Halterungen 411 versehen, die die ineinander geschachtelten Rohrteile 404, 464 miteinander verbinden. Durch diese Ausbildung wird Zwischenraum zwischen dem Zylinder und der Verbindung zwischen den Kolben vermieden, sodass aus diesem Grunde kein (oder nur wenig) Fluid aus dem Auslass Sammelraum 19 in das innere der Zylinder zurueckstroemen kann. Ferner hat diese Figur einen Turbolader 440, dessen Turbine ueber Kanal 441 mittels der Ausstroemungen aus den Auslaessen 6, 66 betrieben wird, waehrend dessen ader ueber die Leitungen 442, 443 zu den Einlaessen 9, 999 des ersten und des zweiten Zylinder-Raumes 1, 61 vorkomprimiertes Fluid, zum Beispiel Luft oder Brennstoff Luftgemisch, liefert.In FIG. 7, the connection is replaced by pipe parts of larger diameter and provided with brackets 411 which connect the pipe parts 404, 464 nested one inside the other. This design avoids a gap between the cylinder and the connection between the pistons, so that for this reason no (or only a little) fluid can flow back from the outlet collecting space 19 into the interior of the cylinder. Furthermore, this figure has a turbocharger 440, the turbine of which is operated via channel 441 by means of the outflows from outlets 6, 66, while the other of which is via lines 442, 443 to inlets 9, 999 of the first and second cylinder chambers 1, 61 delivers pre-compressed fluid, for example air or fuel-air mixture.

Figur 8 illustriert die kurzen Zylinderteile 362 zur Kolbenabdichtung in einer der achsialen Endlagen der Bewegung und im uebrigen zeigt diese Figur noch einmal deutlich die erfindungsgemaessen Teile zum erstem und zweitem Kolben.FIG. 8 illustrates the short cylinder parts 362 for sealing the piston in one of the axial end positions of the movement, and for the rest this figure clearly shows the parts according to the invention for the first and second pistons.

Figuren 9 und 10 zeigen verschiedene Lagen der Doppelkolben.Figures 9 and 10 show different positions of the double pistons.

Figur 11 zeigt ein Aggregat fuer die Erzielung hoher Wirkungsgrade bei unterschiedlichen Belastungen usw., wobei die erfindungsgemaessen Ausbildungen in der Figur erscheinen, das ansosnten wesentliche und neue dieser Figur aber auch auf Aggregate ohne die Merkmale der Erfindung angeordnet werden kann. Die ersten und zweiten Zylinder 2 und 62 sind in dieser Figur in achsialer Richtung verschiebbar in einem Aussengehaeuse 161 gelagert. Die Zylinder koennen dadurch naeher zur zentrischen Achse der Kurbelwelle 56 oder weiter von ihr fort verschoeben werden. Diese Verschiebung kann auch beim Betrieb des Aggregates dieser Figur erfolgen. Auf diese Weise kann man zum 8eispiel den Brennraum eines Verbrennungsmotors oder das Kompressionsverhaeltnis eines Motors, bzw. Kompressors oder Entspanners, willkuerlich vergroessern und verkleinern. Dadurch lassen sich die Wirkungsgrade veraendern und Verluste der Aggregate mit festen, nicht verschiebbaren Zylindern vermeiden oder einschraenken.FIG. 11 shows an aggregate for achieving high efficiencies at different loads, etc., the designs according to the invention appearing in the figure, but the otherwise essential and new of this figure can also be arranged on aggregates without the features of the invention. In this figure, the first and second cylinders 2 and 62 are mounted in an outer housing 161 so as to be displaceable in the axial direction. The cylinders can thereby be moved closer to the central axis of the crankshaft 56 or further away from it. This shift can also take place during operation of the unit in this figure. In this way, one can arbitrarily enlarge and reduce the combustion chamber of an internal combustion engine or the compression ratio of an engine, or compressor or expansion device. This allows the efficiency to be changed and losses of the units with fixed, non-displaceable cylinders to be avoided or restricted.

