WO2000008325A1 - Eccentric and spring system for the internal and external combustion piston motors - Google Patents

Eccentric and spring system for the internal and external combustion piston motors Download PDF

Info

Publication number
WO2000008325A1
WO2000008325A1 PCT/TR1999/000033 TR9900033W WO0008325A1 WO 2000008325 A1 WO2000008325 A1 WO 2000008325A1 TR 9900033 W TR9900033 W TR 9900033W WO 0008325 A1 WO0008325 A1 WO 0008325A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
eccentric
piston
internal
crank
Prior art date
Application number
PCT/TR1999/000033
Other languages
French (fr)
Inventor
Hasan Basri ÖZDAMAR
Original Assignee
Oezdamar Hasan Basri
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 Oezdamar Hasan Basri filed Critical Oezdamar Hasan Basri
Priority to KR1020017001492A priority Critical patent/KR20010079611A/en
Priority to EP99939641A priority patent/EP1102925A1/en
Priority to JP2000563934A priority patent/JP2002522691A/en
Priority to AU53897/99A priority patent/AU5389799A/en
Publication of WO2000008325A1 publication Critical patent/WO2000008325A1/en

Links

Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/06—Adjustable connecting-rods
    • 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
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/22—Cranks; Eccentrics
    • F16C3/26—Elastic crank-webs; Resiliently-mounted crank-pins

Definitions

  • the present invention is related with realizing the production of a more efficient, more powerful and more environment friendly high speed motor, with a spring mechanism that elongates the crank moment arm, independent from the piston stroke and crank shaft rotational circumference in the internal-and external- combustion motors.
  • the moment arm length is equal to the radius of maximum crank shaft rotation circumference or to the half of the piston stroke.
  • the object of the present invention is to elongate the moment arm in internal and external combustion motors with pistons, by changing the center of the connection rod (4) to the utility direction whereas the two eccentrics in the connection rod (4) and crank shaft center remain fixed, wherein the crankshaft arm axis to which the connection rod (4) is joined and the connection rod (4) axis also remain fixed; and consequently a more environment friendly, more efficient and more powerful high-speed motor production is realized.
  • Figure 1 shows the components of the spring mechanism
  • Figure 2 shows the crank peg axis, small eccentric axis and big eccentric axis (connection rod axis) at the rotated positions of the crank shaft at 0°, 45°, 90°, 135°, 180°, 225°, 270°, 315°, 360°.
  • connection rod center 18) Larger eccentric centers at eight different points (connection rod center) 19) Shows the path (route) of the connection rod center
  • the spring mechanism that enhances the motor power, torque and speed by elongatine the crank moment arm, in internal and external combustion piston motors, consists of two coaxial eccentrics (5 and 6) placed on the crank peg (7) in the connection rod (4), and a guiding arm (6) connected directly to the small eccentric piece moving in connection with these eccentrics, a spring compressing arm (5) and spring compressing mechanism (8) directly connected to the larger eccentric, and a spring (11) one end of which is connected to the spring compression mechanism (8) and the other end, to the motor body.
  • the guiding arm (5) manufactured with one end fixed to the smaller eccentric, is provided with a channel (15) on its other end.
  • the guiding support ball (16) connected to the motor body is engaged into the said channel (15).
  • the eccentric (6) moves in connection with the support in the connection rod (4).
  • the center of the connection rod (4) changes, furthermore, the spring compression mechanism (8) and the assembly that facilitates the compression of the spring (11) moves around the axis, proportionally as much as the compression arm (5) and the spring compression allows, by being supported from the spring compression axis or from any suitable location.
  • the compression spring assembly consists of the larger eccentric and the guiding arm (5) fixed to it, a sliding roller bearing for the spring compression mechanism (13), spring compression joints (12), spring (11), crank shaft rotation circumference (10), smaller eccentric guiding support roller (15) and spring compression mechanism (8).
  • the piston (2) pressure acting on the connection rod (4) is greater than the pressure action on the piston (2) at angular positions, due to the eccentrics inside the connection rod (4).
  • the pressure turning the crank shaft (20) is more and the moment arm (length t) is longer; thus providing positive gain in significant amounts.
  • the spring (11) on the spring compression arm (5) acting on the arm from the spring compression mechanism (8) is fixed and the effect point acting on the crank peg (7) is movable, while tightening the spring (11), the spring (11) can be compressed with a larger moment arm. After the tightening of the spring (1 1) the moment arm remains constant with respect to the support point whereas the other arm is far shorter than the arm which tightened the spring. This situation provides numerous advantages with respect to moment arm and spring selection.
  • crank shaft axis and the cylinder (1) and piston (2) driving axis are completely different; this difference causes the piston (2) to provide more effective action of the pressure inside the cylinder (1) in the positive direction.
  • the difference between the crank peg (7) center and the connection rod (4) center holds the piston (2) at a position, higher than that of the crank peg (7) and therefore it is more effected by the pressure created by the explosion in the cylinder.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Transmission Devices (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

