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
  • F01C1/348—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 vanes positively engaging, with circumferential play, an outer rotatable member
• • 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
  • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
  • F01C21/10—Outer members for co-operation with rotary pistons; Casings
  • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
  • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
• • 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
  • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
  • F02B53/04—Charge admission or combustion-gas discharge
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
  • F05C2203/00—Non-metallic inorganic materials
  • F05C2203/08—Ceramics; Oxides
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• thermodynamic cycles are the well known and widely applied Otto, Diesel and Joule cycles. The efficiency is function of the thermodynamic data of the said cycles.
• thermodynamic data The developing forces and the air-exhaust gases separation systems are calculated on the basis of the thermodynamic data:
• thermodynamic cycle system in which participates a constant volume of exhaust gases, fact that has a result the production of the same work by means of a large machine volume in comparison to the proposed solution.
• b. The existence of ceramic protection in conjuction with the existence of an autonomous cooling system (with air surplus) allows the proposed invention to operate with very High temperatures, fact that has as a result the increase of the efficiency, c.
• the mechanism of the patent DE3315571 can not operate as high temperature expander requiring the existence of an autonomous system for the cooling of the moving parts.
• Ceramics 15,16 of the present invention do not come into conduct with vanes 8. According to a prefered embodiment they are incorporated into side covers 4,5 so that their outer surf ace-which is flat- is inside these side covers. The distance between the outer suf ace of side covers and the outer surface of the ceramics is very small (indicatively 40 ⁇ ). According to a preffered embodiment the ceramics 15 -6 are rings. According to another embodiment they are parts of rings which protect the side covers from high temperatures. The boundary conditions which are impopsed in the outer suuf ace of the side covers 4,5 are defined from the thermodynamic cycles which are realised by the present invention according to the existing bibliography.
• the cover 4 has cavities 17, wherein flows the cooling water.
• the cover 5 has cavities 18, wherein also the cooling water flows .
• the cover 10 is connected to the covers 4 and 5 through connecting rods 19 and bolts 20.
• the covers 4,5 together with the mounts 21, 22 and the bolts 23,24 constitute the supporting complex of the whole system.
• the cover 5 is connected to the air pump 26 through the conduid 27.
• the cover 4 bears an exhaust gases conduid. Through the air pump 26 air is introduced in the conduit 27.
• the present invention operates as Otto engine, so that inside the conduit 27 there is a separation plate 28 which prevents the contact of the gasified fuel introduced by the injection system with the air of space 30.
• a separation plate 28 which prevents the contact of the gasified fuel introduced by the injection system with the air of space 30.
• Inside the space 31 takes place gasification of the fuel and the created mixture is then directed in the compression space 34 through the passage 32.
• the currents in the conduit 30 push away the exhaust gases which comes from the expander 35 and coduct it through the passage 33 to the outlet 38.
• the created high temperature at the side covers is balanced by the use of the ceramic material 15 and 16 which does not come into contact with the moving parts.
• cooling water flows through the conduits 17 and 18, on the basis of the data of the cooling systems of the internal combustion engines and with reference to the heat exchange data, according to the above mentioned references relative to the heat exchange. Purpose of this cooling is to form a thermal field such that it permits the elements 13,14 to operate under the limits of their thermal strength.
• the cylinder 9, rotating on the bearings 11 and 12 inside the cover 10, is subjected to thermal oscillation, that is to say it is subjected to high temperatures in the combustion space 39 and the discharge space 35, whereas in the compression space 34 and after the scavenging procedure, it is subjected to low temperatures which correspond to the new intake mixture and to the compression stroke.
• thermal oscillation that is to say it is subjected to high temperatures in the combustion space 39 and the discharge space 35
• the compression space 34 and after the scavenging procedure it is subjected to low temperatures which correspond to the new intake mixture and to the compression stroke.
• the cylinder 9 as well as the drum 6 and the vanes 8 are subjected to thermal oscillation and consequently, according to the theory of the internal combustion engines, are kept into acceptable temperature limits.
• the cooling system of the whole mechanism can be embodied by means of the scavenging system and only with air surplus from the air pump 26, whose flow rate - with reference to the existing bibliography - is calculated in such a way that the removed heat from the vanes 8, the drum 6 and the cylinder 9, during the scavenging, because of the high velocity and thus of the high heat transmission coefficient, will be equal to the gained one by the same elements during the rest strokes.
• the right operation of the cooling system allows the stability of the clearances and the maintenance of a small gap between the vanes 8 and the side covers 4,5.
