US3525215A - Counter piston machine,preferably counter piston motor with hydraulic driving mechanism - Google Patents

Counter piston machine,preferably counter piston motor with hydraulic driving mechanism Download PDF

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Publication number
US3525215A
US3525215A US746674A US3525215DA US3525215A US 3525215 A US3525215 A US 3525215A US 746674 A US746674 A US 746674A US 3525215D A US3525215D A US 3525215DA US 3525215 A US3525215 A US 3525215A
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United States
Prior art keywords
displacer
stroke
piston
counter
driving mechanism
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Expired - Lifetime
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US746674A
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English (en)
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Hans-Joachim Conrad
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Fried Krupp AG
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Fried Krupp AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H43/00—Other fluid gearing, e.g. with oscillating input or output
    • 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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/08—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders arranged oppositely relative to main shaft and of "flat" type
    • 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
    • F01B11/08—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type with direct fluid transmission link

Definitions

  • the present invention relates to a counter piston machine, preferably counter piston motor, With hydraulic driving mechanism.
  • a counter piston machine preferably counter piston motor
  • the advantages of a counter piston machine, especially of a two-cycle counter piston motor, are well known.
  • the counter piston motor yields a satisfactory combustion chamber, avoids the heat losses occurring on the cylinder covers, and permits a simple direct flow scavenging.
  • the invention is particularly directed to a counter piston machine with hydraulic driving mechanism as disclosed, for instance, in German Pat. No. 1,179,778, corresponding to US. Pat. 3,066,476-Conrad issued Dec. 4, 1962.
  • a hydraulic driving mechanism according to the said patent is characterized in that a stroke displacer cooperating with a reciprocating machine element, and a rotating displacer connected with a rotating machine element are interconnected through a hydraulic linkage system.
  • the pressure fluid delivered by said stroke displacer is split up into at least two partial flows. This split-up in partial flows is intended to compensate for all radial and axial pressure forces which are exerted by the pressure fluid upon the rotating displacer. Only the tangential circumferential forces remain which correspond to the torque and which act upon the rotating displacer.
  • sealing elements are provided between the housing and the rotating displacer therein. These sealing elements are guided to be displaceable either in radial or axial or in any desired direction and form pressure chambers into which the partial flows lead which are delivered by the stroke displacer.
  • FIG. 1 illustrates a two-cylinder counter piston motor with a hydraulic driving mechanism according to the prior art
  • FIG. 2 is an axial section through the cylinders of a two-cylinder counter piston diesel engine with a hydraulic driving mechanism according to the invention.
  • FIG. 3 is an axial section through the cylinders of a counter piston motor according to a modification of the present invention with a portion of a hydraulic driving mechanism.
  • this motor will now be described with regard to the working cylinder on hce the left-hand side only. It is assumed that all functions of the other working cylinder on the right-hand side are the same as those on the left-hand side and that only its displacers run ahead or lag with a phase displacement relative to the stroke of the displacers on the left-hand side.
  • a rotatable displacer 2 rotates in the housing 1 of the hydraulic driving mechanism, said displacer 2 being connected to the output shaft 3.
  • Four sliding blocks 4 are slidably arranged in said housing 1 and seal the rotor with regard to the housing, thereby forming four pressure chambers.
  • the two pressure chambers 5, 6 respectively associated with the left-hand working cylinder 4a are arranged diametrically opposite to each other.
  • the counter pistons of the gas sides 7 and 8 are connected through piston rods 9 and 10 to the stroke displacers 11 and 12 for feeding the liquid pressure means.
  • the upper stroke displacer 11 presses the liquid pressure means through a conduit 13 into the pressure chamber 5 of the hydraulic driving mechanism, whereas the lower stroke displacer 12 presses the liquid pressure means through a passage 14 of the hydraulic driving mechanism into the pressure chamber 6;
  • the invention is based on a counter piston machine with a hydraulic driving mechanism of the general type set forth above, and is characterized in that with a counter piston machine of this type, two stroke displacers respectively positively connected with counter pistons are 3 arranged in series in such a way that one of the stroke displacers will through a fluid column act upon the back side of the other stroke displacer, which latter by means of its front side alone acts upon the hydraulic linkage.
  • the fluid medium pressures produced by the two stroke displacers of a working cylinder be of the same magnitude. Pressure variations which result from a different mass force of the two stroke displacers or from a different step-up ratio between the gas piston and the displacers delivering the liquid fluid medium, or from different flow losses will no longer have any influence upon the running of the hydraulic driving transmission.
  • a further advantage of the arrangement according to the invention consists in that the stroke of the two counter pistons does not have to be of the same magnitude. Instead, the strokes of the two counter pistons may be of different magnitude.
  • the stroke of the lower stroke displacer and of the lower gas piston is determined by the stroke volume of the rotating displacer.