In the system consisting of two coaxial eccentrics (5 and 6) one within another, in the connecting rod (4), guiding arms directly connected to these eccentrics and a spring (11) one end of which is connected to the spring compression mechanism (8) and the other end to the motor body, the spring (11) is completely stretched when the piston (2) is at the upper dead point. By the rotation of the crank shaft (20), the piston (2) pushes down the connection rod (4) from the dead point, with the pressure of combusting gas. The stretched spring (11) being supported by the cocking catch lever support, pushes the larger eccentric (5) downswards by means of the cocking catch lever. Both impacts influence the smaller eccentric (6) inside the larger one (5) and the crank peg (7) inside the small eccentric (6) is pushed down by an additional moment arm, thus increasing the turning moment applied on the crank shaft (20).

Description

ECCENTRIC AND SPRING SYSTEM FOR THE INTERNAL AND EXTERNAL COMBUSTION PISTON MOTORS
The present invention is related with realizing the production of a more efficient, more powerful and more environment friendly high speed motor, with a spring mechanism that elongates the crank moment arm, independent from the piston stroke and crank shaft rotational circumference in the internal-and external- combustion motors.
In the conventional motors the moment arm length is equal to the radius of maximum crank shaft rotation circumference or to the half of the piston stroke.
In the patent No. 95/00742 wherein a longer moment arm is provided by means of the eccentrics, separately from the crankshaft rotation circumference and the piston stroke, the crank peg is fixed whereas the piston stroke is variable and the induction and explosion strokes are different. The induction stroke is greater. A spring is placed between the eccentrics inside the connection rod (4). The compression ratio varies depending on such factors as changing the support points of spring compressing arms and fixing them, approaching or diverging of the piston to the dead point due to the position of the spring between the eccentric coaxial pieces in the connection rod (4). This provides more power and higher torque at high speeds. However, both eccentric pieces in the connection rod (4) are under the impact of the spring, which leads to problems during the production phase.
The object of the present invention is to elongate the moment arm in internal and external combustion motors with pistons, by changing the center of the connection rod (4) to the utility direction whereas the two eccentrics in the connection rod (4) and crank shaft center remain fixed, wherein the crankshaft arm axis to which the connection rod (4) is joined and the connection rod (4) axis also remain fixed; and consequently a more environment friendly, more efficient and more powerful high-speed motor production is realized.
In the motors realised in order to achieve the objects of the present invention, the spring mechanism that enhances the motor torque, motor power and motor speed by elongating the crank moment arm, is illustrated in the attached drawings, wherein:
Figure 1) shows the components of the spring mechanism,
Figure 2) shows the crank peg axis, small eccentric axis and big eccentric axis (connection rod axis) at the rotated positions of the crank shaft at 0°, 45°, 90°, 135°, 180°, 225°, 270°, 315°, 360°.
The components shown in the drawings have been numerated separately as follows:
1) Cylinder
2) Piston 3) Piston peg
4) Connection rod
5) Larger eccentric and the eccentric spring compressing arm fixed on it,
6) Smaller eccentric and the eccentric directing piece arm fixed on it,
7) Crank peg 8) Spring stretching (compressing) mechanism
9) Spring stretching support ball
10) Crank shaft rotation circumference
11) Spring
12) Spring stretching ankle 13) Spring stretching mechanism sliding roller
14) Movement channel for larger eccentric spring clamping arm support ball 15) Smaller eccentric guiding support ball channel
16) Smaller eccentric guiding support ball channel
17) Smaller eccentric centres at eight different points
