BE478902A - - Google Patents

Description

       

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  ENERGY RECOVERY DEVICES
The present invention relates to improvements to energy recovery devices of the type comprising a gas turbine with constant volume explosion. It relates more particularly to a new method and apparatus for the use of the energy of the exhaust gases produced by the combustion of successive charges of a combustible mixture in a chamber whose volume remains constant or substantially constant. during the exhaust of the burnt gases and the admission of the fresh gas charges,
In the practice of the method of the invention, using the new apparatus,

     the escape of burnt gases from the combustion chamber and the introduction of fresh charges into said chamber, taking place in such a way as to use the phenomena of exhaust-explosion and of admission-this, spiration and said chamber is ,. therefore, self-evacuating and self-sucking, so that it is not necessary to supply air or gas under pressure for the purpose of sweeping, or the introduction of the gases. The burnt gases leave the chamber as a mass at a high speed, and, as they move away from the chamber; dynamic energy

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 gas is lt-i.li ;, 0c .i.;,:. lr actuate a; turbine.

   Said turbine, which is one of c "'," "r: .ctr: Ti ;; tickG" del1', nvnï'1tiD1;, r: eGt c1i.n) osr: e with respect to 1. ". chamber and i;, #ir;; L <1 in.such way that 1 'in ¯.t¯a, ilF: slow of. color of the .. turbine by the impulse of Gas, not only does not harm t 1) 8.13,;. iJtJ; ', function:; n, t,' c: è. la, chô.1J.- bre pc; r.netta, nt to use the)] u: noJt1Gncs d ' .cna.lel: aent-: pln- sion and d * admission-aspiration, But on the contrary facilitates the:. 1tiliG; Üion of said phenomena? The Laibine rotor actioi1- n'- 'by the J: az can be used to perform work and, de. :, ilJL1, 1e sc a. <.:, ont, 1, eii ::.: au; e.; n 1 n <? yard; pressure beyond the turbine and =; <; ç> 1, o> .es then to carry out a work by their
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 relaxation.
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  In the: ¯w, pi: .rcils -anterior, recupcra.beurs of power 1. ttrroine a [; 8.2 il, constant volume ;, successive charaes of a combustible mixture are ', burned in a combustion chamber at constant volume and, after the combustion of each cl.i; zi "ue, the. chamber must t 0f.mc h: 1.lD.yrÍ.e of the L ';; 3. under pressure which remain behind after the exhaust and said cc li.;:.; ih 1 must be refilled with fresh nharre.

   In the i.nsta, 7¯la, tions, in which the Exhaust-explosion and the intake-suction are not used for the operation of the chambers, the expulsion of the residual U..z and the recharging of the 1 ..: chamber are carried out by the sweeping which exices to expel 1t.es.s' 1> rûlês the introduction of air or gas under pressure in the cllia.tnh-re at the appropriate time of each operating cycle; aen ". 1 Consequently, such installations require, for their operation, a fan or compressor for the compressed gaseous medium.

   The activation of such a fan or compressor is costly. R; hid.d, cr:, tīo .; the, power, which reduces the net flow of the installation. and,;,

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 e.nt9ut: s, ùiJ;, erbm.il: aageGdê 'j (a.:c {lHlbre of residual burnt gases, using pressurized gas or air used to recharge the chamber results in a mixture gases burnt with the fresh charge and by pollution of the latter, hence a loss of the power liable to be released from the charge contained in the interior of the combustion chamber, during the combustion of said charge .



   The operation of two-stroke internal combustion engines is analogous to that of constant volume gas turbines in that the piston does not substantially move during the period in which the exhaust and exhaust take place. mission, so that the cylinder can. be considered to have a practically constant volume. Moreover, such engines in which the exhaust-explosion and the intake-suction are not used, require compressed air or gas for the scanning and recharging of the cylinder, hence a corresponding reduction. of the net flow rate, as a result of the consumption of power to compress the medium and as a result of pollution of the fresh feeds by residual gases during the sweeping process.

   In operation, both constant-volume gas turbines and two-stroke internal combustion engines in which pressurized air or gas is used for scavenging and recharging, the gas pressure at the The interior of the exhaust system determines the pressure of the compressed medium and the power necessary to effect this compression.