• the igniters according to a preffered embodiment can be placed either inside or outside the ceramic elements 15,16. They consist of a cylinder of porcelain having in its center an internal metal wire. The plane of the outer surface of the igniter coincides with the outer surface of the ceramic elements. The spark is created through the passage of minimum resistance between the wire of the igniter and the cylinder 9 or the drum 6. According to another prefered embodiment the igniters can be placed on the drum 6 as it will be mentioned later.
• the materials which are used have dimensions with tolerances which protect the whole structure and the parts from mechanical loads due to thermal expansions. The tolerances are calculated according to the existing bibliography.
• the fuel enters the combustion space 39, through injection systems located at the positions 42,43 according to the data of the technology which has developed about the embodiment of the Diesel cycle. In this case there is no separating plate 28 and fresh air is introduced in the compression space 34.
• the scavenging -cooling system operates in the same way as in the first preffered embodiment, as well as all the stated systems apart from the ignition system, which is replaced by the injection system.
• the precise positions of the injectors, according to one preffered embodiment, are estimated by reduction of the rotary engine to a piston engine, using as basic parameter the ratio ⁇ .
• the fuel supply which is achieved at the piston engines in a discontinuous manner, is achieved according to a preffered embodiment of the present invention continuously.
• injectors of continuous injection the position and the capacity of which can be defined - for a given thermodynamic cycle- according to the existing bibliography.
• the injectors 42,43 can be placed either inside the ceramics 15,16 in the case they are rings, or outside them in the case they are parts of rings.
• a hole with diameter equal to that of an injector is needed to be made.
• this hole can be made by means of a powder metallurgy method.
• a wire with diameter equal to that of an injector is placed inside the powder material in the position that the hole is desired. During the compaction and sintering process, this wire becomes liquid and thus can be rejected, leaving a hole.
• fibers of graphite can be used instead of a metal wire. These fibers can be elimineted through oxidation.
• the igniters and the injection systems of the first and second preffered embodiment can be adapted on the drum 6, and the transmitted current, either electric current of fuel current to the injectors, can be produced by a selector arrangement placed on the shaft 1 outside the whole mechanism and, through passages in the shaft 1 and the drum 6, it can end up to the igniters when reffering to Otto cycle or to the injectors when reffering to Diesel cycle.
• the drum 6 is in contact with the cylinder 9, so the compressed air gets out through the passage 45 (figure 5) - which corresponds to a double-side exhaust from the side covers 4,5 - moving to the burner 46 and therefrom returns to the mechanism through the passage 44, which corresponds to a double-side inlet through the side covers 4,5, where it expands inside the space 35, arriving thereafter at the exhaust gases scavenging system 37 which is schematically represented in fig. 4.
• the burner 46 may be generally substituted by a heat exchanger.
• this heat exchanger can transmit heat by the use of solar energy.
• the mentioned embodiment which is schematically illustrated at figure 5, concerns an embodiment of the Joule cycle, whose characteristics are specified by the aforementioned references.
• the general application of Joule cycle is possible, that is to say its application as a refrigeration machine or as a heat pump.
• the mechanism of the present invention is possible to be used as a thermodynamic cycle embodying a mechanism for the conversion of thermal to mechanical energy as well as a thermodynamic cycle embodying a mechanism for the conversion of mechanical to thermal energy.
• the mechanism of the present invention can operate as a simple compressor, when the single active space is the space 34, while simultaneously the sides are open to the extent of the space 35.
• the same mechanism can operate as an expander, when the single active operation reffering to figure 7, is that of the expansion in the space 35, while the sides are open to the extent of the space 34.
• a fourth preffered embodiment of the present invention is schematically represented at figure 7, when the mechanism operates as a high temperature expander. In this case take effect the above mentioned concerning the simple expander.
• the scavenging system 37 whose task is the removal of the hot gases and the introduction of fresh air, which cools the vanes 8, the drum 9 and the cylinder 6. In this way an by the mediation of the ceramic materials 15,16 the achievement of expansion under very high temperatures is possible.
• the present invention operates according to the arrangement of figure 8.
• the whole arrangement consists of the side covers 47 and 48, which include all the elements of the covers 4 and 5 of the first preffered embodiment, as well as the elements of the cover 10.
• the right side cover 47 consists of the elements 2,4,9,11,12,13,14 and 15, while the left side cover consists of the elements 3,5,9,10,11-12,13,14,16.
• the side covers 47,48 are connected by the connecting rods 19 and the bolts 20 to the intermediate cover 49 (figure 9), which has inner ceramic lining 50 and cooling channel 51.
• the drum 6 extends to the whole area of the arrangement, that is to say to the area which is occupied by the ceramic lining 50.