18) Larger eccentric centers at eight different points (connection rod center) 19) Shows the path (route) of the connection rod center,
20) Crank shaft.
The spring mechanism that enhances the motor power, torque and speed by elongatine the crank moment arm, in internal and external combustion piston motors, consists of two coaxial eccentrics (5 and 6) placed on the crank peg (7) in the connection rod (4), and a guiding arm (6) connected directly to the small eccentric piece moving in connection with these eccentrics, a spring compressing arm (5) and spring compressing mechanism (8) directly connected to the larger eccentric, and a spring (11) one end of which is connected to the spring compression mechanism (8) and the other end, to the motor body. The guiding arm (5) manufactured with one end fixed to the smaller eccentric, is provided with a channel (15) on its other end. The guiding support ball (16) connected to the motor body is engaged into the said channel (15)., When the crank shaft rotates and the motor starts to run, the eccentric (6) moves in connection with the support in the connection rod (4). With this movement the center of the connection rod (4) changes, furthermore, the spring compression mechanism (8) and the assembly that facilitates the compression of the spring (11) moves around the axis, proportionally as much as the compression arm (5) and the spring compression allows, by being supported from the spring compression axis or from any suitable location. The compression spring assembly consists of the larger eccentric and the guiding arm (5) fixed to it, a sliding roller bearing for the spring compression mechanism (13), spring compression joints (12), spring (11), crank shaft rotation circumference (10), smaller eccentric guiding support roller (15) and spring compression mechanism (8). When the piston is at the dead point, the spring is in a completely compressed state. When the crank shaft (20) starts to rotate clockwise, the piston (2) pushes the connection rod (4) down from the dead point by means of the pressure created by the gas exploded in the cylinder (1). This pushing motion is additionally effected by the compressed spring (11) being supported by the compression arm bracket, pushing the larger eccentric downwards by means of the compression arm (5). Both effects act on the smaller eccentric (6) in the larger one (5) and the crank peg (7) inside the small eccentric (6) is pushed downwards by an additional moment arm. Consequently the turning moment applied on the crank shaft (20) is enhanced due to the effect of the additional moment arm on the crank peg (7).
The piston (2) pressure acting on the connection rod (4) is greater than the pressure action on the piston (2) at angular positions, due to the eccentrics inside the connection rod (4). In other words, the pressure turning the crank shaft (20) is more and the moment arm (length t) is longer; thus providing positive gain in significant amounts. Furthermore due to the fact that the effect point location of the spring (11) on the spring compression arm (5) acting on the arm from the spring compression mechanism (8) is fixed and the effect point acting on the crank peg (7) is movable, while tightening the spring (11), the spring (11) can be compressed with a larger moment arm. After the tightening of the spring (1 1) the moment arm remains constant with respect to the support point whereas the other arm is far shorter than the arm which tightened the spring. This situation provides numerous advantages with respect to moment arm and spring selection.
As the crank shaft axis and the cylinder (1) and piston (2) driving axis are completely different; this difference causes the piston (2) to provide more effective action of the pressure inside the cylinder (1) in the positive direction. In other words, the difference between the crank peg (7) center and the connection rod (4) center, holds the piston (2) at a position, higher than that of the crank peg (7) and therefore it is more effected by the pressure created by the explosion in the cylinder.