Figur 12 zeigt die achsialen Endteile des Aggregates der Erfindung und daran verwendbare Abdichtungen, wie Dichtringe 11 in Dichtringkammern 10, Druckleitungen zu den Kammern 10 zur Andrueckung der Dichtringe mit ihren Dichtflaechen 97 und abzudichtende Flaechen benachbarter Teile, sowie bauliche Einzelheiten ohne Bezugszeichen da sie nur fuer die Produktion von Bedeutung sind.Figure 12 shows the axial end parts of the assembly of the invention and seals that can be used thereon, such as sealing rings 11 in sealing ring chambers 10, pressure lines to the chambers 10 for pressing the sealing rings with their sealing surfaces 97 and sealing surfaces of adjacent parts, as well as structural details without reference numerals since they are only for the production matter.

Mit Figur 13 beginnt die Illustration einer weiteren Ausgestaltung der Erfindung. Hierin sind die Doppelkolben nicht durch eine mittlere Verbindung miteinander verbunden, sondern die Kolbenstangen 7 und 207 sind mittels einer Verbindung 707 miteinander verbunden Die Verbindung 707 bildet dabei die Fortsaetze 777 der frueher beschriebenen Figuren und ersetzt diese. Entsprechend hat man zwischen den Kolbenstangen 7 und 207, wie die Erfindung und der Anspruch 1 es ja vorschreiben, jeweils eine Steuernut 15 bzw. 215. Der Deckel ist hier zwischen den beiden Kolben 4 und 44 angeordnet und muss nach dem Anspruch 1 der Erfindung die Kol benstangen und deren Fortsaetze, also zeitweilig Teile der Kolbenstangen 7, 207 und der Fortsaetze, also des Teiles 707, umgreifen und abdichten. Der Deckel 3, 40 hat daher die diese Teile dichtenden Deckelteile 3003 und 4003, zwischen denen der gemeinsame Einlassraum 50 ausgebildet und zum Einlass Anschluss 9 verbunden ist. Damit kein Fluid aus den Zylindern in den Einlass 9 zurueckstroemen kann, befindet sich zwischen dem Einlass 9 und der Einlasskammer 50 ein Rueckschlagventil 112. Der gemeinsame Raum 50 ersetzt die Einzelraeume 315 der frueher beschriebenen Figuren.The illustration of a further embodiment of the invention begins with FIG. Herein the double pistons are not connected to each other by a middle connection, but the piston rods 7 and 207 are connected to each other by a connection 707. The connection 707 forms the extensions 777 of the figures described earlier and replaces them. Accordingly, one has between the piston rods 7 and 207, as prescribed by the invention and claim 1, a control groove 15 and 215, respectively. The cover is arranged here between the two pistons 4 and 44 and must, according to claim 1 of the invention Kol benstangen and their extensions, ie temporarily parts of the piston rods 7, 207 and the extensions, ie the part 707, embrace and seal. The cover 3, 40 therefore has the cover parts 3003 and 4003 sealing these parts, between which the common inlet space 50 is formed and connection 9 is connected to the inlet. In order that no fluid can flow back from the cylinders into the inlet 9, there is a check valve 112 between the inlet 9 and the inlet chamber 50. The common space 50 replaces the individual spaces 315 of the figures described earlier.

Bei der Reziprokation der Kolbenanordnung verbindet die Steuernut 15 zeitweilig den Einlass 9 mit der Zylinderkammer 1, waehrend die Steuernut 215 zu einer anderen Zeit zeitweilig den Einlass 9 mit der Zylinderkammer 61 verbindet. Die Auslass-Schlitze 6 sind in dieser Figur wieder am dem Deckel entgegengesetzt gelegenem achsialem Endteil des betreffenden Zylinders angeordnet, sodass man die Auslaesse 6 nahe den rechten und linken Enden der Figur sieht, waehrend sie in den frueher beschrieben Doppelkolben Aggregaten etwa in der Mitte der betreffenden Figuren zu finden waren.When the piston arrangement is reciprocated, the control groove 15 temporarily connects the inlet 9 to the cylinder chamber 1, while the control groove 215 temporarily connects the inlet 9 to the cylinder chamber 61 at another time. In this figure, the outlet slots 6 are again arranged on the axial end part of the cylinder in question lying opposite the cover, so that the outlets 6 can be seen near the right and left ends of the figure, while in the previously described double-piston units they are located approximately in the middle of the relevant figures were found.

