WO2014072852A1 - Moteur à gaz comprimé - Google Patents

Moteur à gaz comprimé Download PDF

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Publication number
WO2014072852A1
WO2014072852A1 PCT/IB2013/059273 IB2013059273W WO2014072852A1 WO 2014072852 A1 WO2014072852 A1 WO 2014072852A1 IB 2013059273 W IB2013059273 W IB 2013059273W WO 2014072852 A1 WO2014072852 A1 WO 2014072852A1
Authority
WO
WIPO (PCT)
Prior art keywords
engine
compressed gas
gas
previous
engine according
Prior art date
Application number
PCT/IB2013/059273
Other languages
English (en)
Inventor
Valentino Pietro SACELLINI
Original Assignee
Sacellini Valentino Pietro
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 Sacellini Valentino Pietro filed Critical Sacellini Valentino Pietro
Publication of WO2014072852A1 publication Critical patent/WO2014072852A1/fr

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Classifications

    • 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
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0035—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F01B3/0038—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to main shaft axis
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/18—Structural association of electric generators with mechanical driving motors, e.g. with turbines
    • H02K7/1807—Rotary generators
    • H02K7/1815—Rotary generators structurally associated with reciprocating piston engines

Definitions

  • the present invention relates to a compressed gas engine, and an apparatus comprising such engine.
  • the present invention thus falls within such context, setting but to provide an engine functioning with compressed gas, in particular compressed air or vapour (for example water vapour) , suitable therefore to prevent it from creating harmful combustion products, and the functioning of which does not entail global warming nor worsening of the greenhouse effect.
  • compressed gas in particular compressed air or vapour (for example water vapour)
  • vapour for example water vapour
  • FIG. 1 shows a schematic diagram of the apparatus of the present invention, according to a possible embodiment
  • FIG. 1 shows a cross-sectional view of the engine usable in the apparatus in figure 1, according to one implementation of the invention
  • figure 3 shows a view from above of the engine in figure 2, in which the head has been removed;
  • FIG. 4 is a schematic diagram of the contact surfaces between the engine body and the propulsion rotor at the bevelled surface of the former;
  • FIG. 5 shows a variant of a rotation pin, usable as an alternative to the pin shown in figure 2; and [0013] - figure 6 shows a cross-section along the plane VI- VI of figure 5 of the rotation pin and of the radially innermost portion of the rotating drum.
  • reference numeral 2 globally denotes a compressed gas engine .
  • Such engine 2 comprises an engine body 10 and a propulsion rotor 12 which circumscribes, together with the engine body 10, two or more expansion chambers 14, 16, 18, 20 for the compressed gas. Preferably three or more (for example four or more) of the aforesaid chambers are provided.
  • the rotor 12 and the expansion chambers 14, 16, 18, 20 are susceptible to a rotation in relation to the engine body 10 around a primary rotation axis X under the expansion effect of the compressed gas.
  • the drawings show an engine 2 with four expansion chambers angularly equidistant, although other variants may provide for a greater or smaller number of such chambers (and of corresponding pistons) .
  • Embodiment variants with a non-equidistant distribution in a circumferential direction (an irregular pitch) of the expansion chambers may also be hypothesised.
  • the expansion of the gas acts on the engine body 10, and in particular on a head 44 thereof, and on the propulsion rotor 12 to promote its rotation.
  • such rotor is configured to move other kinematisms (,not shown) mechanically suitable for connection to the latter by means of transmission means 74.
  • the movement of the propulsion rotor 12 may be used to move a transmission shaft of a motor vehicle, engageable with said means 74.
  • a power axis Y of the engine 2 may be inclined in relation to the primary rotation axis X, for example at an angle of 140° to 165°, preferably approximately 150°-160°, in particular 155°.
  • the engine body 10 comprises a substantially cylindrical wall 70 which extends around the primary rotation axis X.
  • Said cylindrical wall 70 delimits an abutment surface 72 with the propulsion rotor 12, preferably bevel-shaped.
  • the engine body 10 further defines an inner chamber 76, wherein the propulsion rotor 12 is at least partially housed.
  • the abutment surface 72 circumscribes the access aperture to the inner chamber 76.
  • the propulsion rotor 12 is axially constrained to the engine body 10 by means of a retention flange 102.
  • such flange is in abutment with the rotor ⁇ 12 so that the latter is free to rotate, and is retained to the engine body by one or more tie-rods 104, 104' which axially compact the engine.
  • tie-rods 104, 104' which axially compact the engine.
  • the engine 2 further comprises at least one entrance aperture 22 of the compressed gas and at least one exit aperture 24 of the expanded gas, fluidically connected upstream and downstream of the expansion chambers 14, 16, 18, 20 in the transit direction T of the gas, schematically shown by an arrow in figures 1 and 3.
  • a single entrance aperture 22 and a single exit aperture 24 are made in the engine body 10.
  • the entrance aperture is made at the head 44, while a further variant provides that the exit aperture 24 crosses the cylindrical wall 70.
  • a further embodiment (not shown) provides, conversely, that the entrance aperture is made in the cylindrical wall, while the exit aperture is made in the head, as happens for example in the Newcomen steam engine.
  • the direction of transit of compressed gas would obviously be opposite to that shown in the figures, in that the gas would act from the lower part of the pistons, according to the picture shown in figure 2.