Claims

1. Eccentric and spring system in the internal and external combustion motors with piston, characterized in that the spring (11) is completely compressed when the piston (2) is at the dead point; when the crank shaft (20) starts to rotate clockwise, the piston (2) pushes the connection rod (4) down from the dead point by means of the cressure created by the gas exploded in the cylinder (1); that the said pushing motion is additionally effected by the compressed spring (11) being supported by the compression arm bracket, pushing the larger eccentric down wards by means of the compression arm (5) ; that both effects act on the smaller eccentric (6) in the larger one (5) and the crank peg (7) inside the small eccentric (6) is pushed downwards by an additional moment arm and that consequently the turning moment applied on the crank shaft (20) is enhanced due to the effect of the additional moment arm on the crank peg (7).
2. Eccentric and spring system in the internal and external combustion motors with piston, according to Claim 1 , characterized with the guiding arm (6) one end of which is on the crank peg (7) in the connection rod (7), manufactured as fixed on the small eccentric (6) and the other end of which is provided with a channel, a guiding support ball connected to the motor body, being engaged into the said channel, (15) and when the crank shaft (20) rotates to start the motor, which provides the motion of the eccentric in the connection rod (4), as joined to the support.
3. Eccentric and spring system in the internal and external combustion motors with piston, according to Claim 1, characterized with the spring compression arm (5) carrying the spring compression mechanism (8), connected to the spring (11) over the spring compression joint (12), one end of which is connected to the larger eccentric on the crank peg (7) in the connection rod (4) and the other end of which is provided with a channel (14) so that the spring compression support ball (9) can move in it.
4. Eccentric and spring system in the internal and external combustion motors with piston, according to Claim 1, characterized with a spring (11) one end of which is connected to the spring compression mechanism (8) and the other end, to the motor body.
5. Eccentric and spring system in the internal and external combustion motors with piston, according to Claims 1 and 3, characterized in that the said larger eccentric (5) is directly acted upon by the spring (11).
6. Eccentric and spring system in the internal and external combustion motors with piston, according to Claims 1 and 4, characterized in that the effect of the said spring (11) on the spring compression mechanism (8) remains constant with respect to the support point.
PCT/TR1999/000033 1998-08-04 1999-08-04 Eccentric and spring system for the internal and external combustion piston motors WO2000008325A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
KR1020017001492A KR20010079611A (en) 1998-08-04 1999-08-04 Eccentric and spring system for the internal and external combustion piston motors
EP99939641A EP1102925A1 (en) 1998-08-04 1999-08-04 Eccentric and spring system for the internal and external combustion piston motors
JP2000563934A JP2002522691A (en) 1998-08-04 1999-08-04 Eccentric wheel and spring arrangement for internal combustion and external combustion engine piston motors
AU53897/99A AU5389799A (en) 1998-08-04 1999-08-04 Eccentric and spring system for the internal and external combustion piston motors

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
TR1998/1486 1998-08-04
TR9801486 1998-08-04

Publications (1)

Publication Number Publication Date
WO2000008325A1 true WO2000008325A1 (en) 2000-02-17

Family

ID=21621600

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/TR1999/000033 WO2000008325A1 (en) 1998-08-04 1999-08-04 Eccentric and spring system for the internal and external combustion piston motors

Country Status (5)

Country Link
EP (1) EP1102925A1 (en)
JP (1) JP2002522691A (en)
KR (1) KR20010079611A (en)
AU (1) AU5389799A (en)
WO (1) WO2000008325A1 (en)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2807105A1 (en) * 2000-04-04 2001-10-05 Peugeot Citroen Automobiles Sa INTERNAL COMBUSTION ENGINE WITH VARIABLE VOLUMETRIC RATIO AND CYLINDER
WO2001092700A1 (en) * 2000-05-29 2001-12-06 Meta Motoren- Und Energie-Technik Gmbh Device for modifying the compression of a cylinder in an ic piston engine
KR100388560B1 (en) * 2001-09-05 2003-06-25 엘지전자 주식회사 Rotary resonance type compressor assembly
DE10237044A1 (en) * 2002-08-09 2004-02-19 Helmut Obieglo Piston/cylinder, for an IC motor, has a guide linkage between the crank and the piston connecting rod to give an eccentricity in the guide path for improved power
KR100426358B1 (en) * 2001-09-05 2004-04-06 엘지전자 주식회사 Rotary resonance type compressor assembly
WO2004113681A1 (en) * 2003-06-26 2004-12-29 Arvid Murray Johnson Linear into rotatory or vice versa motion convertor
WO2005061893A1 (en) * 2003-12-24 2005-07-07 Lg Electronics Inc. Compressor
KR100785318B1 (en) * 2006-06-21 2007-12-17 엘지전자 주식회사 Compressor
DE102006054677A1 (en) * 2006-11-17 2008-05-21 Helmut Obieglo Prime mover e.g. thermal engine, has drive section describing path around rotation center, which is characterized by flow of eccentricity and movement of piston, which is subjected with load between upper and lower dead centers
CN100453850C (en) * 2003-06-26 2009-01-21 阿维德·默里·约翰逊 Linear into rotatory or vice versa motion convertor
WO2010009094A1 (en) * 2008-07-16 2010-01-21 Wilkins Larry C Internal combustion engine with improved fuel efficiency and/or power output
US8468997B2 (en) 2009-08-06 2013-06-25 Larry C. Wilkins Internal combustion engine with variable effective length connecting rod
US8746188B2 (en) 2010-03-17 2014-06-10 Larry C. Wilkins Internal combustion engine with hydraulically-affected stroke
US20150300241A1 (en) * 2014-02-04 2015-10-22 Ronald A. Holland Opposed Piston Engine
CN110700941A (en) * 2019-10-08 2020-01-17 何观龙 Engine capable of changing center resistance of crankshaft