Figur 14 zeigt einen Laengsschnitt durch den Mitteleinsatz 40, der die beiden Deckel 3003 und 4003 jenseits der gemeinsamen Einlasskammer 50 bildet. Die Einlaesse 9 sind in diese Figur noch nicht eingearbeitet, da die Figur besonders die lage der Deckel relativ zur gemeinsamen Einlass- kammer 50 zeigen soll.FIG. 14 shows a longitudinal section through the center insert 40, which forms the two covers 3003 and 4003 beyond the common inlet chamber 50. The inlets 9 have not yet been incorporated into this figure, since the figure in particular is intended to show the position of the covers relative to the common inlet chamber 50.

In Figur 15 sind in radialer Richtung mit Achsen in der Lage der gepfeilten Ebene der Figur 14, die Einlaesse eingezeichnet mit den Ventilen 112 und deren Einzelheiten darin. Waehrend man in Figur 13 nur ein Einlassventil sieht, ist aus Figur 21 erkennbar, dass stattdessen auch meere Ventile aus einem Einlass 9 oder aus mehreren Einlaessen 9 angeordnet und zur gemeinsamen Einlass- kammer 50 offnungsfaehig, oder zu ihr verschliessbar sein koennen.In FIG. 15, in the radial direction with axes in the position of the arrowed plane of FIG. 14, the inlets are drawn in with the valves 112 and their details therein. While only one inlet valve can be seen in FIG. 13, it can be seen from FIG. 21 that instead sea valves from an inlet 9 or from a plurality of inlets 9 can also be arranged and opened to the common inlet chamber 50, or can be closable to it.

In der Figur 16 ist der mittlere Kolbenstangenteil 707 der Figur 13 in zwei einzelne, individuelle Kolbenstangenfortsaetze 507 und 607 getrennt, wobei zwischen den Fortsaetzen 507 und 607 eine gemeinsame Verbindung 307 ausgebildet ist. Durch die Anordnung dieser Verbindung wird es moeglich, die Kolbenanordnung 4, 44 mit weiteren Aggregaten, zum Beispiel mit den Pump-(oder Motor) Kolben 24 zusammen arbeiten zu lassen. Zum Beispiel koennen an der Verbindung 307 Hubstege 76, 77 mit Kolbenhub Fuehrungsflaechen 78, 79 angeordnet sein, die die Aufgabe haben, die weiteren Kolben 24, deren Achsen unter einem Winkel zur Achse der Kolbenstange 7, 207 angeordnet sind, in die Zylinder 21 hereinzudruecken. Die Kolben 24 koennen so Fluidstroeme aus den Zylindern 21 foerdern, wenn die erfindungsgemaesse Kolbenanordnung in den Zylindern 2, 62 reziprokiert. Zur Kraftuebertragung koennen zwischen den Kolben 24 und den Hubstegen 76, 77, Hebel 75, Rollen 72, Wellen 73, Druckplatten 71 und Kolbenschuhe 70 bzw. andere geeignete Mittel angeordnet sein.In FIG. 16, the middle piston rod part 707 of FIG. 13 is separated into two individual piston rod extensions 507 and 607, a common connection 307 being formed between the extensions 507 and 607. The arrangement of this connection makes it possible for the piston arrangement 4, 44 to work together with further units, for example with the pump (or motor) piston 24. For example, lifting webs 76, 77 with piston stroke guide surfaces 78, 79 can be arranged on the connection 307, which have the task of pushing the additional pistons 24, the axes of which are arranged at an angle to the axis of the piston rod 7, 207, into the cylinders 21 . The pistons 24 can thus convey fluid currents from the cylinders 21 if the piston arrangement according to the invention is in the Cylinders 2, 62 reciprocated. For power transmission can be arranged between the piston 24 and the lifting webs 76, 77, lever 75, rollers 72, shafts 73, pressure plates 71 and piston shoes 70 or other suitable means.