  • the engine 2 comprises interception means 48 to regulate the flow of compressed gas to the expansion chambers.
  • the interception means 48 comprise at least one (solenoid) valve or at least one gate valve.
  • such means 48 can be positioned at the entrance aperture 22.
  • the interception means are thus suitable to vary the through cross-section of the compressed gas through the entrance aperture.
  • the head 10 of the engine body 44 delimits a proximal storage 46 of compressed gas communicating with the expansion chamber 14, 16, 18, 20; this way, the flow of compressed gas coming out of the proximal storage 46 is immediately made available to the expansion chambers, without the dead time which would be needed in the case of a storage or tank 8, 8' positioned more distally to the engine 2.
  • the interception means 48 are at least partially housed in the proximal storage 46, for example as shown by the dotted line in figure 2, in particular in abutment with an end wall 100 which delimits the head 44 in the direction of the expansion chambers.
  • the interception means 48 are positioned downstream of the proximal storage 46, and can be commanded to control the flow of gas coming out therefrom.
  • the engine 2 comprises heating means (for example an electric resistor) in thermal communication with the aforesaid storage 46 to increase the calorific value - thus the expansion - of the compressed gas upon its introduction into the expansion chambers 14, 16, 18, 20.
  • heating means for example an electric resistor
  • the propulsion rotor 12 comprises a plurality of pistons 26, 28, 30, 32 movable (preferably translatable) inside the expansion chambers 14, 16, 18, 20 to vary the volume thereof.
  • each piston 26, 28, 30, 32 is movable in the respective expansion chamber 14, 16, 18, 20 between a position of minimum volume VI of the chamber 14, 16, 18, 20 wherein the pressure of the compressed gas is maximum, and a position of maximum volume V2 of the chamber wherein said pressure is minimum and wherein the gas is expanded.
  • the expansion of the compressed gas in the expansion chambers causes a distancing of the pistons (for example in relation to the head 44 ' or in relation to the end wall 100 of the engine body) so that each of such chambers passes alternately from the minimum volume VI to the maximum volume V2.
  • the movement of the pistons produces a rotation of the propulsion rotor 12.
  • the pistons 26, 28, 30, 32 are further rotatable around the primary rotation axis X along a rotor trajectory R, for example circular or ellipsoidal, which intercepts the axis X at an angle A other than 90°.
  • a rotor trajectory R for example circular or ellipsoidal, which intercepts the axis X at an angle A other than 90°.
  • the representation in figure 1 shows an obtuse angle A while figure 2, substantially specular to the previous, identifies an acute angle A.
  • the piston 26 is initially placed in the position of minimum volume VI of the respective expansion chamber 14. Given that in such circumstance the pressure of "the compressed gas entering the chamber through the entrance aperture 22 is maximum, the piston is distanced under the thrust of the pressure accomplishing the movement (or preferably translation) in the expansion chamber, and rotating along the rotor trajectory R, for example in a circular direction (as shown schematically by the arrow in figure 3) . After going through a rotation of approximately 180°, such piston 26 will occupy the opposite position (which in the figures is that engaged by the piston 30) wherein the volume V2 of the chamber is maximum and where, by virtue of the expansion of the gas having taken place, the pressure is minimal.
  • the at least two pistons will have inverted their positions, so that at the piston marked by reference numeral 30 a new cycle of expansion of the gas as described may take place.
  • the frequency of entrance and of expansion of the compressed gas will take place with a reduced rate for example, for an engine with four pistons such as that shown, every 90° of rotation.
  • each piston 26, 28, 30, 32 is connected and extends towards the expansion chambers 14, 16, 18, 20 from a bottom surface 50 of the propulsion rotor 12. Said connection is preferably made by a cuff 52, 54 which receives a rod 56, 58 of the piston 26, 28, 30, 32 with a swivelling movement around several axes M, Z.
  • each piston is rotatable around a secondary rotation axis M (in the case in point substantially parallel to the primary rotation- axis X) and around a tertiary rotation axis Z, for example incident or orthogonal to the aforesaid secondary axis M.
  • the bottom surface 50 is destined for sliding contact with the abutment surface 72 of the cylindrical wall 70.
  • the interposition of roller means 78', 78" for example one or more roller bearings, may be provided for.
  • the cylindrical wall 70 has a variable thickness of wall around the primary rotation axis X.
  • such wall has a minimum wall thickness at the greater semi-axis 108 of the ellipsis/ovoid, while it has a maximum thickness at the smaller semi-axis 110.
  • the cylindrical wall 70 has a pair of opposite sickle-shaped portions 112, 112', preferably having their concavities facing towards the primary rotation axis X.
  • the centre of symmetry of such portions 112, 112' is positioned at the smaller semi-axis 110 of the ellipsis.
  • each cuff 52, 54 delimits an articulation basin 80 suitable for housing at least partially an end portion of the rod 56, 58, the latter for example of a generally spherical shape.
  • the propulsion rotor 12 comprises a rotating drum 34, partially housed in the engine body 10, in particular partially housed in the inner chamber 76 which separates the expansion chambers 14, 16, 18, 20 and guides the movement of the pistons 26, 28, 30, 32.
  • the rotating drum 34 may for example be seen from above in figure 3 where the head 44 has been removed from the engine.