   Even when the gas pressure in the exhaust system is relatively low, for example of the order of a few millimeters of mercury, the power loss for the fan drive is appreciable and, when

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 the pressure of the gases in the exhaust system is increased, the loss of power also increases and the sweeping operation becomes more difficult and unsatisfactory.
In a number of prior US patents of the Applicant, e.g., Nos. 2,102,599, 2,123,569, 2,130,721, 2,131,959;

  and 2,144,065. A two-stroke internal combustion engine has been described, designed and operated in such a way that it can utilize the exhaust-explosion and intake-suction phenomena and the same data also apply to. the. design and commissioning of the combustion chamber of an explosion gas turbine.

   In an engine operated so as to use the explosion exhaust, as disclosed, in the patents mentioned above, immediately after opening the exhaust port in the. The burnt gases which are inside the cylinder react against the walls of said cylinder in such a way that their mass is accelerated in a direction tending to cause them to exit. through the exhaust ports. The speed acquired by the mass of the burnt gases then increases until the moment of. mass eventually becomes so large that the said mass ceases to react against the walls of the cylinder.

   At this time, the acceleration period of the. mass of burnt gases touches .. sa. end and the mass continues to move out and away from the cylinder at a high speed by virtue of its moment. During the (acceleration period) the mass of the burnt gases in its explosion-exhaust entrains and accelerates the gases. inert materials which are in its path in the exhaust pipe near the exhaust port

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 of the cylinder and the mass of inert gases thus driven and accelerated is integrated into the mass of burnt gases which produces the acceleration.

   The combined mass of inert and burnt gases thus accelerated during the burnt gas acceleration period which can, for simplicity, be represented by suppression "exhaust gas mass", and which consists of the burnt gases and inert gases which are between said burnt gases and the acceleration front moving through said inert gases, reaches its maximum speed and moment in the exhaust-explosion process when the burnt gases begin to leave the cylinder under mass form, which occurs when the period of acceleration of the mass of the exhaust gases is completed by the cessation of the reaction of the flue gases against the cylinder walls.

   Consequently, at the end of the acceleration period the mass of the exhaust gases has its maximum dynamic energy.



   The speed of propagation of the acceleration front through the inert gases in the exhaust pipe of the gases near their exhaust port during the aeration of the flue gases is of the order of 650 to 1300 meters per second and can be much higher. The speed with which the accelerating front, ration moves depends on the intensity of the explosion of the exhaust gases out of the chamber, which in turn depends on the amount of energy released by the combustion of the mixture, energy acquired by the burnt gases.

   The intensity of the explosion also depends on the smallness of the time interval during which a surface

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 this sufficiently la.rte of 1 (oriiice; 'd'Éch; àppei, ient is open to allow the escapeitenq-expl, osion, and the volume of the mass of inert gases which must be accelerated shml tal10-ment with the mass of flue gas The speed of displacement of the mass of the exhaust gas varies depending on the following factors.
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 airlocks mentioned and, in practice, from 325 ours to more than thousand meters per second. The position of the accelerating front which moves through the inert gases can be determined using a cathode beam oscillograph or by other suitable means.



   When the mass of exhaust gas moves through the exhaust gas tube of the engine after the end of the burnt gas acceleration period, said mass drives, compresses and displaces the mass of inert gases. what
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 encounter on its paroonrs, and the velocity and dynamic energy of the mass of the exhaust gates steadily diminish as a result of the work thus done. A pressure is developed internally in the mass. mobile of the exhaust gases and of the inert gases on which said mass and; in this front, the dynamic enlargement of the mass fies cs-z of the exhaust is transformed into potential pressure energy u ze; zse .

   When the mass of the exhaust cells has lost all of its dynamic energy, an elastic pressure front is formed and the front immediately explodes, which has pomreefiEè'LdGe to reject the, mass of gases, comprising the gases burns which contributed to the formation of said forehead; pressure
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 vsrs the cylinder. The mass of exhaust ut: .z can, as a consequence}, be considered as bouncing.

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 cylinders on the exploding pressure front. If the exhaust port is closed before the mass of the discharged gases reaches the cylinder, said gases cannot penetrate into said cylinder and, consequently, cannot adversely affect its contents.