In Figur 17 sind die Kolben 24 mit Kolbenstangen 164 (mit den Kolbenschuhen 70 an ihnen) versehen, damit die Zylinder 21 grosse Durchmesser erhalten koennen. Die Kolben 24 koennen dann Pressluft erzeugen und liefern, indem sie Luft ueber Einlass Ventile 84 ansaugen und ueber Auslassventile 84 aus dem Zylinder heraus liefern. Kanaele 165 zur Kammer um die Kolbenstange 164 herum koennen dazu dienen, Kompression in dieser Kammer zu verhindern. Die genannten Einlass- und Auslass Ventile koennen als Schwenk- oder Rotier- Walzen ausgebildet sein und die Kolben 24 koennen dann zwecks Verhinderung von totem Raum im Zylinderkammernrest mit Ausnehmungen versehen sein, die gleichen Radius, wie die Walzen der Ventile haben.In FIG. 17, the pistons 24 are provided with piston rods 164 (with the piston shoes 70 on them) so that the cylinders 21 can have large diameters. The pistons 24 can then generate and deliver compressed air by drawing air in through intake valves 84 and delivering it out of the cylinder via exhaust valves 84. Channels 165 to the chamber around the piston rod 164 can serve to prevent compression in this chamber. Said inlet and outlet valves can be designed as swiveling or rotating rollers and the pistons 24 can then be provided with recesses to prevent dead space in the remainder of the cylinder chamber, the same radius as the rollers of the valves.

In Figur 18 sind drei Aggregate der Figur 13 mit ihren Achsen unter Winkeln von 60 Grad einem gemeinsamem Kurbelgehaeuse 80 mit einer gemeinsamen Kurbelwelle 54, 56 zugeordnet, wobei die Kolben 44 jeweils mittels Pleueln zu dem betreffendem Exzenterlager 54 der Kurbelwelle verbunden sind. Da die Doppelkolben Aggregate der Figur 19 in beiden achsialen Richtungen abwechselnd Krafthuebe erzeugen, entstehen an den Pleueln der Figur 24 abwechselnd Druck- und Zug- Huebe. Folglich sind in Figur 24 nur drei Aggregate der Figur 13 angeordnet, aber sie erzeugen pro Kurbelwellen Umdrehung sechs Krafthuebe, wie ein uebliches Sechszylinder Aggregat. Diese Ausfuehrung ist besonders interressant als Flugmotor, weil e einmal hohe Leistung bei geringem Gewicht bietet und zum anderem den hoehenmaessig grossen Raumbedarf von Sechskolben- Sternmotoren auf fast die H elfte verkleinert.In FIG. 18, three units of FIG. 13 are assigned with their axes at angles of 60 degrees to a common crankcase 80 with a common crankshaft 54, 56, the pistons 44 being connected to the respective eccentric bearing 54 of the crankshaft by means of connecting rods. Since the double-piston units of FIG. 19 alternately generate power strokes in both axial directions, the connecting rods of FIG. 24 alternately produce compression and tension strokes. Consequently, only three units of FIG. 13 are arranged in FIG. 24, but they generate six power strokes per crankshaft revolution, like a conventional six-cylinder unit. This version is particularly interesting as an aircraft engine, because it offers high performance with low weight and, on the other hand, reduces the large amount of space required by six-piston radial engines to almost half.

In Figur 18 ist noch eingezeichnet, dass dem Einlass 9 und der Kammer 50 noch zu den Zylinder-Kammern 31 und -41 gerichtete Einlassventile 101, 102 im Deckel (Mittelstueck) 40 angeordnet sein koennen.It is also shown in FIG. 18 that the inlet valves 101 and 102 facing the cylinder chambers 31 and -41 can be arranged in the cover (center piece) 40 of the inlet 9 and the chamber 50.