  • the drum has a plurality of drum lobes 82, 84, 86, 88 at the various chambers. Between each pair of said drum lobes a housing 90, 92, 94, 96 may be provided for the at ' least partial housing of a magnetic element 68 (described below) .
  • the rotating drum 34 delimits an access opening 36, 38, 40, 42 of the compressed gas for each expansion chamber 14, 16, 18, 20; the openings are distanced from each other so that, in any angular position of the drum 34, a single access opening is aligned with the entrance aperture 22 identified by the engine body 10. This way, the compressed gas is released into a single expansion chamber at a time, so as to avoid unwanted pressure drops inside the pneumatic circuit of the engine.
  • ceramic rubbing surfaces may be foreseen.
  • the propulsion rotor 12 and/or the rotating drum 34 are guided in rotation by a rotation pin 60 connected centrally to the engine body 10, and in particular engaged with the head 44.
  • the rotation pin 60 which extends along the primary rotation axis may be fitted coaxially to the engine body 10 and/or to the rotating drum 34.
  • the pin 60 is traversed by at least one fluidic passage 62, 126, 64 to. place in communication the expansion chamber 14, 16, 18, 20 and the exit aperture 24 of the expanded gas.
  • each expansion chamber 18 communicates externally by means of the venting aperture 98 of the expanded gas, and each piston 26, 28, 30, 32 is configured to act as an interception component of the expanded gas towards the exit aperture 24.
  • the stroke of the pistons makes it possible to free the venting aperture 98 when the propulsion rotor 12 is in a specific angular position, thereby permitting the fluidic connection.
  • a check valve 128 may be provided for at the fluidic passage 62, 126, 64 to prevent the return of the expanded gas towards the expansion chamber which it has just left.
  • such valve may be at least partially housed inside the pin 60, and specifically inside the axial duct 126.
  • the rotation pin 60 is axially divided into a first portion 122 integral with the engine body 10 (for example joined in rotation) and in a second portion 124, rotatable in relation to the * first portion 122 and delimiting at least a part of the fluidic passage 62, 126, 64. [0055] Consequently, according to the previous variants, the rotation pin 60 or the second portion 124 preferably houses at least partially the check valve 128 to prevent the aforesaid return to the expansion chamber.
  • the rotation pin 60 has a spider cross-section so as to delimit a plurality of passages 126, and specifically to delimit a fluidic passage 126 for each expansion chamber.
  • one or more pistons may have a slot or a fall 106, facing towards the venting aperture 98, to anticipate the exit of the expanded gas.
  • the engine body comprises a plurality of coil windings 66 suitable for interacting with at least one magnetic element 68 joined in rotation to the propulsion rotor 12 to generate an electric current.
  • the engine body comprises a plurality of coil windings 66 suitable for interacting with at least one magnetic element 68 joined in rotation to the propulsion rotor 12 to generate an electric current.
  • four magnetic elements are provided for, each housed in a respective housing 90, 92, 94, 96 of the drum.
  • the aforesaid electric current may be used to power the heating means of the proximal storage 46.
  • the present invention also relates to an apparatus 1 comprising a compressed gas engine 2 according to any of the previous embodiments, electric-mechanical means of re-compression 4, 6 of the expanded gas and at least one collection tank 8, 8'.
  • the apparatus 1 comprises a pair of collection tanks 8, 8 ' , for example arranged in parallel for alternate or concurrent use.
  • a further embodiment provides that, by operating one or more second valves 118, 120 positioned downstream, the emptying of such tanks 8, 8' may also be regulated at will.
  • the electric-mechanical re-compression means are connected downstream to the exit aperture 24 (again with reference to the direction of transit T of the gas in the circuit) , and are preferably also powered by the electric current generated by the interaction of the coil windings 66 with the magnetic element 68.
  • the term "also" being taken to mean that, given the inevitable dispersion of energy, such current must necessarily be integrated by means of a supplementary external source.
  • the collection tank 8, 8' is suitable to feed the compressed gas to the engine 2, and is advantageously configured to receive compressed gas at least from the electric-mechanical re-compression means 4, 6.
  • such means 4, 6 may comprise an engine 6 operating a mechanical compressor 4.
  • the engine and compressor are positioned coaxially to the rotation axis of the shaft of said engine 6.
  • the re-compression means 4, 6 comprise an engine such as that illustrated according to any of the previous variants; however such engine will need to be modified in such as way as to cause a re-compression of the expanded gas entering therein, by means of a mechanical action of the pistons on the gas generated through a consumption of electricity, thereby obtaining the compressed gas.
  • the engine and method according to the present invention are suitable to completely eliminate the use of fossil fuels for the locomotion of vehicles or other means, and to prevent them from generating harmful products of combustion.
  • the apparatus described is highly integrated, in a perspective of optimising energy and consumption.
  • the engine and method according to the present invention are suitable to immediately make available the power required in specific functioning circumstances, thereby avoiding the dead times of gas transport.
  • the engine and method according to the present invention present an innovative swivelling system of the pistons which permits a freedom of movement with a reduced rate of wear.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

