WO1993003265A1 - Oldham drive engine - Google Patents
Oldham drive engine Download PDFInfo
- Publication number
- WO1993003265A1 WO1993003265A1 PCT/JP1992/000989 JP9200989W WO9303265A1 WO 1993003265 A1 WO1993003265 A1 WO 1993003265A1 JP 9200989 W JP9200989 W JP 9200989W WO 9303265 A1 WO9303265 A1 WO 9303265A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- flange
- slider
- engine
- case
- output
- Prior art date
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
- F16H—GEARING
- F16H21/00—Gearings comprising primarily only links or levers, with or without slides
- F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
- F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
- F16H21/18—Crank gearings; Eccentric gearings
- F16H21/22—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric
- F16H21/28—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric with cams or additional guides
-
- 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
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/04—Engines with prolonged expansion in main cylinders
-
- 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
Definitions
- the present invention relates to a piston engine in which the pressure in a cylinder received by a piston is transmitted to an output shaft as effectively as possible. It relates to an Oldham-driven engine that effectively outputs as rotational torque. Background art
- engines that have become widespread in practical use include a piston engine that transmits the reciprocating motion of the cylinder to the crankshaft through a rod and a crank, and a combustion chamber around the rotor to directly control the mouth.
- a rotating engine is known.
- the rotary engine is only used for special specifications because the output shaft rotates smoothly and the output efficiency is good, but the fuel consumption cost is high.
- An object of the present invention is to provide an Oldham-driven engine for effectively extracting the maximum combustion pressure near the top dead center of Biston to an output shaft so as to solve the above-mentioned problems.
- the present invention provides a case in which a cylinder, into which a piston connected to the tip of a rod is inserted, is rotatably supported by an output shaft that rotates in connection with reciprocation of a base end of the rod. It concerns a fixed engine.
- a flange-shaped slider is housed in the case, and the slider is connected to an end of the pad with a rotating shaft.
- An idler flange rotatably supported on the inner surface of the case and a flange fixed to the output shaft are provided on both sides of the slider in such a manner as to be rotatable on the inner surface of the case with a fixed axial distance therebetween.
- ridges are formed so as to be mutually slidable and alternately intersect.
- the high driving force of the piston which can be obtained at the moment when the combustion pressure is the highest at the time of combustion at the piston top dead center position in the piston engine, is the same as that of the conventional engine.
- the amount of energy taken out to the output side is large and the rotation of the output shaft is performed smoothly.
- the reduction mechanism can be omitted correspondingly.
- the present invention also provides the above-mentioned engine, wherein the shaft center of the idler flange is The axis of the output flange is arranged at a rotationally symmetric position with respect to the axis of the cylinder, and the straight line connecting the axes of both flanges has a constant phase in the anti-rotation direction of the slider with respect to the axis of the cylinder. Forming a corner. As a result, the torque is most efficiently transmitted to the output shaft from the moment the piston starts from top dead center, and the explosion engine in the cylinder is output without waste.
- a plurality of combinations of cylinders and cases are arranged and connected and fixed, and idler flanges connected to the side surfaces of the sliders in each case via the uneven strips are rotatable at the partition portions of the adjacent cases.
- An output shaft is provided on the case at the end of a plurality of cases that are pivotally supported and connected.
- the axis of the two idler flanges in each case or the axis of the idler flange and the output flange is arranged at a rotationally symmetric position with respect to the axis of each cylinder.
- the straight line connecting the axes of the two flanges forms a constant phase angle in the counter-rotating direction of the slider with respect to the axis of the cylinder, so that the efficiency of the piston is higher than the instant when the piston starts from top dead center. Good output is obtained.
- FIG. 1 is a sectional view showing an embodiment of the engine of the present invention
- FIG. 2 is a sectional view taken along the line II--II in FIG. 1
- FIG. 3 is an abbreviated description of an engine corresponding to FIG.
- FIG. Fig. 4 is an explanatory diagram of a conventional piston engine and its output measurement method.
- Fig. 5 is a comparison diagram of the output between the Oldham-driven engine shown in Figs. 3 and 4 and the conventional Biston engine. The figure shows a comparison of the output of Oldham ⁇ driven engines and a conventional biston engine, which were tested under conditions different from those shown in Fig. 5, and Fig. 7 shows the case where the Oldham-driven engine was replaced with two cylinders. It is sectional drawing which shows an example of a case. BEST MODE FOR CARRYING OUT THE INVENTION
- FIGS. 1 to 3 are principle structural diagrams of an engine showing an embodiment of the present invention, in which a piston 2 is inserted into a cylinder 1, and the cylinder is provided with intake and exhaust ports 5a and 5b.
- a combustion chamber 3 is formed on the rod side, and one end of a piston rod 4 is connected to the piston 2 from the back (lower) surface side by a connecting shaft 6, and an output end of the rod 4 is an Oldham case described below. Inserted in 7.
- the Oldham case 7 incorporates an idler flange 8, an output flange 9 and a slider 11, which will be described later.