Figuren 19 und 20 zeigen weitere Einzelheiten solcher zusaetzlichen Ventile im Mittelstueck 40. So ergiebt sich aus den Figuren 19 und 20, dass statt einem Ventilsatz mehrere angeordnet sein koennen. In den Figuren 19 und 20 sind es vier solcher Ventilsaetze 101, 102 mit Schaeften und Federhaltern 105 in Federnspannern 106 mit Federlagern 108. Die Einlaesse zu den Ventilen sind durch die Fenster 104 gezeigt.FIGS. 19 and 20 show further details of such additional valves in the middle piece 40. It thus follows from FIGS. 19 and 20 that several can be arranged instead of one valve set. In FIGS. 19 and 20 there are four such valve sets 101, 102 with shafts and spring holders 105 in spring tensioners 106 with spring bearings 108. The inlets to the valves are shown through the windows 104.

Claims (8)

1. A fluid flow facilitating device, an aggregate through which flows fluid, within a cylinder (2) reiprocable piston (4), a from the piston in axial direction extended shaft (7), a the cylinder on one of its axial ends closing and the shaft sealingly guiding cover (3), a by the cylinder (2), piston (4), shaft (7) and cover (3) boardered cylinder-chamber (1, 61), in the wall of the cylinder provided outlet passages (6) for leading fluid out of the cylinder-chamber with the outlet passages periodically openable and closeable during the movement of the piston by a corner of the piston and an in the cover provided inlet passage (9) for leading fluid into the cylinder-chamber with the inlet passage openable and closeable by reciprocating movement of the shaft, while the inlet- and outlet passages are so arranged that fluid flows in a one-way direction, which direction is parallel to the movement of the piston, from the inlet passage to the outlet passage and that the fluid during this one-directional flow is compressed and passed out from the cylinder-chamber or utilized to drive the piston (4), characterized therein,
that the piston-shaft (7) is provided with a radially outwardly open, fully along the periphery of tne shaft extended, circular contol-recess (15, 45) which recess for the control of the inlet passage (9) cooperates with a a portion of the shaft surrounding and in the over (3) provided inlet-space (315), and, that the piston-shaft (7) is in the relative to the piston (4) opposed direction from the control recess (15, 315) provided with an extension (777), which is sealingly guideable in the cover (3).
2. The device of claim 1, characterized therein, that the piston (4) constitutes a first piston (4), that shaft (7) constitutes a first shaft (7), the recess (15) constitutes a first recess (15), the extension (777) constitutes a first extension (777), that the first piston (4) is in the relative to the first recess opposed direction connected by a medial portion (46, 55, 60, 404, 411, 464) to a second piston (64) and that the second piston (64) is symmetrically to the middle between both pistons (4 and 64) and symmetrically to the first piston, shaft, recess and extension provided with a second shaft (67), the second shaft provided with a second control recess (415) and a second extension (2777), which co-operate with a provided second inlet arrangement (209, 2315), a second cylinder (62) and with a second outlet passage (66).
3. The device of claim 1 characterized therein, that the extension (777) is endwards of a cover (40) formed as an extension-connection-member (707) which in the to the first control recess (15) opposed direction forms a second control recess (215) between the mentioned connection-member and a second piston-shaft (207) of a to the second-shaft connected piston (44),
the cover (40) forms endwards of the sealable portion of the cover - portion (3003) a second cover portion (4003) for the sealing of the piston shaft (7) and of the connection member (707) with the second cover pnrtion (4003) surrounding portions of the second shaft (207), of the second recess (215) and of the second extension (707), and that a common inlet chamber (50) is provided in the common cover (40) between the cover- portions (3003) and (4003).
4. The device of claim 3, characterized therein, that at least one inlet passage (9) is provided before the inlet chamber (50) and that a one-way inlet valve (112) is provide between the inlet passage (9) and the inlet-chamber (50).
5. The device of claim 1, characterized therein, that one-way inlet valves (101, 102, 112) are provided in the cover portions (3003 and 4003) and between the inlets (9, 50) and the neighboring cylinder-chambers (6, 61).
6. The device of claims 2 or 3, characterized therein, that the piston assembly, which includes at least one piston and one piston shaft, is connected by a connecting rod (46-48) to an relative to the medial axis of the crankshaft eccentrically provided connecting rod bearings (43) of a crankshaft (56) and that three of the piston assemblies are provided to a common housing (80) with the axes of the piston assemblies angularly spaced by sixty degrees, relatively to each other.
7. The device of claim 3, characterized therein, that the connection member (707) is provided with two extensions which form axial end portions (507 and 607) on both ends of a medial rod- portion (307) with the rod portion located between the mentioned extensions, and that the mentioned medial rod portion is provided lift- guides (76, 77) which form guide faces (78,79) for the driving of additional pistons (24), while the additional pistons (24) are with their axes inclined relative to the axis of the medial rod portion.
8. The device of claim 1, characterized therein, that the piston assembly, which includes at least one piston and at least one piston-shaft, is connected by a piston rod (46, 55) to an eccentric piston and bearing (54) of a crankshaft (56) and that the cylinder (2, 62) is adjustably provided in a guide (161 in such an arrangement, that the distance between the outer dead point location of the respective piston (4, 64) and the cover (3) is variable and that thereby the compression ratio of the device is variable.
EP85106624A 1983-11-18 1985-05-29 Aggregate with through flow by a fluid Expired - Lifetime EP0204011B1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE19833341718 DE3341718A1 (en) 1983-11-18 1983-11-18 Units through which fluid flows with pistons moving backwards and forwards in cylinders, such as pumps, motors, combustion engines or internal combustion engines
AT85106624T ATE57741T1 (en) 1985-05-29 1985-05-29 AGGREGATE WITH FLUID FLOWING THROUGH.
DE8585106624T DE3580271D1 (en) 1985-05-29 1985-05-29 FLOWED AGGREGATE.
EP85106624A EP0204011B1 (en) 1985-05-29 1985-05-29 Aggregate with through flow by a fluid