La présente invention porte sur un moteur à gaz comprimé (2), comprenant un corps de moteur (10), un rotor de propulsion (12) qui entoure, conjointement avec le corps de moteur (10), plusieurs chambres de détente (14, 16, 18, 20) pour le gaz comprimé, qui peuvent tourner par rapport au corps de moteur (10) ; ce rotor étant approprié pour être relié à des moyens de transmission (74). Le moteur comprend en outre au moins une ouverture d'entrée (22) du gaz comprimé et au moins une ouverture de sortie (24) du gaz comprimé, qui sont raccordées fluidiquement en amont et en aval des chambres de détente (14, 16, 18, 20) dans la direction de passage (T) du gaz ; et le rotor de propulsion (12) comprend une pluralité de pistons (26, 28, 30, 32) mobiles à l'intérieur des chambres de détente (14, 16, 18, 20) pour faire varier leur volume. Les pistons (26, 28, 30, 32) peuvent tourner autour de l'axe de rotation du rotor le long d'une trajectoire de rotor (R) qui coupe ledit axe à un angle (A) différent de 90°. L'invention porte en outre sur un appareil (1) comprenant un tel moteur.
PCT/IB2013/059273 2012-11-08 2013-10-10 Moteur à gaz comprimé WO2014072852A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT000159A ITBS20120159A1 (it) 2012-11-08 2012-11-08 Motore ad aria compressa
ITBS2012A000159 2012-11-08

