EP0656461A2 - Gas engine with rotating blades - Google Patents
Gas engine with rotating blades Download PDFInfo
- Publication number
- EP0656461A2 EP0656461A2 EP94830548A EP94830548A EP0656461A2 EP 0656461 A2 EP0656461 A2 EP 0656461A2 EP 94830548 A EP94830548 A EP 94830548A EP 94830548 A EP94830548 A EP 94830548A EP 0656461 A2 EP0656461 A2 EP 0656461A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- gas engine
- previous
- fact
- rotating blades
- engine
- 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- Withdrawn
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
- F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F01C1/3446—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
Definitions
- the technics disposes of internal combustion engine as: gas turbine, pistone engine ( Otto or Diesel) and rotating engine ( Wankel ).
- Figures, 1 through 7 represent the working strokes of the engine. By these crossing sections, the shape proposed is the preferred design, but it could also be a different one.
- the engine we are talking about can have one or more stages connected between each other.
- FIG 1 shows a schematic crossing section where the ring 15 is static and his internal surfaces is shaped and the central rotor 10 runs around the axis 6.
- the couple of blades 12 and 13 have a radial motion inside the rotor and the end seal of blades describe the internal shape of the ring 15 during rotation.
- the blades are pushed to contact the internal shape of the ring 15 by a radial pressure.
- the pressure can be: pneumatic, hydraulics, mechanical or of a different kind.
- centrifugal thrust could be sufficient to ensure the sealing of blades to the profile of ring 15 without requiring any additional pressure.
- the number of blades is not binding, it fixes the shape of the inner ring surface which permits the working strokes of the engine.
- the working strokes of the engine are: inlet, compression, firing and exhaust.
- the figure 2 shows the beginning of the inlet stroke (see arrow F).
- the exhaust hole is sealed from the inlet hole by a seal 17 which is loaded on the rotor by the spring 18. Any different energy may be employed.
- the inlet of gases is realized during the rotation of the rotor 10 in direction of arrow F .
- the volume variation is defined by the external diameter of rotor, by the internal profile of ring 15 and the left lateral surface of blade 12.
- the inlet holes and the exhaust holes could have a different arrangement.
- the figure 3 shows the inleted gases at the end of inlet stroke (see arrow A).
- the arrow B shows the gases during the compression stroke between the blade 13P and the blade showed by arrow C.
- the figure 4 shows the volumetric change during the most difficult position of the compression stroke.
- thermic level raises as much as the pressure and the absorbtion of thermal energy increases.
- the figure 5 shows the compressed gases when the firing stroke starts.
- the fired gases energy produces a pressure, inside the combustion chamber, constraining the surface S of the blade 12P to rotate around the axis 6 and to slip along the internal profile of the static ring 15.
- the figure 7 shows the end of the exhaust of burned gases. To eliminate the burned gases as much as possible, an additional little duct connected to the exhaust hole has been designed. It can be seen on the figure 1.
- the seal 17 insures the separation of the inlet hole by the exhaust hole.
- the power attachement (the power shaft) is on the central rotor 10 and comes out from the flanges of the external seals coupled to the static ring 15 surfaces.
- Any kind of fuel can be used for this engine: gasoline, fuel oil, gas, petroil, etc.
- the ignition system may have a coil ignition, electronic ignition, or a different one.
- the cooling system can be with:
- the engine Using cooling liquid, the engine must be provided of internal ducts for the coolant.
- the engine In case of air cooling system, the engine must be provided of cooling ribs.
- the engine must be provided of a suitable lubricating system to allows parts to move one on each other freely without friction.
- the engine must have a complete set of accessories to rum in complete autonomy.
- the output power is 1/30 of the power calculated as the maximum pressure, during firing stroke on the piston surface, was on during the complete cycle (inlet, compression, firing, exhaust) and with the maximum torque lenght, refereted to the crankshaft.
- weight/power ratio that can be as low as 0.2, similar to the aviation gas turbine ratio.