   The displacement in the form of mass of the gases of the cylinder by exhaust-explosion therefore leaves the cylinder empty so that it is not necessary, as in engines not using the exhaust-explosion, to supply the cylinder air or gas under pressure for the layage tank or gas expulsion.



   When the burnt gases cease to react against the walls of the cylinder, the acceleration of the gases disappears, and the gases exit the cylinder at a high speed under the form of mass by virtue of the moment acquired, the mass of gas which is moves outward leaves behind a void in the cylinder.
In charging the cylinder of an internal combustion engine carried out in such a way as to use the phenomenon of aspiration, the fresh gases or combustible mixture virtually explode from outside the cylinder to the vacuum left in said cylinder as. described above.

   The use of fresh gas aspiration is completed by opening the intake port to the extent and within the proper time frame approximately when the burnt gases leave the cylinder as a mass and, when the cylinder has been thus filled by suction, the inlet port is closed, either before or after the blocking of the burst port, depending on the type of engine, and the cylinder load.

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 is thus accomplished.



   In order to accomplish the exhaust-explosion in which the burnt gases are thrown as a mass out of the cylinder at a high speed, the surface of the exhaust port open as the gases leave the cylinder as a mass, must be suitably proportioned to the cross section of the cylinder, as set forth in the above mentioned patents.

   In some insta.l- lations the open area of the exhaust port may be equal to or even less than a quarter of the cross section, the of the. combustion chamber.The maximum effective opening area of the exhaust port is eggle to the section of the cylinder, but in practice it is sufficient to open said orifice to half or a little more than the section of the cylinder. me out of the total section.



   The time required for the opening of the exhaust orifice to the extent defined above varies according to the installations. If the. mass of the exhaust gases, is accelerated and, consequently, acquires its dynamic energy in the space of 1/130 of a second, the moment of the trap is sufficient to produce $ ne, self-evacuation of the cylinder and is sufficient also to ensure satisfactory intake-suction at atmospheric pressure and without the aid of a fan or the like. In practice, satisfactory self-evacuation of the cylinder is obtained by exhaust-explosion. ,

   when the mass of the burnt gases is accelerated and begins to move by the sole virtue of its moment in the space of 1/300 of a second, but a shorter acceleration interval, for example of the order of 1 / 430 of a second increases the moment of

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 the mass. Perfect use of the exhaust-blast process is obtained in a suitably designed cylinder, when the opening of an exhaust port having a section equal to approximately half the cross section of the cylinder Carried out during the shorter of the above-mentioned time intervals.



   The phenomenon of admission-suction is of a nature analogous to that of exhaust-explosion in that, in both of the aforesaid phenomena, a medium at a given pressure fills by explosion a space which contains another; ni- place at lower pressure. In the exhaust-explosion the burnt gases inside the cylinder have an initial pressure, higher than the inert gases inside the exhaust -tube, while in the intake-suction, air or the combustible mixture outside the cylinder are at atmospheric pressure or at a pressure higher than atmospheric pressure and they fill the vacuum existing inside the cylinder.

   Due to the similarity between the two phenomena, it is necessary, in order to use the inlet-suction in a satisfactory manner for recharging the cylinder, to open the inlet port to an extent and to a time interval having approximately the same order of magnitude as above established with regard to the exhaust port., '
Although fresh charges can be introduced, into a combustion chamber or into the cylinder of an internal combustion engine operating in a µ-mode. use the explosion-exhaust and intake-suction ,. with pressure

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 a.tmosnhéidue said charges can 4bcaleinent if it is ct: ire, be at a pressure greater than. the pressure 8, t1.lOS- pherique.

   In this last case; the chamber or cylinder (te: theire.,. to- v <cu trice and o.uto-asl) iatricep and the higher pressure of the loads SG # 't especially lz ct.alnenter the: niverw of pros- si.on through the whole or system. The eJ1, Z burn which is the space of r :: OLÜ1Listic.n under faith of nn.3 :: Jn hune vi-;:; '3 ;; 80 11;), 1 istique then have a ylus, 'Jr = LnC3e 8np.rcie dynamic and the in :: t, ll.tion works i <.ve <; a <rate) lLlc lev6.



