EP0028224B1 - Tandemmaschine mit entgegengesetzten freien kolben - Google Patents

Tandemmaschine mit entgegengesetzten freien kolben Download PDF

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Publication number
EP0028224B1
EP0028224B1 EP80900774A EP80900774A EP0028224B1 EP 0028224 B1 EP0028224 B1 EP 0028224B1 EP 80900774 A EP80900774 A EP 80900774A EP 80900774 A EP80900774 A EP 80900774A EP 0028224 B1 EP0028224 B1 EP 0028224B1
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EP
European Patent Office
Prior art keywords
cross
compressor
pistons
cylinders
fixed
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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
Application number
EP80900774A
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English (en)
French (fr)
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EP0028224A1 (de
Inventor
Henry Benaroya
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B71/00—Free-piston engines; Engines without rotary main shaft
    • F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
    • F02B71/06—Free-piston combustion gas generators per se

Definitions

  • the invention relates to tandem machines with opposite free pistons comprising at least two groups of piston-cylinder engines arranged parallel one beside the other and at least two compressor elements, each of these groups piston-cylinder engine comprising two cylinders aligned in each of which work two opposite engine pistons, the two external engine pistons of each group being connected to compression pistons by means of external crosspieces fixed to each other by at least one connecting element, so that an external moving element is thus formed, while the two internal driving pistons of each group are connected to each other and to other compressor pistons by an internal cross member to thereby form an internal moving element.
  • the external mobile assembly is subjected to longitudinal vibrations created by the harmonics of the periodic forces as well as to bending vibrations created by asymmetries of operation in the piston-cylinder engine groups, these asymmetries being due mainly to differences in the rate of combustion, the advance of combustion, the condition of the injectors, etc.
  • One of the parameters most unfavorably influencing the amplitude of these vibrations is the length of the lever arms by which the rods of the compressor pistons are connected to the above-mentioned external transverse pieces (cross-pieces).
  • the invention aims in particular to obtain a shortening of these lever arms and, consequently, a reduction in the amplitude of the above-mentioned vibrations.
  • the compressor pistons forming part of the external moving element are arranged outside the transverse parts of this element, while the driving pistons and the connecting element or elements forming part of this same moving element are located inner side of said sleepers.
  • each of the crossmembers of the external mobile assembly is mounted, so as to be able to slide thereon, on a rod or a tube which extends between two fixed supports and which are located on either side of said piece , it is advantageous to fix the cylinders of the compressor pistons forming part of this movable assembly on the external support of said rod or of said tube.
  • the external mobile assembly comprising two external crosspieces connected by at least one tie rod, each carrying four external pistons displaceable in four of said engine cylinders and two compressor pistons sliding in external compressor cylinders.
  • One of the problems which then arises is constituted by the difference in intrinsic mass between the internal and external mobile equipment, which it is necessary to compensate for by adding masses which cause significant efforts on the synchronization means; another problem is constituted by the dimensions and the mass reached by the sleepers, which must transmit significant and alternating forces between compressor pistons and engine pistons.
  • the invention also aims in this case to reduce the mass of each of the crews, by acting in particular on that of the sleepers which constitutes an important element thereof, and to balance these masses as intrinsically as possible.