Abstract
Description
- At the moment, the technics disposes of internal combustion engine as: gas turbine, pistone engine (Otto or Diesel) and rotating engine (Wankel).
- These kinds of engines have reached such a perfection through the years that any further effort to improve them could be uneconomical compared whith the new efficiency obtained.
- The advantages of the invention are:
- 1- more power at the same cubic capacity
- 2- low ratio weight/power
- 3- less volume
- 4- low production cost
- The invention is shown in the attached figures. Figures, 1 through 7, represent the working strokes of the engine. By these crossing sections, the shape proposed is the preferred design, but it could also be a different one.
- The engine we are talking about can have one or more stages connected between each other.
- The following description is refererred to one stage only in order to show its items and how the engine works.
- The figure 1, of the attached drawings, shows a schematic crossing section where the
ring 15 is static and his internal surfaces is shaped and thecentral rotor 10 runs around theaxis 6. The couple ofblades ring 15 during rotation. - The blades are pushed to contact the internal shape of the
ring 15 by a radial pressure. - The pressure can be: pneumatic, hydraulics, mechanical or of a different kind.
- At a given R.P.M. the centrifugal thrust could be sufficient to ensure the sealing of blades to the profile of
ring 15 without requiring any additional pressure. - The number of blades is not binding, it fixes the shape of the inner ring surface which permits the working strokes of the engine.
- The working strokes of the engine are: inlet, compression, firing and exhaust.
- The following description is referred to the running of the segment marked by the arrow showing the rotation direction.
- The figure 2 shows the beginning of the inlet stroke (see arrow F).
- The exhaust hole is sealed from the inlet hole by a
seal 17 which is loaded on the rotor by thespring 18. Any different energy may be employed. - The inlet of gases is realized during the rotation of the
rotor 10 in direction of arrow F. - The volume variation is defined by the external diameter of rotor, by the internal profile of
ring 15 and the left lateral surface ofblade 12. - Gases comes through the inlet hole 1 (see arrow) that is on the sealing lateral flanges fixed at the lateral surfaces of the
ring 15. - The inlet holes and the exhaust holes could have a different arrangement.
- The figure 3 shows the inleted gases at the end of inlet stroke (see arrow A).
- The inlet hole, now, is closed by
blade 13. The inleted gases, showed by arrow A, start to be compressed. - The arrow B shows the gases during the compression stroke between the
blade 13P and the blade showed by arrow C. - The figure 4 shows the volumetric change during the most difficult position of the compression stroke.
- It is well known that during an adiabatic transformation there is an absorbtion of thermal energy as much bigger as the thermic level is, and as much lower as the insulation is.
- Moreover, the thermic level raises as much as the pressure and the absorbtion of thermal energy increases.
- At this point, the compression ratio is bigger than the compression ratio during the firing stroke (see figure 5), which means that will be spent more energy than required for the firing condition.
- By increasing the compression ratio could be generated a spontaneous ignition involving the engine work.
- To avoid these troubles, a
pressure relieving piston 7 driven by a mechanical or different one fastener has been foreseen. - The figure 5 shows the compressed gases when the firing stroke starts.
- At this moment, between elctrodes of spark-
plug 9, which has to be designed for this kind of engine, the ignition spark is on. - The fired gases energy produces a pressure, inside the combustion chamber, constraining the surface S of the
blade 12P to rotate around theaxis 6 and to slip along the internal profile of thestatic ring 15. - At this moment starts the expansion of fired gases and it finishs at the beginning of
exhaust hole 14, as showed in the figure 6. - The figure 7 shows the end of the exhaust of burned gases. To eliminate the burned gases as much as possible, an additional little duct connected to the exhaust hole has been designed. It can be seen on the figure 1.
- The
seal 17 insures the separation of the inlet hole by the exhaust hole. - At this moment the working cycle of the engine is completed. It must noted that during a 360° run there will be a number of complete cycles (all strokes) equal to the number of the couples of
blades - The power attachement (the power shaft) is on the
central rotor 10 and comes out from the flanges of the external seals coupled to thestatic ring 15 surfaces. - Any kind of fuel can be used for this engine: gasoline, fuel oil, gas, petroil, etc.