  ') c, .Yls African patent application n L) 68.1 <JC' du de! ':' -, 1., ii <J¯ea .: filed 1. 1.5 April 1, Eé> 1w il il é1, (; describes a recu11é i,; i, -teai of power comprising a turbine at GD.Z in. volume
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 constant and comprising a combustion chamber in which
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 are burned successive C1l.F: rk; eS of a combustible mixture. ' The cW.LÙ1 1'e operates in such a way as to use 1 9 'c: clla,;, elnent-explosion and the intake-aspiration and exhaust blLZ expelled from said chamber passing through a tube rl' (ClJ. D.ll1) emcnt which leads them ç. a relaxation room.

   The tube is of such a shape and cross-section that the mass of the exhaust cells leaving the chamber moves the inert j;> z li within the tube towards the chamber. forward a considerable distance through said tube before a pressure front this backflow develops and explodes.
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  One of the two exhaust or intake ports is formed
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 before the [;, 1Z discharged by the pressure front reaches the exhaust port and, in this way, the L:, cz, are C] 1Lêw.Gc.sins under pressure in the tube and in the deLcnte chamber and their trigger can be used to perform an A

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 job. Accet effect, the expansion chamber is read again at the inlet of a turbine and the stored gases actuate the rotor of said turbine before being evacuated.



   In an installation similar to that described in the above-mentioned application, it is advantageous to obtain a maximum acceleration of the mass of the exhaust gases so that said mass can acquire a speed and an energy maximum dynamics.

   Any decrease in the rate of explosion energy as a result of the use of part of the energy in acceleration of the mass of the exhaust gases results in a decrease in the rate of mass. flue gas leaves the chamber) which interferes with the proper self-evacuation of the, says. ::

       chamber and its recharging by the sole action of the gases, To avoid such a reduction in the rate of explosive energy capable of accelerating a mass of exhaust gas, it is advantageous to reduce the mass of inert gases in the exhaust tube , in the vicinity of the exhaust port, when a mass of burnt gas inside the chamber initiates its exhaust-explosion.



   However, in the installation described in the above-mentioned application, in which the exhaust gas expansion stored under pressure in the gas exhaust pipe and in the expansion chamber, is used to actuate a turbine, it is advantageous to increase the pressure of the stored gases so as to increase the flow rate of said turbine. Such an increase in the pressure of the stored gases in turn increases the volume of the mass of inert gases hindering the movement of the burnt gases.

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 during their acceleration l ±, by:;, ii [, <i, di;, iin ;;, e 1.F. 'itese and the on of said se.

   They have: vi.r1Ci1t, therefore,, 1 L; e, Such e 1 o; = 1: .-, i 1 1. i. i r, n, the p 1; -; s sq 1: -. dc: s E; :. z e; <iis: .i zo, -> 1 # 1] ;; 'n <; must; 1118 exceed a value of tcri.lincc the advance ". end gJe 1 <-> 1ìts C / Jz do not take ne o p¯> ii; e ;. r.:. what lu hiaosc d.ns CI '<i' écha.pj = e;.; Ient .x. # Çjaié # e lUle 1.c <,>] 1 <iii; .iion and a knot suitable to ensure anc a'ii.lisi: .tioii or'.tisfr'isante de l'c'- ch ;;. jppe; iieri-t-erplonion and 1 ': ->. i; -. tissioii-a, spi.i # .. Li.an. He ect 8 (; 1.,. 18- 'Obviously deny that these conditions Li.> iLcnt the flow rate of the turbine ..