  • the stroke of the upper gas piston is determined by the stroke of the lower gas piston and by the surface ratio of the effected piston surface of the stroke displacers which enclose the liquid pressure medium therebetween. If a complete mass equalization or balance is desired, the products of the weight of each of the two stroke displacers and the respective strokes pertaining thereto must be of the same magnitude.
  • FIG. 2 of the drawing illustrating an axial section through the cylinders of a two-cylinder counter piston diesel engine with a hydraulic transmission
  • the housing 1 contains a working shaft 3 having mounted thereon the rotating displacer 3.
  • Four sliding blocks 4 are radially displaceably arranged in housing 1 in such a way that through the intervention of sealing strips 4b they engage the outer circumference of the rotating displacer 2 and also engage lateral covers of the housing (not shown). In this way the sliding blocks 4 seal off four pressure chambers.
  • Each two oppositely located pressure chambers are acted upon by a lower stroke displacer of the two illustrated working cylinders.
  • the actuation of two oppositely located pressure chambers is, however, the fundamental difference over that in FIG. 1.
  • the pressure chamber 5 is acted upon by the upper stroke displacer 11 through the passage 13
  • the pressure chamber 6 is acted upon by the lower stroke displacer 12 through the passage 14.
  • both pressure chambers 5 and 6 associated with the left-hand working cylinder 4a are acted upon by the lower stroke displacer 12. More specifically, the pressure chamber 5 is acted upon by the lower stroke displacer 12 through a passage 17, whereas the pressure chamber 6 is acted upon by the lower stroke displacer 12 through a passage 14.
  • the liquid pressure medium delivered by the upper stroke displacer 11 is passed into a pressure chamber 19 through a passage 18 on the back side of the lower stroke displacer 12.
  • the said delivered fluid pressure medium then acts upon an annular surface 12a which equals the difference between the piston surface 12b of the lower stroke displacer 12 and the cross-section of the piston rod 10. If now in the combustion chamber 20 an ignition takes place, the two gas pistons 7 and 8 are driven away from each other, and these pistons now act through the stroke displacer 12 feeding the liquid pressure medium upon the rotating displacer 2.
  • the lower counter piston 8 with the piston rod 10 and the lower stroke displacer 12 is by gas pressure or the inertia force pressed against the fluid pressure medium.
  • conditions of operation are possible in which this will not be assured.
  • the inertia force is insufficient to press the lower piston safely against the liquid pressure medium.
  • a conduit 15 to convey a gaseous or liquid pressure medium to the lower side of the lower stroke displacer in order to assure a safe pressing.
  • the upper counter piston 7 is no longer through piston rod 9 directly connected to a stroke displacer for the liquid pressure medium. Instead, the upper counter piston 7 is connected through a transverse yoke 21 and two pull-rods 22 and 23 to two stroke displacers 24 and 25 which through the intervention of the liquid pressure medium in chamber 19 act upon the back side of stroke displacer 12.
  • a gaseous or liquid pressure medium it is possible with the embodiment of FIG. 3 to cause a gaseous or liquid pressure medium to act through feeding lines 26 and 27 upon the back sides of the stroke displacers 24 and 25.
  • the invention is applicable in connection with counter piston motors and also with machine tools which work in conformity with the counter piston principle, for instance, two compressors and pumps.
  • a twostrokc-cycle operation may be considered.
  • the invention is also applicable to four-stroke-cycle engines, for instance, with counter piston four-stroke-cycle compressors.
  • the rotating displacer may also be provided with axially displaceable sliding blocks.
  • a counter piston machine which includes: cylinder means, two counter running pistons reciprocable in said cylinder means, first and second linearly movable displacer means respectively rnovably connected to said counter running pistons, said second linearly movable displacer means having a smaller piston area and an oppositely located larger piston area, means for hydraulically connecting said first displacer means with said smaller piston area of said second linearly movable displacer means, rotatable displacer means, and passage means establishing communication between said larger piston area of said second linearly movable displacer means and said rotary displacer means for conveying fluid displaced by said second linearly movable displacer means to said rotary displacer means 2.
  • a machine which includes: piston rods respectively connecting said first and second linearly movable displacer means with said counter running pistons so that each of said first and second displacer means has a smaller piston area adjacent the respective piston rod pertaining thereto and located opposite a piston area larger than said smaller piston area by the diameter of the piston rod cross-section adjacent said smaller piston area, and chamber means arranged adjacent to and communicating with said smaller piston area of said second linearly movable displacer means and also communicating with said passage means, said passage means communicating with the larger piston area of said first linearly movab e displacer means.
  • said first linearly movable displacer means comprises at least two dilferential displacer pistons having the smaller piston area thereof in fluid communication with each other and with the smaller area of said second linearly movable displacer means, and which includes yoke means and piston rod means interconnecting said smaller piston areas of said two differential pistons with the counter running piston pertaining thereto.
  • a machine which includes: conduit means communicating with the smaller piston area of said first displacer means and adapted to be connected to a source of pressure fluid.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Hydraulic Motors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)
US746674A 1967-07-22 1968-07-22 Counter piston machine,preferably counter piston motor with hydraulic driving mechanism Expired - Lifetime US3525215A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19671650630 DE1650630B1 (de) 1967-07-22 1967-07-22 Hydrostatisches Getriebe