- The ignition system may have a coil ignition, electronic ignition, or a different one.
- The cooling system can be with:
- 1) cooling liquid with:
- natural circulation with radiator
- forced circulation with a pump, thermal switch and radiator
- forced circulation of a cooling liquid in a sealed system, with pump, thermal switch and radiator
- 2) air circulation:
- with a fan and duct
- flowing ram air.
- Using cooling liquid, the engine must be provided of internal ducts for the coolant.
- In case of air cooling system, the engine must be provided of cooling ribs.
- The engine must be provided of a suitable lubricating system to allows parts to move one on each other freely without friction.
- The engine must have a complete set of accessories to rum in complete autonomy.
- To understand the advantages of such engine, it must point out with follows:
- 1) for a reciprocating engine the capacity is measured after a complete cycle. That happens in two revolution of the power shaft (crankshaft). i.e.
C = V·N where:
C = total capacity in cm²
V = volume of a single cylinder during inlet stroke (radius of piston²·π·suction stroke)
N = number of cylinders
Than, to compare the engine we are talking about, the capacity will be the volume of inleted gases during two revolutions of the rotor (item 10) i.e.
C = 2·V·n·S where:
C = total capacity
V = volume of inleted gases betweenblades 13 and 12p (see pos. A fig. 3)
n = number of couples of blades (12 and 13)
S = number of stages - 2) Talking of a reciprocating engine at the moment of the max pressure (firing), the lever torque lenght measured, normally to the axis of the piston, between the center of the crank and the power shaft axis, is at minimum lenght and increases to the max lenght when the gases pressure is drastically decreased. It still decreases up to the beginning of exit stroke.
- It is then possible to say that the max pressure works (power stroke) for about 1/15 of the completecycle with a lever torque lenght of about 1/2 of its maximum.
- Knowing that:
P = C·N/716.2 where:
P = power in HP
C = torque in Kgm
N = RPM - It is then possible to consideres that in a reciprocating engine, the output power is 1/30 of the power calculated as the maximum pressure, during firing stroke on the piston surface, was on during the complete cycle (inlet, compression, firing, exhaust) and with the maximum torque lenght, refereted to the crankshaft.
- In conclusion:
- (1) P = (Ps·S·b·N·n/716.2)·1/30 where:
P = power in HP
Ps = max pressure in Kg/cm²
S = piston topsurface
b = max torque lever lenght in m
N = RPM
n = number of pistons
Looking at this new engine we are talking about, we can to consider the max torque lenght to be constant and equal to the radius ofrotor 10.
To be noted that such radius is not related to the volume of the inleted gases (volume of the engine).
The max fired pressure works with an angle equal to:
(360°/n)·n where:
n = number of blade couples
Than we can to assume such pressure to be constant during a revolution ofrotor 10.
This is possible because, during the expansion, if the pressure of the fired gases decreases, the acting surface increases.
It is possible to say: - (2) P1 = Ps·S·b·N·n/716.2 where:
P1 = power in HP
Ps = max pressure in Kg/cm²
S = acting surface (see fig.5)
b = torque lever lenght (radius of rotor 10)
N = RPM
n = total efficiency
Using comparable values in (1) and (2), it is possible to demostrate that P1 is from 2 to 4 times higher then P. - An other advantage is the weight/power ratio that can be as low as 0.2, similar to the aviation gas turbine ratio.