  L # i. present invention n. for object to establish a device r; 'cupc'rateu.r power C011lJrennnt iUle -le combustion constant volume or pi.:;.tīqai:i>:Fùiif. contant, from which there is a drizzle of loads S suc ce s i vemen t of year, Jùàli.nge: oài.: iba # t'ibào.
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  : L '! R:;} lil .-:') lJ8jl1ent 'eJ) losi.Ofl des É C'. burns is.-1:. il lsô for bc.la:.'Gr Lr C '':,:. ilJrP .. and L '::: rl; is:;.'; O! 1 -; 'J' '' l, i.) 'E.t'ion i, i is used for the, recJl'r :::: er. In the new device x'écuAifra; .teu: c de IJu, ÍfJs :: J1; ce l'r) nsYClc dyn.l, 111Í1.U8 is i, ll "CE. ' des [,;. 1,2 r1'c} ln,) pCL1Cllt lOr FWI.l 'J.1 ..;

   e <iÔjii - ;;.; inot outward and E'tl'F3 'C¯U iÛtlLLil' (i the C71t.i71i) rG- '' oZ. a velocity bZJli.sti, q, -. 1.C; L through a nt ab escape of the y, <, verc the point where a pressure front of rcfoJ.lenlent develops and explodes, the oClL Lltilisel 'l 'nerie 6ynamigu.e des, 1, Z of exhaust projected by explosion, a turbine zur, impal- sine this new concentration is iiF3ti ,, Ile on the path dJ5 C'; 'Z, and, when 1 <-, said {I.7. pass through the turbine at an Ëra'nde vi +, r; 5 -e, they actuate the rotor of said turbine at a high peripheral speed.

   Za. turbine is installed between the exhaust port of the chamber and the explosion point of the discharge pressure front and, in such a way 1-1 I that we obtain

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 For optimum results, the turbine rotor is approximately located at the point reached by the acceleration front which moves through the inert gases in the gas exhaust tube at the moment when the burnt gases cease to react against the walls. chamber and begin to leave it as a mass by explosion.

   As a result, the rotor begins to receive each impulse of the inert gases which have been accelerated by the burnt gases, at the moment when the mass of said burnt gases has acquired its maximum speed and moment and ceases to react 'against the walls of the bedroom. At the moment which has just been defined, the acceleration of the burnt gases is completed and the gases have acquired their speed and the maximum dynamic energy and, if the rotor is placed in the position indicated, the mass of the exhaust gases, composed of the burnt gases and the inert gases of the exhaust tube, accelerated by the said burnt gases during their acceleration period, passes entirely through the rotor and actuates it at full dynamic energy without reaction against the walls of the chamber.



   The turbine of the new power recovery device is of a new construction and constitutes one of the parts of the invention. Said turbine is constructed in such a way that the masses of exhaust gas pass through it successively and the point where the discharge pressure front of the gases explodes is situated well beyond said turbine. In this way, the latter only uses part of the dynamic energy of the gases which pass through it and said gases retain sufficient dynamic energy to enable them to push the inert gases out of the outlet of the gasket.

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 turbine to a reservoir connected to the said outlet either directly or via a suitable tube.

   The discharge pressure front then explodes internally with the gases at a point situated well beyond the outlet of the turbine and, either in the reservoir or in the tube which leads there. If desired, however, the gases from the turbine can be vented either directly or through a tube, in which case the explosion point of the discharge near-ion front is located above. beyond the outlet of the turbine and either into the tube or to the free air beyond the tube.



   The impulse turbine of the new power recovery device prevents the. mass of the gases discharged by the pressure front and the gases stored under pressure beyond the turbine to pass back through said turbine in the opposite direction. For this purpose, the turbine is constructed and arranged so as to develop centrifugal forces in the masses of gas which pass through it, said forces being opposed to the.

   pressure of the gases enclosed internally to the exhaust tank and to the tube connecting the outlet of the turbine to the reservoir and prevents said gases from being discharged or from expanding when passing through the turbine in the opposite direction towards the exhaust tube. pement leading to the combustion chamber. In order to develop (such centrific forces thanks to the high speed of rotation of the rotor of the turbine, the inlet chamber which leads to said rotor is disposed approximately in the center of rotation of the latter and the passages at through the vanes extend radinally towards the outlet of the rotor.

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   The turbine can also be arranged such that the blades of the rotor have an axial deflection action which prevents the discharged gases or those which are stored under pressure inside the tank and to the tube connecting said tank to the outlet of the turbine, from passing through. the. turbine in reverse direction towards the gas exhaust pipe leading to the chamber. For this purpose, the blades can be arranged relatively closely spaced from each other in one or more rows with a suitable destator device and said blades have a suitable curvature and angle, so as to develop axial forces or of deflection in the masses of gas passing through the turbine, forces which are usable for the mentioned purpose.