  • the axes of the internal compressor cylinders pass through the extension of the small median of said rectangle while the axes of the external compressors, arranged outside said rectangle, pass through the extension of the large median of the latter.
  • the machine illustrated in fig. 1 includes two groups of engine piston-cylinders A and B but it could include a larger number of groups of engine piston-cylinders. Each of these groups has two aligned engine cylinders 1 and 2. In each of these cylinders work two opposite engine pistons 3, 4 and 5, 6. Each of these cylinders is surrounded by sweeping and exhaust breeches communicating with the delimited compartment by the pistons by means which are not shown, very schematically; than on one of the cylinders 1.
  • the machine further comprises eight compressor cylinders 7, 8, 9, 10, 11, 12, 13, 14 in which the compressor pistons 15, 16, 17, 18, 19, 20, 21, 22 work.
  • the compressor cylinders are arranged in such a way that the compressor pistons operate with double effect.
  • the suction and discharge valves which are located on both sides of the compressor cylinders are not shown in fig. 1, their arrangement being conventional.
  • the movable members can be viewed as distributed between an exterior crew and an interior crew.
  • the exterior engine pistons 3 and 6 of the two groups of engine piston-cylinders A and B as well as the compressor pistons 15, 16, 17, 18 of the exterior compressor cylinders 7, 8, 9, 10 are part of the exterior mobile equipment in the axial direction.
  • the rods of these engine and compressor pistons are fixed on external crosspieces 23, 24, connected by two rods or tie rods 25, 26.
  • the transverse parts 23, 24 are mounted, so as to be able to slide thereon on rods or tubes 27, 28 which are fixed on either side of these transverse parts on fixed supports 29, 30 and 31, 32 which are part of the frame of the machine.
  • each of the parts 23 and 24 is fixed to a corresponding section of rod or tube which slides in two bearings fixed to the frame of the machine, each placed on one side of the part.
  • the compressor elements of the external moving element are arranged on the external side of the parts 23, 24, while the external engine pistons 3 and 6 of this same moving element and the connecting rods 25 and 26 are located between the crosspieces 23, 24, that is to say on the inner side of these parts.
  • a lower radial development obviously corresponds to a lower mass and to a less sensitivity to vibrations.
  • a reduction in mass is also very advantageous since it makes it possible to increase the number of beats per unit of time and therefore the power of the machine (product of the energy supplied per cycle by the number of cycles per unit of time) .
  • the compressor cylinders 7, 8 and 9, 10 in which the compressor pistons 15, 16, 17, 18 forming part of the external moving assembly work are fixed respectively to the parts 29 and 31 of the frame of the machine on which are also fixed the outer ends of the rods or tubes 27, 28.
  • the interior crew includes the interior engine pistons 4 and 5 of the two engine piston-cylinder groups A and B as well as the compressor pistons 19, 20, 21, 22.
  • the rods of all these engine and compressor pistons are fixed on a cross-member interior 33 in which are formed openings 34, 35 for the free passage of the tie rods 25, 26 of the exterior movable element.
  • the compressor cylinders 11, 12, 13, 14 in which the compressor pistons 19, 20, 21, 22 work are advantageously fixed on the outside of the part 36 of the frame inside which are the piston-engine cylinder groups. .
  • the transverse part 33 of the internal movable element has a radial length greater than that of the transverse parts 23, 24 of the external movable element.
  • the minimum distance between the interior compressors and the axis is determined by the size of the sweeping and exhaust pants of the engine cylinders.
  • the invention entails other advantages .
  • This ease of assembly and disassembly is especially important for the valve plate of the compressor cylinders.
  • the injectors of the engine cylinders are also easily accessible and therefore easy to disassemble.