Claims (21)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ITNA930027A IT1270497B (en) | 1993-12-03 | 1993-12-03 | INTERNAL COMBUSTION ENGINE WITH ROTATING VANE |
ITNA930027 | 1993-12-03 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0656461A2 true EP0656461A2 (en) | 1995-06-07 |
EP0656461A3 EP0656461A3 (en) | 1995-08-02 |
Family
ID=11387601
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94830548A Withdrawn EP0656461A3 (en) | 1993-12-03 | 1994-11-24 | Gas engine with rotating blades. |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0656461A3 (en) |
IT (1) | IT1270497B (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112006001615B4 (en) * | 2005-06-16 | 2014-02-06 | Arkady Ivanovich Tararuk | rotor motor |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR627392A (en) * | 1926-10-06 | 1927-10-03 | Turbine-type internal combustion engine | |
FR797578A (en) * | 1935-10-08 | 1936-04-29 | Explosion turbine engine | |
US2960075A (en) * | 1957-09-20 | 1960-11-15 | Hazel B Phillips | Rotary type fluid motor |
DE2043099A1 (en) * | 1970-08-31 | 1972-04-13 | Rizza, Pietro La; Lorenz, Paul; χ 9412 Schneeberg | Rotary piston internal combustion engine |
DE2256397A1 (en) * | 1972-11-17 | 1974-05-22 | Gerold Bieber | COMBUSTION ENGINE ACCORDING TO THE VINE CELL PRINCIPLE |
DE2316529A1 (en) * | 1973-04-03 | 1974-10-24 | Alfons Lugauer | POWER MACHINE, E.G. COMBUSTION OR HYDRAULIC MOTOR OR PUMP |
FR2273947A1 (en) * | 1974-06-07 | 1976-01-02 | Hogarth Alexander | INTERNAL COMBUSTION ROTARY ENGINE |
GB1427038A (en) * | 1973-02-13 | 1976-03-03 | Garton H W | Rotary-vane machine |
US3952709A (en) * | 1974-10-23 | 1976-04-27 | General Motors Corporation | Orbital vane rotary machine |
DE3004676A1 (en) * | 1980-02-08 | 1981-08-13 | Econo-Mo-Systems E.Scherf, 8034 Germering | IC engine with cylindrical rotor - has rotor centrally located in elliptical working chamber and sealed by vanes |
-
1993
- 1993-12-03 IT ITNA930027A patent/IT1270497B/en active IP Right Grant
-
1994
- 1994-11-24 EP EP94830548A patent/EP0656461A3/en not_active Withdrawn
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR627392A (en) * | 1926-10-06 | 1927-10-03 | Turbine-type internal combustion engine | |
FR797578A (en) * | 1935-10-08 | 1936-04-29 | Explosion turbine engine | |
US2960075A (en) * | 1957-09-20 | 1960-11-15 | Hazel B Phillips | Rotary type fluid motor |
DE2043099A1 (en) * | 1970-08-31 | 1972-04-13 | Rizza, Pietro La; Lorenz, Paul; χ 9412 Schneeberg | Rotary piston internal combustion engine |
DE2256397A1 (en) * | 1972-11-17 | 1974-05-22 | Gerold Bieber | COMBUSTION ENGINE ACCORDING TO THE VINE CELL PRINCIPLE |
GB1427038A (en) * | 1973-02-13 | 1976-03-03 | Garton H W | Rotary-vane machine |
DE2316529A1 (en) * | 1973-04-03 | 1974-10-24 | Alfons Lugauer | POWER MACHINE, E.G. COMBUSTION OR HYDRAULIC MOTOR OR PUMP |
FR2273947A1 (en) * | 1974-06-07 | 1976-01-02 | Hogarth Alexander | INTERNAL COMBUSTION ROTARY ENGINE |
US3952709A (en) * | 1974-10-23 | 1976-04-27 | General Motors Corporation | Orbital vane rotary machine |
DE3004676A1 (en) * | 1980-02-08 | 1981-08-13 | Econo-Mo-Systems E.Scherf, 8034 Germering | IC engine with cylindrical rotor - has rotor centrally located in elliptical working chamber and sealed by vanes |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112006001615B4 (en) * | 2005-06-16 | 2014-02-06 | Arkady Ivanovich Tararuk | rotor motor |
Also Published As
Publication number | Publication date |
---|---|
EP0656461A3 (en) | 1995-08-02 |
IT1270497B (en) | 1997-05-06 |
ITNA930027A0 (en) | 1993-12-03 |
ITNA930027A1 (en) | 1995-06-03 |
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