EP0183258A2 - Freikolbenmaschine mit einem hydraulischen Übertragungsmechanismus - Google Patents

Freikolbenmaschine mit einem hydraulischen Übertragungsmechanismus Download PDF

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Publication number
EP0183258A2
EP0183258A2 EP85115091A EP85115091A EP0183258A2 EP 0183258 A2 EP0183258 A2 EP 0183258A2 EP 85115091 A EP85115091 A EP 85115091A EP 85115091 A EP85115091 A EP 85115091A EP 0183258 A2 EP0183258 A2 EP 0183258A2
Authority
EP
European Patent Office
Prior art keywords
piston
hydraulic
free piston
crankshaft
free
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.)
Withdrawn
Application number
EP85115091A
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English (en)
French (fr)
Other versions
EP0183258A3 (de
Inventor
Isogai Daikichiro
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0183258A2 publication Critical patent/EP0183258A2/de
Publication of EP0183258A3 publication Critical patent/EP0183258A3/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers
    • 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
    • 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
    • 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
    • F02B71/045—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby with hydrostatic transmission
    • 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
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the present invention relates to a free piston engine having a hydraulic power transmission mechanism.
  • An object of the invention to provide a free piston engine having a hydraulic power transmission mechanism which is simple in structure and requires little space.
  • a free piston engine having a hydraulic power transmission mechanism characterised by: at least one free piston one end face of which is exposed to pressure of combustion gas or compressed gas and the other end face of which is exposed to hydraulic pressure, said free pistons being adapted to reciprocably move in a cylinder; a rotary piston rotatably mounted on a crank pin of a crankshaft to rotate about the crank pin, said rotary piston having the contour of epitrochoidal curve as seen in the cross-sectional plane; and a hydraulic power transmission system having working hydraulic medium filled in a space defined between the other end face of the free piston and the rotary piston so as to convert linear reciprocable movement of the free piston to rotational movement of the crankshaft.
  • the principle of operation of the engine is based on the conversion of reciprocable movement of the piston, through a hydraulic system, to rotary movement of the crankshaft and vice versa.
  • pistons in the engine of the invention act as free pistons of which one end face serves as cover for inhibiting leakage of working liquid, for instance, hydraulic oil.
  • An epitrochoid rotary piston to be described later carries out quasi-reciprocable movement as the crankshaft rotates and its effective volume varies in the sine-curved fashion.
  • the crankshaft is caused to rotate in such a direction that the aforesaid pressure decreases.
  • a rotary body has the crosssectional configuration comprising an epitrochoidal curve which extends around the crank pin of the crankshaft, a predetermined relation is established between ratio of the number of revolutions of the crankshaft to the number of revolutions of the epitrochoidal body and direction of rotation by employing a train of phase gears. Further, when the extent of eccentricity of the epitrochoidal rotary body is equalized to an extent of eccentricity of the crank pin, it results that the epitrochoidal rotary body acts as a rotary piston.
  • FIG. 1 schematically illustrates the case where a single epitrochoidal rotary body is rotatably mounted on the crank pin of the crankshaft, wherein a mark • designates a center of rotation of the crankshaft and a mark 0 .does a center of rotation of the epitrochoidal rotary body. Further, reference letter R designates a radius of generation of epitrochoid and reference letter e does an extent of eccentricity.
  • the crankshaft rotates in the clockwise direction and the epitrochoidal rotary body does in the anticlockwise direction by the same extent.
  • the epitrochoidal rotary body carries out a kind of reciprocable movement relative to the crankshaft during their rotation as mentioned above.
  • the epitrochoidal rotary body is referred to below as epitrochoidal rotary piston or simply as rotary piston.
  • sealing members adapted to come in slidable contact with the rotary piston are secured not to the rotary piston but to the housing in which the rotary piston is accomodated.
  • the engine is provided with phase gears in order to associate the number of revolutions of the crankshaft with the number of revolutions of the epitrochoidal rotary piston.
  • Fig. 2 which schemically illustrates the case where a pinion (smaller diameter gear) having a pitch circle of which diameter is determined to 1/2 dt comes in rolling contact with a stationary gear wheel (ring gear) having a pitch circle of which diameter is determined to dt, the pinion is caused to rotate as shown in Figs. 2 (a) to (d) when it is operatively connected to the epitrochoidal rotary piston.
  • a pinion small diameter gear
  • ring gear stationary gear wheel
  • a volume of discharged oil or displacement volume V of the epitrochoidal rotary piston is represented by the following equation, when a plurality of working chambers whose number is represented by Z are formed in the space as defined between the epitrochoidal rotary piston and the cylinder (see, for instance, "The Wankel R C Engine” authored by R. F. Ansdale).
  • the epitrochoidal rotary piston is a single knot epitrochoidal rotary piston as shown in Fig. 1, the number of Z amounts to 2.
  • the equation (3) can be represented in the modified manner as noted below.
  • the diameter d& of pitch circle of the gear wheel is determined two times as wide as the diameter ds of pitch circle of the pinion but dimensional determination should be made in such a manner that the epitrochoidal rotary piston carries out movement as shown in Fig. 1. This can be achieved by allowing the gear wheel to rotate at a certain rate relative to the crankshaft without any necessity for immovably holding the gear wheel.