Publications (1)

Publication Number Publication Date
WO2014072852A1 true WO2014072852A1 (fr) 2014-05-15

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PCT/IB2013/059273 WO2014072852A1 (fr) 2012-11-08 2013-10-10 Moteur à gaz comprimé

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IT (1) ITBS20120159A1 (fr)
WO (1) WO2014072852A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190609871A (en) * 1906-04-27 1907-02-14 Frederick Lamplough Improvements in or relating to Pneumatic Transmission of Power.
GB191021424A (en) * 1910-09-14 1911-05-25 Charles Richardson Pratt Improvements in Rotary Piston Pumps or Motors.
GB191014135A (en) * 1910-06-10 1911-05-25 Universal Speek Control Co Improvements in Apparatus for Transmitting Motion by Means of a Fluid, and to Pumps or Motors such as are used therefor.
FR436702A (fr) * 1911-10-09 1912-04-03 Charles Clifton Cowan Appareil producteur de force motrice
GB990679A (en) * 1960-07-06 1965-04-28 Citroen Sa Andre Improvements in driving systems for electric generators
WO1994011614A1 (fr) * 1992-11-12 1994-05-26 814405 Ontario Limited Vilebrequin
JP2005090447A (ja) * 2003-09-19 2005-04-07 Denso Corp 流体機械
WO2006090421A1 (fr) * 2005-02-23 2006-08-31 Orbitech Engineering S.R.L. Moteur à transmission desmodromique
CN2937546Y (zh) * 2006-08-15 2007-08-22 兰州理工大学 一种液压电机轴向柱塞泵
US20110243780A1 (en) * 2007-12-06 2011-10-06 Kuehne Manfred Axial piston machine

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB190609871A (en) * 1906-04-27 1907-02-14 Frederick Lamplough Improvements in or relating to Pneumatic Transmission of Power.
GB191014135A (en) * 1910-06-10 1911-05-25 Universal Speek Control Co Improvements in Apparatus for Transmitting Motion by Means of a Fluid, and to Pumps or Motors such as are used therefor.
GB191021424A (en) * 1910-09-14 1911-05-25 Charles Richardson Pratt Improvements in Rotary Piston Pumps or Motors.
FR436702A (fr) * 1911-10-09 1912-04-03 Charles Clifton Cowan Appareil producteur de force motrice
GB990679A (en) * 1960-07-06 1965-04-28 Citroen Sa Andre Improvements in driving systems for electric generators
WO1994011614A1 (fr) * 1992-11-12 1994-05-26 814405 Ontario Limited Vilebrequin
JP2005090447A (ja) * 2003-09-19 2005-04-07 Denso Corp 流体機械
WO2006090421A1 (fr) * 2005-02-23 2006-08-31 Orbitech Engineering S.R.L. Moteur à transmission desmodromique
CN2937546Y (zh) * 2006-08-15 2007-08-22 兰州理工大学 一种液压电机轴向柱塞泵
US20110243780A1 (en) * 2007-12-06 2011-10-06 Kuehne Manfred Axial piston machine

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