Publications (1)

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US3525215A true US3525215A (en) 1970-08-25

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US746674A Expired - Lifetime US3525215A (en) 1967-07-22 1968-07-22 Counter piston machine,preferably counter piston motor with hydraulic driving mechanism

Country Status (9)

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US (1) US3525215A (pm)
BE (1) BE718381A (pm)
CH (1) CH494909A (pm)
DE (1) DE1650630B1 (pm)
FR (1) FR1579136A (pm)
GB (1) GB1198378A (pm)
IE (1) IE32205B1 (pm)
NL (1) NL6809760A (pm)
SE (1) SE330465B (pm)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3702057A (en) * 1969-12-23 1972-11-07 Grundig Emv Process for control and regulation of double piston-driven engine with hydrostatic motion transducers
US3704585A (en) * 1969-12-23 1972-12-05 Grundig Emv Process for controlling and regulating piston-driven engines with hydrostatic motion transducers
US3767325A (en) * 1972-06-20 1973-10-23 M Schuman Free piston pump
US3782859A (en) * 1971-12-07 1974-01-01 M Schuman Free piston apparatus
US3811283A (en) * 1972-02-11 1974-05-21 Battelle Institut E V Multi-cylinder stirling gas motor with double-acting pistons
US3839863A (en) * 1973-01-23 1974-10-08 L Frazier Fluid pressure power plant
US3990239A (en) * 1974-01-24 1976-11-09 Daimler-Benz Aktiengesellschaft Hot gas piston engine
US4345437A (en) * 1980-07-14 1982-08-24 Mechanical Technology Incorporated Stirling engine control system
US4350012A (en) * 1980-07-14 1982-09-21 Mechanical Technology Incorporated Diaphragm coupling between the displacer and power piston
US4387568A (en) * 1980-07-14 1983-06-14 Mechanical Technology Incorporated Stirling engine displacer gas bearing
US4387567A (en) * 1980-07-14 1983-06-14 Mechanical Technology Incorporated Heat engine device
US4408456A (en) * 1980-07-14 1983-10-11 Mechanical Technolgy Incorporated Free-piston Stirling engine power control
US4418533A (en) * 1980-07-14 1983-12-06 Mechanical Technology Incorporated Free-piston stirling engine inertial cancellation system
US4733534A (en) * 1986-09-29 1988-03-29 Southard Albert A Internal combustion engine and output motion transducer
US6065289A (en) * 1998-06-24 2000-05-23 Quiet Revolution Motor Company, L.L.C. Fluid displacement apparatus and method
GB2379482A (en) * 2002-01-15 2003-03-12 Alexander Orestovich Monfor Hydraulic motor-generator
US7363760B1 (en) 2003-10-02 2008-04-29 Mccrea Craig R Thermodynamic free walking beam engine
WO2014129923A1 (ru) 2013-02-22 2014-08-28 Kasyanov Vadim Vadimovich Двигатель внутреннего сгорания
US20160376983A1 (en) * 2015-06-23 2016-12-29 Ricardo Daniel ALVARADO ESCOTO Highly efficient two-stroke internal combustion hydraulic engine with a torquing vane device incorporated.

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61129401A (ja) * 1984-11-28 1986-06-17 Daikichiro Isotani 液圧による動力伝達機構を有するフリ−ピストン機関
RU2207447C2 (ru) * 1999-11-30 2003-06-27 Касьянов Вадим Константинович Способ работы силовой установки и силовая установка для его осуществления
RU2199672C2 (ru) * 2001-05-14 2003-02-27 Касьянов Вадим Константинович Силовая установка
WO2008024019A1 (fr) * 2006-08-15 2008-02-28 Sergej Vitalievich Eliseev Installation de transformation d'énergie
DE102009010746B3 (de) * 2009-02-26 2010-07-01 Hyon Engineering Gmbh Umweltfreundlicher Motor in modularer Bauweise
WO2011144188A1 (de) 2010-05-17 2011-11-24 Hyon Engineering Gmbh Brennkraftmaschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3024591A (en) * 1958-12-23 1962-03-13 American Mach & Foundry Bounce compensator for free piston engines
US3031972A (en) * 1956-06-23 1962-05-01 Janicke Hermann Free piston engine driven pump assembly
US3066476A (en) * 1960-02-06 1962-12-04 Beteiligungs & Patentverw Gmbh Arrangement for converting a reciprocatory movement into a rotary movement
US3073108A (en) * 1961-10-23 1963-01-15 Ward Walter Internal combustion engine
US3085392A (en) * 1959-12-03 1963-04-16 Achilles C Sampietro Internal combustion engines
US3119230A (en) * 1961-05-10 1964-01-28 Kosoff Harold Free piston engine system