  • the diameter ds of pitch circle of the pinion is determined on the basis of dimension of the crankshaft and the dimension e is determined on the basis of volume of discharged oil
  • the diameter dl of pitch circle of the gear wheel is determined automatically because there is a necessity for meeting the requirement associated with the relation as represented by the equation (1).
  • the equation (2) fails to be established and therefore decision should be made as to at what rate the gear wheel should rotate relative to the crankshaft in order to maintain the operative relation between the pinion and the crankshaft.
  • a ratio of the diameter dk of pitch circle of the gear wheel (ring gear) to the diameter ds of pitch circle of the pinion (smaller diameter gear) is determined as noted below.
  • the pinion As the crankshaft rotates in the clockwise direction, the pinion is caused to rotate in the anticlockwise direction.
  • the engine of the invention includes a space filled with hydraulic medium in the area located between reciprocable free pistons and epitrochoidal rotary pistons in order to transmit generated power from the free pistons to the rotary pistons.
  • the space of which both opened ends are closed by the free piston and the rotary piston is called below as “working hydraulic chamber”. This working hydraulic chamber should meet the following two requirements.
  • the engine of the invention includes a cylinder housing 10 in which cylinders 12a and 12b are fitted. Intake holes on both the cylinders 12a and 12b are communicated with a scavenging pipe 13, whereas exhaust holes on the same are communicated with an exhaust pipe 14.
  • the middle part of each of the cylinders 12a and 12b is surrounded by a cooling water passage 15. As will be best seen from Fig. 6, the middle parts of the cylinders 12a and 12b are communicated with pre-combustion chambers 17a and 17b.
  • An intermediate wall 19a, a top housing 50 and a top cover 51 are arranged one above another on the cylinder housing 10, whereas an intermediate wall 19b and an output section housing 30 are arranged below the lower end of the cylinder housing 10.
  • the top cover 51, the top housing 50, the intermediate wall 19a, the cylinder housing 10, the intermediate wall 19b and the output section housing are firmly fastened by means of a plurality of tightening bolts 53 to build an integral structure.
  • the top housing 50 is provided with hydraulic cylinders 50a and 50b which are located in vertical alignment with the cylinders 12a and 12b
  • the output section housing 30 is provided with hydraulic cylinders 30a and 30b which are located in vertical alignment with the cylinders 12a and 12b.
  • Piston portions lla', llb' llc' and lld' adapted to receive gas pressure are accomodated in the cylinders 12a and 12b as well as the cylinders 12a and 12b and piston portions lla", llb", llc" and lld" adapted to be exposed to hydraulic pressure are accomodated in the hydraulic cylinders 50a, 50b, 30a and 30b of both the top housing 50 and the output section housing 30.
  • the piston portions as mentioned above are connected to one another via intermediate rods llao, llbo, llco and lldo whereby free pistons lla, llb, llc and lld are built.
  • the intermediate walls 19a and 19b have holes formed thereon through which the intermediate rods llao, llbo, llco and lldo are slidably displaced and each of the holes is fitted with an O-ring for the purpose of inhibiting an occurrence of oil leakage.
  • a predetermined pressure hydraulic chamber 35 is formed in the space as defined between the hydraulic cylinders 30a, 30b, 30c and 30d and the intermediate rods llao, llbo, llco and lldo.
  • each of the hydraulic chambers 35 is communicated with hydraulic pressure source such as accumulator or the like (not shown) via an inlet port 18 and a hydraulic passage 35' extending through the cylinder housing 10 in the vertical direction.
  • An output shaft 31 extends through the output section cylinder 30 in the horizontal direction and epitrochoid rotary pistons 33a and 33b are rotatably mounted on the crank portion of the output shaft 31.
  • the one rotary piston 33a defines working hydraulic chambers 34a and 34b between both the free pistons llb and 11d.
  • the other rotary piston 33b defines working hydraulic chambers 34c and 34d between both the free pistons lla and 11c.
  • Hydraulic oil in the working hydraulic chambers 34a and 34c is extracted therefrom by a predetermined volume by operating a metering pump 40a for the purpose of inhibiting an occurrence of deterioration of hydraulic oil and the situation is the same with hydraulic oil in the working hydraulic chambers 34b and 34d which is extracted therefrom in the same manner.
  • reference numerals 20a, 20b, 20c and 20d each designate a respective mechanical stop which serves to stop further upward and downward movement of the free pistons. These stops provide oil by-pass holes not to disturb the flow.
  • the rotary pistons 33a and 33b are provided with phase gears 38a and 38b in the form of pinion at the outer end part of their axial extension.
  • the pinions 38a and 38b mesh with phase gears 37a and 37b (having a larger diameter) in the form of ring gear along the inner periphery of the latter.
  • the gears 37a and 37b are rotatably mounted in such a manner as to rotate relative to the output shaft 31.
  • the gears 37a and 37b mesh with gears 36d and 36e which are fixedly mounted on an auxiliary shaft 32 extending in parallel with the output shaft 31.
  • Another gear 36c fixedly mounted on the auxiliary shaft 32 is brought in meshing engagement with a gear 36a fixedly mounted on the output shaft 31 via an intermediate gear 36b.
  • a series of speed reduction gears as mentioned above are accomodated in the space as defined between the side covers 41a and 41b for the working hydraulic chambers and the end covers 42a and 42b.
  • a speed reduction ratio is properly determined for each of the gears in accordance with the principle as described above.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)
  • Fuel-Injection Apparatus (AREA)
EP85115091A 1984-11-28 1985-11-28 Freikolbenmaschine mit einem hydraulischen Übertragungsmechanismus Withdrawn EP0183258A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP251414/84 1984-11-28
JP25141484A JPS61129401A (ja) 1984-11-28 1984-11-28 液圧による動力伝達機構を有するフリ−ピストン機関