  • the air discharged by the external compressors 7, 8, 9, 10 can be cooled separately under very good conditions.
  • the exterior of the frame which surrounds the piston-engine cylinder groups and on which only the compressor cylinders of the internal moving assembly are mounted offers space for the installation of injection controls which can thus be brought closer to the injectors .
  • the variant illustrated in fig. 2, where the members corresponding to those of FIG. 1 bear the same reference number, comprises four groups of piston-engine cylinders: in this figure has been shown diagrammatically the radial size of the breeches 37 for sweeping and exhausting the engines.
  • the interior compressors 14 which are supported on the frame 36 cannot be closer to the axis than they are in FIG. 2, due in particular to the presence of the sweeping and exhaust pants surrounding the engine cylinders 2.
  • the pistons 38 are, in the embodiment of FIG. 3, carried by rods 40 integral with the crosspieces 23, placed in extension of an axial tie rod 41 which replaces the tie rods 25 and 26 of FIG. 1.
  • the rods 40 may be constituted by extensions of the tie rod 41 on which the crosspieces 23 are fixed.
  • the rod 40 extends beyond the piston 38 and it can thus be supported by guide bearings 42 placed on either side of each cylinder 39.
  • the axial tie rod 41 is, for its part, guided by two bearings 43 placed near the sleepers and one of which is visible in FIG. 3.
  • the crosspieces 23 can then either be guided only by the axial tie rod 41 and the rods 40 which carry them and slide in the guide bearings 43 and 42, or be further guided by sliding on an even number of rods or fixed tubes 44 arranged symmetrically, as shown in dashes in fig. 3.
  • Rods 44 can also guide the cross-member 33.
  • the internal cross member 33 which, due to the forces to which it is subjected, will generally be machined in a single forged part, is fixed to an axial guide tube 45, carried by bearings (not shown ) separated from each other, by a distance at least equal to three times the diameter of the tube, and fixed to the frame.
  • the cross member 33 comprises two opposite horizontal arms fixed to the rods of the pistons of the internal compressor cylinders 11-14. Two protrusions of the cross are attached to the rods of the eight pistons of the internal engine cylinders.
  • the external mobile assembly comprises two external cross members 23 whose span can be made much smaller than that of the central cross member 33, which offers several advantages. On the one hand, there is a tendency to balance the masses of internal and external crews inherently. On the other hand, the stresses undergone by the external crosspieces are significantly reduced, particularly during the driving phase, when forces of opposite signs are transmitted by the rods of external driving pistons and the tie rods 25 and 26 connecting between the crosspieces. 23, placed in line with the rods of the pistons of the compression cylinders 7, 10 and 8, 9. This arrangement of the tie rods allows them to pass outside the central cross-member 33. It is consequently possible to give them a one-piece construction and authorize a relatively easy disassembly of the cross-member 33.
  • central and external sleepers which has just been described has significant advantages compared to the arrangement which consists in placing the axes of the internal and external compressors in the same plane (FIG. 2).
  • a first solution consists in providing it with sliding bearings on fixed guide tubes.
  • tandem machine which has just been described can work, either as a compressor in which the compressed air in the compressor cylinders is discharged to the outside, or, and preferably, as pressurized gas autogenerator in which at least most of the compressed air in the compressor cylinders is used for sweeping and supercharging the engine cylinders in which the combustion gases only fully expand, so that a hot, pressurized mixture of combustion gases and purge air comes out of the exhaust openings of the engine cylinders, a mixture that can be used to drive a turbine.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Seasonings (AREA)
  • Control And Other Processes For Unpacking Of Materials (AREA)
  • Confectionery (AREA)