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE296450C (pm) *
US1457968A (en) * 1921-07-12 1923-06-05 Esnault-Pelterie Robert Continuous-action synchronizer
CH247096A (de) * 1945-09-18 1947-02-15 Schweizerische Lokomotiv Einrichtung zur Synchronisierung von gegenläufigen Freiflugkolben.
DE1179778B (de) * 1960-02-06 1964-10-15 Beteiligungs & Patentverw Gmbh Vorrichtung zur Umwandlung einer hin- und hergehenden Bewegung in eine Drehbewegung und umgekehrt, insbesondere fuer Brennkraft-maschinen

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3031972A (en) * 1956-06-23 1962-05-01 Janicke Hermann Free piston engine driven pump assembly
US3024591A (en) * 1958-12-23 1962-03-13 American Mach & Foundry Bounce compensator for free piston engines
US3085392A (en) * 1959-12-03 1963-04-16 Achilles C Sampietro Internal combustion engines
US3066476A (en) * 1960-02-06 1962-12-04 Beteiligungs & Patentverw Gmbh Arrangement for converting a reciprocatory movement into a rotary movement
US3119230A (en) * 1961-05-10 1964-01-28 Kosoff Harold Free piston engine system
US3073108A (en) * 1961-10-23 1963-01-15 Ward Walter Internal combustion engine

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3702057A (en) * 1969-12-23 1972-11-07 Grundig Emv Process for control and regulation of double piston-driven engine with hydrostatic motion transducers
US3704585A (en) * 1969-12-23 1972-12-05 Grundig Emv Process for controlling and regulating piston-driven engines with hydrostatic motion transducers
US3782859A (en) * 1971-12-07 1974-01-01 M Schuman Free piston apparatus
US3811283A (en) * 1972-02-11 1974-05-21 Battelle Institut E V Multi-cylinder stirling gas motor with double-acting pistons
US3767325A (en) * 1972-06-20 1973-10-23 M Schuman Free piston pump
US3839863A (en) * 1973-01-23 1974-10-08 L Frazier Fluid pressure power plant
US3990239A (en) * 1974-01-24 1976-11-09 Daimler-Benz Aktiengesellschaft Hot gas piston engine
US4387567A (en) * 1980-07-14 1983-06-14 Mechanical Technology Incorporated Heat engine device
US4350012A (en) * 1980-07-14 1982-09-21 Mechanical Technology Incorporated Diaphragm coupling between the displacer and power piston
US4387568A (en) * 1980-07-14 1983-06-14 Mechanical Technology Incorporated Stirling engine displacer gas bearing
US4345437A (en) * 1980-07-14 1982-08-24 Mechanical Technology Incorporated Stirling engine control system
US4408456A (en) * 1980-07-14 1983-10-11 Mechanical Technolgy Incorporated Free-piston Stirling engine power control
US4418533A (en) * 1980-07-14 1983-12-06 Mechanical Technology Incorporated Free-piston stirling engine inertial cancellation system
US4733534A (en) * 1986-09-29 1988-03-29 Southard Albert A Internal combustion engine and output motion transducer
US6065289A (en) * 1998-06-24 2000-05-23 Quiet Revolution Motor Company, L.L.C. Fluid displacement apparatus and method
GB2379482A (en) * 2002-01-15 2003-03-12 Alexander Orestovich Monfor Hydraulic motor-generator
GB2379482B (en) * 2002-01-15 2003-11-26 Alexander Orestovich Monfor Hydraulic motor-generator
US7363760B1 (en) 2003-10-02 2008-04-29 Mccrea Craig R Thermodynamic free walking beam engine
WO2014129923A1 (ru) 2013-02-22 2014-08-28 Kasyanov Vadim Vadimovich Двигатель внутреннего сгорания
US20160376983A1 (en) * 2015-06-23 2016-12-29 Ricardo Daniel ALVARADO ESCOTO Highly efficient two-stroke internal combustion hydraulic engine with a torquing vane device incorporated.

Also Published As

Publication number Publication date
NL6809760A (pm) 1969-01-24
FR1579136A (pm) 1969-08-22
IE32205L (en) 1969-01-22
DE1650630B1 (de) 1970-08-20
BE718381A (pm) 1968-12-31
CH494909A (de) 1970-08-15
IE32205B1 (en) 1973-05-16
SE330465B (pm) 1970-11-16
GB1198378A (en) 1970-07-15

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