Publications (2)

Publication Number Publication Date
EP0183258A2 true EP0183258A2 (de) 1986-06-04
EP0183258A3 EP0183258A3 (de) 1987-05-13

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP85115091A Withdrawn EP0183258A3 (de) 1984-11-28 1985-11-28 Freikolbenmaschine mit einem hydraulischen Übertragungsmechanismus

Country Status (2)

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EP (1) EP0183258A3 (de)
JP (1) JPS61129401A (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996033343A1 (en) * 1995-04-20 1996-10-24 Split Cycle Technology Limited Free piston engine
AU694858B2 (en) * 1995-04-20 1998-07-30 Split Cycle Technology Limited Free piston engine
RU2476698C1 (ru) * 2011-06-24 2013-02-27 Касьянов Вадим Вадимович Свободнопоршневой двигатель внутреннего сгорания
WO2014129923A1 (ru) * 2013-02-22 2014-08-28 Kasyanov Vadim Vadimovich Двигатель внутреннего сгорания

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1252964B (de) * 1960-05-18 1967-10-26 Beteiligungs & Patentverw Gmbh Brennkraftmaschine
FR1579136A (de) * 1967-07-22 1969-08-22
DE2137114A1 (de) * 1971-07-24 1973-02-01 Herwig Dipl Ing Dr Ing Kress Hydrostatisches getriebe

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4878313A (de) * 1972-01-31 1973-10-20
JPS5439524A (en) * 1977-09-05 1979-03-27 Hitachi Ltd Display unit with next screen display function

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1252964B (de) * 1960-05-18 1967-10-26 Beteiligungs & Patentverw Gmbh Brennkraftmaschine
FR1579136A (de) * 1967-07-22 1969-08-22
DE2137114A1 (de) * 1971-07-24 1973-02-01 Herwig Dipl Ing Dr Ing Kress Hydrostatisches getriebe

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996033343A1 (en) * 1995-04-20 1996-10-24 Split Cycle Technology Limited Free piston engine
AU694858B2 (en) * 1995-04-20 1998-07-30 Split Cycle Technology Limited Free piston engine
US6029616A (en) * 1995-04-20 2000-02-29 Split Cycle Technology Limited Free piston engine
RU2476698C1 (ru) * 2011-06-24 2013-02-27 Касьянов Вадим Вадимович Свободнопоршневой двигатель внутреннего сгорания
WO2014129923A1 (ru) * 2013-02-22 2014-08-28 Kasyanov Vadim Vadimovich Двигатель внутреннего сгорания

Also Published As

Publication number Publication date
EP0183258A3 (de) 1987-05-13
JPS61129401A (ja) 1986-06-17

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