- the Oldham case 7 has a circular shape when viewed from the front so as to provide a space for the above-mentioned slider 11 to rotate (revolve) along the circular orbit 12, and has a cylindrical opening 1 at the upper end. 3 is connected to the lower end opening of the cylinder 1 at a flange 14 provided on the outer peripheral edge of the opening 13.
- a circular idler flange 8 is rotatably fitted to and supported by a bearing 16 on the rear side in the Oldham case 7.
- an output flange 9 is rotatably supported by an output shaft 17 at a position parallel to the idler flange 8 and at a lower position with a fixed center distance L therebetween.
- the output flange 9 and the output shaft 17 are rotatably supported by a housing 18 also serving as a cap which is detachably fitted to the front side of the Oldham case 7.
- the above flanges 8 and 9 are supported by abrasion-resistant ceramic bearings or bearings as appropriate, and an oil line (oil groove) is formed when the peripheral surface forms a sliding surface. '.
- two circular plates 10 a and 10 b are integrally connected by a shaft 19 at the center of both plates.
- the formed spool-shaped slider 11 is inserted, and a boss 20 at the output end of the rod 4 is connected to the shaft 19.
- the concavo-convex strips 8a, 11a and 11b are fitted on the opposing surfaces of the flanges 8, 9 and both surfaces of the slider 11 so as to pass through their respective center points and to be slidable in the normal direction to each other.
- 9b are formed, and the ridges 8a, 11a and the ridges lib, 9b are cross-shaped so as to be orthogonal to each other when viewed from the front.
- each ridge is The combination of the idler flange 8, the output flange 9, and the slider 11 may be the rotation of the slider 11 if one of the flanges 8, 9 rotates. It constitutes an Oldham coupling mechanism in which the rotation is transmitted to the other flange via the revolution.
- piston 2 when piston 2 is retracted (down) by the generation of combustion pressure with piston 2 at the top dead center as shown in Figs. Due to the tilting and sliding action of the slider, the slider 11 rotates (revolves) in the same direction along the circular slider path 12 while rotating clockwise (rotating), and the output flange 9 and the output shaft 17 are rotated. Driven clockwise.
- the idler flange 8 rotates once, and the rotation and revolution of the slider 11 makes the output shaft 17 rotate half a turn, and the rotation speed is reduced to 1Z2.
- One revolution of the output shaft 17 includes two explosion processes.
- the axis of the output flange 9 and the idler flange 8 in this embodiment is rotationally symmetric positions with respect to the axial center of the silicon Sunda 1, moreover centerline B 2 connecting the axes of the flanges 8, 9 on the axis
- a fixed phase angle 6 (for example, 35 °) is provided in the counter-rotating direction of the slider 11, and when the piston 2 starts from the top dead center A, it rotates most efficiently with respect to the output shaft 17. It has a structure to transmit power.
- Fig. 5 shows a model test of the difference in the rotational force of the output shaft 17 using the mechanism of the engine according to the present embodiment (Fig. 3) indicated by reference numeral a (Fig. 3) and the conventional piston engine (Fig. 4) indicated by reference numeral b. 7 is a graph measured and compared by using FIG. That is, in this embodiment, as shown in FIG. 3, a measuring arm 21 is attached to the output shaft 17 to apply a constant load to the piston 2 from above, and the rotational torque T of the tip of the measuring arm 21 is applied. Was measured according to the change in the rotation angle / S of the arm 21.
- Fig. 4 shows a conventional piston engine mechanism.
- the cylinder 1, piston 2, rod 4, etc. corresponding to each part of the engine mechanism of the above embodiment are all denoted by the same reference numerals, and the dimensions of each part are the same. It was the same as that of the Oldham drive engine shown in Fig. 1 to Fig. 3.
- the output efficiency of the piston 2 with respect to the output shaft 17 is greater in the present embodiment indicated by the symbol a from the moment of starting than in the conventional crank type piston engine indicated by the symbol b. If this is extremely high and continues up to about 90 ° after starting the output shaft, a is approximately 1.6 times that of b in terms of the integrated output ratio.
- Fig. 6 shows the conditions of the mechanism of the engine according to the present invention and the conventional piston engine.
- FIG. 5 is a measurement comparison diagram obtained by performing a model test under conditions different from those shown in FIG. 5 (differences are indicated by the asterisks * above).
- the engine of the present invention reduces the rotation speed of the output shaft 17 to 1 Z2 for driving the piston as compared with a conventional crankshaft engine, but the normal engine output is greatly reduced by the operating drive. Since the speed is reduced, there is an advantage that the speed reduction mechanism can be omitted only for that portion, but there is no practical problem.
- FIG. 6 shows an example in which the engine of the present invention is a two-cylinder engine.
- the cylinder 1 and the Oldham case ⁇ are connected in series as shown in the figure, and two flanges 8,
- a spool-like flange that is fixed coaxially to the shaft 8 by a shaft 21 is rotatably supported by a shaft, and both sliders 11 are connected.
- a housing 18 ' is attached in the Oldham case 7 on the left side of the figure.
- the idler flange 8 ' is pivotally supported, and the rotating force of the left slider 11 is transmitted to the output shaft 17 via the flange 8, the right slider 11 and the flange 9.