Claims (10)

1. Tandemmaschine mit entgegengestzten Freiflugkolben mit wenigstens zwei parallel nebeneinander angeordneten Motorgruppen mit Kolben und Zylindern und wenigstens zwei Verdichterelemente, wobei jede Motorgruppe mit Kolben und Zylindern (A, B) zwei in einer Flucht liegende Zylinder (1, 2) umfasst, in deren jedem zwei gegenläufige Motorkolben (3, 4 oder 5, 6) arbeiten, wobei die beiden äusseren Motorkolben (3, 6) einer jeden Gruppe mit Verdichterkolben (15, 16 oder 17, 18) durch äussere Querstücke (23, 24) verbunden sind, welche aneinander durch wenigstens ein Verbindungselement (25, 26) - befestigt sind, sodass eine äussere bewegliche Anordnung entsteht, während die beiden inneren Motorkolben (4, 5) einer jeden Gruppe miteinander und mit anderen Verdichterkolben durch ein inneres Querstück (33) verbunden sind, sodass eine innere bewegliche Anordnung entsteht, dadurch gekennzeichnet, dass die der äusseren beweglichen Anordnung angehörenden Verdichterkolben (15, 16, 17, 18) in axialer Richtung auf der Aussenseite der Querstücke (23, 24) dieser Anordnung angeordnet sind, während die der gleichen äusseren beweglichen Anordnung angehörenden Motorkolben (3, 6) und das Verbindungselement oder die Verbindungselemente (25, 26) auf der Innenseite dieser Querstücke (23, 24) liegen.
2. Maschine nach Anspruch 1, bei welcher jedes Querstück (23, 24) der äusseren beweglichen Anordnung auf einer Stange oder einem Rohr (27, 28) gleitet, welches sich zwischen zwei festen, beiderseits dieses Querstücks liegenden Haltern (29, 30 oder 31, 32) erstreckt, dadurch gekennzeichnet, dass der Halter (29 oder 31) des äusseren Endes des Rohrs oder der Stange zue Befestigung der Zylinder (7, 8 oder 9, 10) dient, in welchen der äusseren beweglichen Anordnung angehörende Verdichterkolben arbeiten.
3. Maschine nach Anspruch 1, dadurch gekennzeichnet, dass jedes Quarstück (23, 24) der äusseren beweglichen Anordnung an einem Stangen- oder Rohrabschnitt befestigt ist, wobei jeder dieser Abschnitte in zwei beiderseits dieses Querstücks angeordneten festen Lagern (42, 43) gleitet.
4. Maschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Verdichterzylinder (11 bis 14) der inneren beweglichen Anordnung an dem die Motorgruppe mit Kolben und Zylinderen umgebenden Gestell (36) angebracht sind.
5. Maschine nach Anspruch 1, bei welcher die Querstüpke der äusseren beweglichen Anordnung durch eine einzige in der Achse der Maschine angeordnete Verbindungsstange (41) verbunden sind, dadurch gekennzeichnet, dass die verbindungsstange jenseits der Querstücke Verlängerungen (40) zum Antrieb von auf diese Achse liegenden Verdichtern (39) aufweist.
6. Maschine nach Anspruch 5, dadurch gekennzeichnet, dass sich diese Verlängerungen jenseits der Verdichter in festen Führungslagern (42) erstrecken.
7. Maschine nach anspruch 5 oder 6, dadurch gekennzeichnet, dass die Querstücke von der axialen Verbindungsstange geführt werden, welche in feste Führungslagern (42, 43) gleitet.
8. Maschine nach Anspruch 1, dadurch gekennzeichnet, dass die innere bewegliche Anordnung auf jeder Seite des Querstücks vier längs der in der Ecke eines Rechtecks angeordneten Zylinderkolben (2) verschiebbare innere Motorkolben aufweist und zwei Verdichterkolben, die in die inneren Verdichtungszylinder (11, 12, 13 und 14) gleiten, deren Achsen an diesem Rechteck vorbeiführen, dass die äussere bewegliche Anordnung vier an jedem äusseren Querstück befestigte, in die Motorzylinder verschiebbare Motorkolben aufweist, und zwei Verdichterkolben, die in die äusseren Verdichterzylinder (7, 10 und 8, 9) gleiten und die Achsen der inneren Verdichterkolben (11, 14 und 12, 13) durch die Verlängerung der kleinen Mittellinie des Rechtecks führen, während die Achsen der äusseren Verdichterzylinder (7, 10 und 8, 9) durch die Verlängerung der grossen Mittellinie des Rechtecks führen (Fig. 4).
9. Maschine nach Anspruch 8, dadurch gekennzeichnet, dass die äusseren Querstücke von zwei in der Ebene der Achsen der äusseren Verdichter angeordneten Verbindungselementen (25, 26) geführt werden, vorzugsweise entlang den Achsen dieser Verdichter.
10. Maschine nach Anspruch 1 oder 9, dadurch gekennzeichnet, dass jedes Querstück mit Führungsmitteln versehen ist, die aus mindestens einem, an das Querstück befestigten, sich in die festen Lager verschiebbaren Rohr bestehen, wobei die Entfernung mindestens dem vierfachen Rohrdurchmesser entspricht.
EP80900774A 1979-05-07 1980-11-17 Tandemmaschine mit entgegengesetzten freien kolben Expired EP0028224B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7911513A FR2456231A1 (fr) 1979-05-07 1979-05-07 Perfectionnements apportes aux machines tandem a pistons libres opposes comportant plusieurs elements compresseurs
FR7911513 1979-05-07