• the vanes 8 extend to the whole area of the drum 6 and end up to the cylinders 9, without coming into mechanical contact with the ceramic lining 50.
• the scavenging arrangement is represented at figure 8 where the inlet air coming from the air pump 26 is lead through the opening 52 to the separating plate 53 and through the guide vanes 54,55 to the outlets 56,57 and to the compression space 34. Reffering to the application of the Otto or Diesel cycles take effect the same as in the first and second preffered embodiment, as far as it concerns the separating plate 28, the fuel inlet system 29, the position of the igniters 40,41 35and the position of the injectors 42,43. Schematically the whole arrangement operates according to the figure 10, where the schematically represented scavenging arrangement 37 is depicted at figure 8 and where all the rest procedures are the same as the aforesaid in the first and second preffered embodiment.
• the whole system operates also according to the schematic arrangement of the figure 1 where take effect the same things as in the figure 5, with the difference that the scavenging arrangement 37 is the one depicted at figure 8, while the outlet port 58 and inlet port 59, are positioned on the cover 49.
• This arrangement can operate as high temperature expander which is schematically depicted at figure 12
• the only active arrangements of figure 12 are the expansion in the space 35 and the scanenging system 37.
• the side covers which belong to the space 34 are free, so that the inlet air, introduced by means of the scanenging system 37, functions as cooling means.
• the leakage from the high pressure space to the low pressure space can not be of greater value than the one corresponding to the velocity v r .
• the corresponding velocity will have approximately 0,7 Mach.
• the rotation speed of the end of the vane 8 corresponds to the same Mach number, it is namely approximately 250 m/sec
• first and the second embodiment are conciderably more effective in the case low peripheral velocities of vanes 8 and that in these embodiments we have considerable limits of tolerances between vanes 8 and side covers 4,5.
• This preffered embodiment of the invention might need high peripheral velocities.
• the vane 8 ends up through shafts 60 to a bearing 61, which rolls on the cylinder 9, avoiding thus the sliding friction forces which are converted to rolling friction forces.
• the high peripheral velocities of the cylinder 9, when these are necessary for operational reasons, can be balanced by the arrangement of figure 15, where two arms 62, are fixed on the cover 10, wherein bearings 64 are supported, the shafts of the freely rotated wheels 63, which support the free rotation of the cylinder 9.
• the ball bearings 11,12 can be substituted by a needle bearing system.
• a ring of soft metal 65 (figure 16) must be placed on the cover 10, on which the cylinder 9 rotates with the assistance of a lubrication system through which the oil flows in the gap 66.
• the lubrication system and the type of the soft metal must be specified according to the cited references relative to lubrication.
• the present invention operates as a pump, as it is illustrated at the figures 17,18,19,20.
• the cylinder 9 rolls inside the cylinder 67 playing the role of a ball bearing according to one preffered embodiment.
• the water inlet takes place through the space 68 and the outlet through the space 69.
• the side covers 70, 71 play the role of the side covers 4,5 and they are fixed on the cylinder 67 by the bolts 72.
• the eccentric shaft is driven by the centralized shaft 73 by the mediation of eccentric transmission couplings 74 and 75.
• the pump operates with double suction, which is effected through the plate 76 and the inlet ports 77 and 78, which externally have a cloth filter 79 and a grid 80 for the detainment of the sand in the case that the pump is used as a deep well pump.
• the pump outlet there is a diverging nozzle 81 bearing recovery vanes 82, which serves the balancing of the losses due to the high dynamic pressure.
• the internal cylinder 9 is sealed with respect to the cylinder 67 by the use of sealing O-rings 83.
• This embodiment can be also applied on the basis of the arrangement of figure 16.
• soft metal 65 we use rubber material while the lubricating fluid is the water itself.
• water lubricated material which covers both elements 9 and 10.
• this material can be ertalon (commercial name).
• the sixth embodiment constitutes a possitive displacement pump which has almost a constant efficiency for a wide range of flow rates. This is an important advantage for the ground water pumps since the centerf ugal ground water pumps have high efficiency only in a small range of flow rates. In the case of high peripheral velocities, driving vanes in the suctions of this embodiment are placed so that the pressure losses are minimized. An improvement of this embodiment is shown in fig.20.
• this invention can be used in a high pressure pumping system. This system is described in figure 21.
• the auxilliary centrifugal pump 93 sucks fluid from the tank 95 and feeds the pump of the present invention with the help of two convergent nozzles 88 and 89. These nozzles have driving vanes which are designed according to the existing bibliography, so that the peripheral velocities of vanes 8 and the flow rate of the proposed pump are taken into account.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Supercharger (AREA)

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Publications (1)

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Cited By (2)

Citations (15)

• 1997
  • 1997-06-12 GR GR970100237A patent/GR970100237A/el unknown
• 1998
  • 1998-06-11 WO PCT/GR1998/000015 patent/WO1998057038A1/en active Application Filing

Patent Citations (30)

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