- the left piston 2 is provided at a position where a smooth rotational force is generated in the most efficient phase with respect to the right piston 2. It is also possible to increase the number of cylinders and use multiple cylinders. Industrial applicability
- the Oldham-driven engine of the present invention can be used as a prime mover in a wide field like the conventional crank-type piston engine and rotary engine.
- the engine of the present invention can be used as an engine for automobiles, various working machines, working vehicles, generators, and the like.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transmission Devices (AREA)
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP92916705A EP0597104B1 (en) | 1991-08-02 | 1992-08-03 | Oldham drive engine |
DE69223970T DE69223970T2 (de) | 1991-08-02 | 1992-08-03 | Maschine mit oldhamkupplung |
US08/182,157 US5425334A (en) | 1991-08-02 | 1992-08-03 | Oldham drive engine |
KR1019940700259A KR970004671B1 (ko) | 1991-08-02 | 1992-08-03 | 올덤 구동 엔진 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3/216177 | 1991-08-02 | ||
JP3216177A JP2530951B2 (ja) | 1991-08-02 | 1991-08-02 | オルダム駆動エンジン |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1993003265A1 true WO1993003265A1 (en) | 1993-02-18 |
Family
ID=16684497
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1992/000989 WO1993003265A1 (en) | 1991-08-02 | 1992-08-03 | Oldham drive engine |
Country Status (6)
Country | Link |
---|---|
US (1) | US5425334A (ja) |
EP (1) | EP0597104B1 (ja) |
JP (1) | JP2530951B2 (ja) |
KR (1) | KR970004671B1 (ja) |
DE (1) | DE69223970T2 (ja) |
WO (1) | WO1993003265A1 (ja) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19607920A1 (de) * | 1996-03-01 | 1997-09-04 | Bayerische Motoren Werke Ag | Hypozykloidisches Kurbelgetriebe für Hubkolbenmaschinen, insbesondere Brennkraftmaschinen |
US5755195A (en) * | 1996-03-11 | 1998-05-26 | Dawson; Lyle E. | Internal combustion engine with a gear arrangement on a connection between the piston and the crankshaft and a method of operation thereof |
JP2000130101A (ja) * | 1998-10-29 | 2000-05-09 | Nikko:Kk | 4サイクル内燃エンジン |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01240701A (ja) * | 1988-03-18 | 1989-09-26 | Nissan Shatai Co Ltd | 可変容量型往復ピストン装置 |
JPH01247708A (ja) * | 1988-03-29 | 1989-10-03 | Nissan Shatai Co Ltd | 可変容量型往復ピストン装置の潤滑油供給構造 |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3563222A (en) * | 1968-07-16 | 1971-02-16 | Kenjiro Ishida | Perfectly balanced vibrationless rotation-reciprocation devices of crankshaft rotary motion system |
US4073196A (en) * | 1976-08-13 | 1978-02-14 | Gilbert T. Hendren, Jr. | Cranking system of varying radius |
JPS6477701A (en) * | 1987-09-18 | 1989-03-23 | Nissan Shatai Co | Variable capacity reciprocating piston unit |
JPH01190901A (ja) * | 1988-01-22 | 1989-08-01 | Nissan Shatai Co Ltd | 可変容量型往復ピストン装置 |
GB8904058D0 (en) * | 1989-02-10 | 1989-04-05 | Jaguar Cars | Internal combustion engine |
-
1991
- 1991-08-02 JP JP3216177A patent/JP2530951B2/ja not_active Expired - Lifetime
-
1992
- 1992-08-03 KR KR1019940700259A patent/KR970004671B1/ko not_active IP Right Cessation
- 1992-08-03 DE DE69223970T patent/DE69223970T2/de not_active Expired - Fee Related
- 1992-08-03 EP EP92916705A patent/EP0597104B1/en not_active Expired - Lifetime
- 1992-08-03 US US08/182,157 patent/US5425334A/en not_active Expired - Fee Related
- 1992-08-03 WO PCT/JP1992/000989 patent/WO1993003265A1/ja active IP Right Grant
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01240701A (ja) * | 1988-03-18 | 1989-09-26 | Nissan Shatai Co Ltd | 可変容量型往復ピストン装置 |
JPH01247708A (ja) * | 1988-03-29 | 1989-10-03 | Nissan Shatai Co Ltd | 可変容量型往復ピストン装置の潤滑油供給構造 |
Non-Patent Citations (1)
Title |
---|
See also references of EP0597104A4 * |
Also Published As
Publication number | Publication date |
---|---|
DE69223970D1 (de) | 1998-02-12 |
JP2530951B2 (ja) | 1996-09-04 |
EP0597104B1 (en) | 1998-01-07 |
US5425334A (en) | 1995-06-20 |
KR970004671B1 (ko) | 1997-04-02 |
EP0597104A4 (en) | 1995-11-29 |
JPH0539731A (ja) | 1993-02-19 |
EP0597104A1 (en) | 1994-05-18 |
DE69223970T2 (de) | 1998-06-04 |
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