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4628225B2 (en) * 2005-09-08 2011-02-09 株式会社ケイセブン Reciprocating cylinder device with variable compression ratio

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2287908A (en) * 1940-11-04 1942-06-30 Schmidt Henry Internal combustion engine
FR1146123A (en) * 1955-02-09 1957-11-06 Device for eliminating dead center in the rotation of crankshafts of internal combustion engines and steam engines
US3693463A (en) * 1970-08-03 1972-09-26 Wilbur G Garman Linkage for a reciprocating engine crankshaft

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2287908A (en) * 1940-11-04 1942-06-30 Schmidt Henry Internal combustion engine
FR1146123A (en) * 1955-02-09 1957-11-06 Device for eliminating dead center in the rotation of crankshafts of internal combustion engines and steam engines
US3693463A (en) * 1970-08-03 1972-09-26 Wilbur G Garman Linkage for a reciprocating engine crankshaft

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1143127A1 (en) * 2000-04-04 2001-10-10 Peugeot Citroen Automobiles SA Internal combustion engine with variable capacity and compression ratio
FR2807105A1 (en) * 2000-04-04 2001-10-05 Peugeot Citroen Automobiles Sa INTERNAL COMBUSTION ENGINE WITH VARIABLE VOLUMETRIC RATIO AND CYLINDER
WO2001092700A1 (en) * 2000-05-29 2001-12-06 Meta Motoren- Und Energie-Technik Gmbh Device for modifying the compression of a cylinder in an ic piston engine
US6581552B2 (en) 2000-05-29 2003-06-24 Meta Motoren-Und Energie-Technik Gmbh Apparatus for changing the compression of a cylinder of a piston engine
KR100388560B1 (en) * 2001-09-05 2003-06-25 엘지전자 주식회사 Rotary resonance type compressor assembly
KR100426358B1 (en) * 2001-09-05 2004-04-06 엘지전자 주식회사 Rotary resonance type compressor assembly
DE10237044A1 (en) * 2002-08-09 2004-02-19 Helmut Obieglo Piston/cylinder, for an IC motor, has a guide linkage between the crank and the piston connecting rod to give an eccentricity in the guide path for improved power
CN100453850C (en) * 2003-06-26 2009-01-21 阿维德·默里·约翰逊 Linear into rotatory or vice versa motion convertor
WO2004113681A1 (en) * 2003-06-26 2004-12-29 Arvid Murray Johnson Linear into rotatory or vice versa motion convertor
WO2004113682A1 (en) * 2003-06-26 2004-12-29 Arvid Murray Johnson Linear into rotatory or vice versa motion convertor
US7503305B2 (en) 2003-06-26 2009-03-17 Arvid Murray Johnson Rotatory crank shaft
US7908962B2 (en) 2003-12-24 2011-03-22 Lg Electronics Inc. Compressor
WO2005061893A1 (en) * 2003-12-24 2005-07-07 Lg Electronics Inc. Compressor
KR100785318B1 (en) * 2006-06-21 2007-12-17 엘지전자 주식회사 Compressor
DE102006054677A1 (en) * 2006-11-17 2008-05-21 Helmut Obieglo Prime mover e.g. thermal engine, has drive section describing path around rotation center, which is characterized by flow of eccentricity and movement of piston, which is subjected with load between upper and lower dead centers
WO2010009094A1 (en) * 2008-07-16 2010-01-21 Wilkins Larry C Internal combustion engine with improved fuel efficiency and/or power output
US9341110B2 (en) 2008-07-16 2016-05-17 Wilkins Ip, Llc Internal combustion engine with improved fuel efficiency and/or power output
US8468997B2 (en) 2009-08-06 2013-06-25 Larry C. Wilkins Internal combustion engine with variable effective length connecting rod
US8869769B2 (en) 2009-08-06 2014-10-28 Wilkins Ip, Llc Internal combustion engine with variable effective length connecting rod
US8746188B2 (en) 2010-03-17 2014-06-10 Larry C. Wilkins Internal combustion engine with hydraulically-affected stroke
US20150300241A1 (en) * 2014-02-04 2015-10-22 Ronald A. Holland Opposed Piston Engine
CN110700941A (en) * 2019-10-08 2020-01-17 何观龙 Engine capable of changing center resistance of crankshaft