Publications (2)

Publication Number Publication Date
EP0028224A1 EP0028224A1 (de) 1981-05-13
EP0028224B1 true EP0028224B1 (de) 1983-01-12

Family

ID=9225147

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80900774A Expired EP0028224B1 (de) 1979-05-07 1980-11-17 Tandemmaschine mit entgegengesetzten freien kolben

Country Status (11)

Country Link
US (1) US4412476A (de)
EP (1) EP0028224B1 (de)
JP (1) JPS6329090B2 (de)
BE (1) BE883149A (de)
CA (1) CA1132457A (de)
DE (1) DE3061594D1 (de)
FR (1) FR2456231A1 (de)
IT (1) IT1193389B (de)
NO (1) NO152061C (de)
SU (1) SU1036253A3 (de)
WO (1) WO1980002442A1 (de)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5020422A (en) * 1990-01-29 1991-06-04 Sims James O Piston/cylinder assembly
US5431087A (en) * 1994-06-15 1995-07-11 Kambara; Goro Extended stroke linear actuator assembly
NO306424B1 (no) * 1998-03-02 1999-11-01 Knut O Dalland Aggregat av trykkmediumsylindere
KR20080025366A (ko) * 2005-04-29 2008-03-20 텐딕스 디벨롭먼트, 엘엘씨 래디얼 임펄스 엔진, 펌프 및 압축기 시스템과 관련 동작방법
US20100242891A1 (en) * 2008-10-30 2010-09-30 Timber Dick Radial impulse engine, pump, and compressor systems, and associated methods of operation
CA2768939A1 (en) * 2011-11-18 2013-05-18 Lancaster Wind Systems Inc. Wind to electric energy conversion with hydraulic storage
CN105874218B (zh) * 2013-11-05 2020-02-07 伊顿智能动力有限公司 高输出液压缸和活塞结构
CN104329165B (zh) * 2014-10-17 2017-02-01 华侨大学 一种两缸四冲程液压自由活塞发动机

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1188375A (fr) * 1956-12-13 1959-09-22 Joy Mfg Co Groupe moto-compresseur à pistons libres
US2956555A (en) * 1958-02-07 1960-10-18 Braun Anton Free piston engine
FR1491208A (fr) * 1965-03-17 1967-08-11 Perfectionnements apportés aux machines à pistons libres
FR94629E (fr) * 1967-05-24 1969-09-19 Benaroya Henry Perfectionnements apportés aux machines tandem a piston libres.
FR1601540A (de) * 1968-12-27 1970-08-24
FR2432089A1 (fr) * 1978-07-26 1980-02-22 Benaroya Henry Installation de production d'energie a generateur a pistons libres

Also Published As

Publication number Publication date
IT8021860A0 (it) 1980-05-07
CA1132457A (fr) 1982-09-28
NO152061B (no) 1985-04-15
NO810015L (no) 1981-01-05
DE3061594D1 (en) 1983-02-17
BE883149A (fr) 1980-11-07
IT1193389B (it) 1988-06-15
JPS56500464A (de) 1981-04-09
FR2456231A1 (fr) 1980-12-05
WO1980002442A1 (fr) 1980-11-13
SU1036253A3 (ru) 1983-08-15
JPS6329090B2 (de) 1988-06-10
EP0028224A1 (de) 1981-05-13
US4412476A (en) 1983-11-01
NO152061C (no) 1985-07-24

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