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP85106624A EP0204011B1 (en) 1985-05-29 1985-05-29 Aggregate with through flow by a fluid

Publications (2)

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EP0204011A1 EP0204011A1 (en) 1986-12-10
EP0204011B1 true EP0204011B1 (en) 1990-10-24

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AT (1) ATE57741T1 (en)
DE (1) DE3580271D1 (en)

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DE102008058558B4 (en) * 2008-11-20 2020-04-23 Volkswagen Ag Heat engine
CN107369479B (en) * 2017-07-31 2023-08-22 清华大学天津高端装备研究院 Differential pressure-based passive shutdown system for an integrated stack and a nuclear reactor
CN114628833B (en) * 2021-12-13 2023-11-10 杭叉集团股份有限公司 Portable new forms of energy fork truck battery module
CN114738107B (en) * 2022-04-13 2023-03-31 西华大学 Pneumatic supercharging system and method for multi-cylinder engine
CN116201537B (en) * 2023-03-09 2024-05-10 夸克能源工程实验室(深圳)有限公司 Petroleum recovery experimental system

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Publication number Priority date Publication date Assignee Title
GB191121990A (en) * 1911-10-05 1912-10-07 Albert Rigaud A Double-acting Internal Combustion Engine.
FR452070A (en) * 1912-11-04 1913-05-06 William Richard Flitcroft Patc Gas engines
DE677073C (en) * 1935-08-20 1939-06-17 Georges Raymond Langrognet Internal combustion engine with double-acting pistons
US3340857A (en) * 1965-10-19 1967-09-12 Arthur E Brown Two stroke cycle internal combustion engine

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DE3580271D1 (en) 1990-11-29
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