Also Published As

Publication number Publication date
KR20010079611A (en) 2001-08-22
EP1102925A1 (en) 2001-05-30
AU5389799A (en) 2000-02-28
JP2002522691A (en) 2002-07-23

Similar Documents

Publication Publication Date Title
WO2000008325A1 (en) Eccentric and spring system for the internal and external combustion piston motors
US7293542B2 (en) Motor with rotary connecting rod bolt
JP2693197B2 (en) Power or work machines, especially internal combustion engines
KR100245960B1 (en) Crank mechanism
US4044629A (en) Reciprocating piston machine
US20020002957A1 (en) Variable compression ratio mechanism of reciprocating internal combustion engine
KR920703979A (en) An internal combustion engine
WO2000023699A1 (en) Crank system for internal combustion engine
JP2004506117A5 (en)
US3693463A (en) Linkage for a reciprocating engine crankshaft
US4301695A (en) Reciprocating piston machine
WO2010009094A1 (en) Internal combustion engine with improved fuel efficiency and/or power output
US6003480A (en) Wobble plate engine
US6273052B1 (en) Coupling arrangement for reciprocating piston engine
US11261947B2 (en) Apparatus to convert linear motion to rotary motion
WO2021006926A1 (en) Apparatus to convert linear motion to rotary motion
US20120019005A1 (en) Internal combustion engine with rocker member-affected stroke
JPH05504394A (en) A device for achieving four-cycle operation of an internal combustion engine, etc. by a single rotation of the crankshaft.
GB2245646A (en) (64) Variable compression ratio i.c. engine
RU2733794C1 (en) Motor
JP2958310B1 (en) Piston / crank mechanism
AU703504B2 (en) Wobble plate engine
RU2092697C1 (en) Piston engine
AU720401B2 (en) Internal combusion engines compression reciprocating engine
WO1995005551A1 (en) Slider-crank driving mechanism for the transformation of a reciprocating motion into rotation or vice versa

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AL AM AT AU AZ BA BB BG BR BY CA CH CN CU CZ DE DK EE ES FI GB GE GH GM HR HU ID IL IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MD MG MK MN MW MX NO NZ PL PT RO RU SD SE SG SI SK SL TJ TM TR TT UA UG US UZ VN YU ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW SD SL SZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE BF BJ CF CG CI CM GA GN GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
WWE Wipo information: entry into national phase

Ref document number: 1020017001492

Country of ref document: KR

WWE Wipo information: entry into national phase

Ref document number: 1999939641

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 09762250

Country of ref document: US

WWP Wipo information: published in national office

Ref document number: 1999939641

Country of ref document: EP

REG Reference to national code

Ref country code: DE

Ref legal event code: 8642

WWP Wipo information: published in national office

Ref document number: 1020017001492

Country of ref document: KR

WWW Wipo information: withdrawn in national office

Ref document number: 1999939641

Country of ref document: EP

WWW Wipo information: withdrawn in national office

Ref document number: 1020017001492

Country of ref document: KR