   In order to maintain the stored gases beyond the turbine, centrifugal forces can be used as well as the axial deflection forces developed by the rotation of the rotor.



   The rotor of the turbine, maintained at a high speed of rotation by the masses of exhaust gases which act on it successively by impulse, plays a further role in that it operates between successive impulses so as to produce an effect suction on the inlet pipe when the exhaust port is blocked As a result of this effect, the intake gases which have entered the exhaust pipe during the period when the exhaust ports 'and intake are opened simultaneously, are sucked through the turbine after each exhaust-explosion, .and the mass of inert gases existing in the tube is reduced and, therefore, offers less resistance to the exhaust. next explosion.



  The mass of the exhaust gases leaving the chamber during

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 said next exhaust-explosion therefore acquires greater speed. Increasing the velocity of the mass of burnt gases leaving the chamber improves the self-evacuating property, and the. following recharge by intake-suction is correspondingly increased.

   Due to the easier acceleration of the burnt gases and the greater efficiency of the. transformation of the potential energy of the fuel mixture into dynamic energy of the flue gases according to the conditions described; the dynamic energy available to operate the turbine, developing the explosive discharge pressure front and compressing the stored gases is increased, as a lesser proportion of said energy is transmitted to the inert gases in the exhaust pipe of the before the mass of the exhaust gases acts on the turbine rotor.



   The action of the turbine rotor to. High speed of rotation by preventing the return of the exhaust gases through the turbine to the exhaust pipe connecting the turbine to the exhaust port, leaves available a time interval during which the exhaust port the inlet-suction of the new charge can be closed without risk of harm. During the intake period in which the exhaust and intake ports are both open, part of the fresh gas passes through the combustion chamber and enters the exhaust pipe at the rest of the. mass of the exhaust gases going vt, rs the impulse turbine.

   When the chamber is filled with a load under pressure so as to increase the pressure level across the entire power recovery device, the gases

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 The charge entering the exhaust gas tube would, if left there, provide appreciable resistance to the acceleration of the next mass of burnt gases within the chamber. However, the rotor of the turbine sucks said gases out of the gas exhaust tube, thus reducing the volume of inert gases in said tube and, consequently, reducing the resistance offered by said mass.

   Due to the vacuum left in the exhaust tube behind each mass of exhaust gas passing through it and due to the suction effect of the rotor of the turbine, it is desirable to plug the ori - inlet pipe after the exhaust port, so that part of the fresh charge cannot be sucked out of the chamber by suction from the exhaust port opened after closing the intake port.



  However, the chamber can be overloaded with fresh gas, using the intake device and practicing the method set forth in Applicant's US Pat. No. 2,281,185.



   As stated in the prior patents mentioned above, it is advantageous in the implementation. action of a combustion chamber using the exhaust-explosion phenomenon to reduce the masses of inert gases located on the path. burnt gases during the period during which said burnt gases undergo their acceleration, so that said acceleration can approach its maximum.

   In such a way that the masses of inert gases can provide a minimum resistance to the outward displacement of the burnt gases in mass form from the combustion chamber.

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 tion, resistance measured per unit length of said path the gas exhaust tube must not be of too large a section, otherwise this tube would contain a volume (the inert gases too large and the said gases would offer too high a resistance On the other hand, the tube must not be of too small a section either, otherwise it would restrict the pitch of the gas mass which passes through it.

   The best results are obtained by giving the tube a cross section at its end adjacent to the exhaust port substantially equal to the total area of said open port at the time when the burnt gases leave the chamber as a gas. mass. Further, the section of the tube should have approximately the same shape as that of the exhaust port and the inner surface of the tube should be smooth and preferably polished.

   The cross-section may increase slightly) either imperceptibly) or by degrees towards its end connected to the turbine and the tube is preferably straight, although it may be slightly curved provided it does not exhibit the mass of gases no surface capable of pushing back said mass or of hindering the movement of the gases away from said chamber such that the pressure front of the internal discharge of the gases would explode at a point closer to the chamber.

   A tube which fulfills these requirements can be regarded as offering a "free passage II to the masses of exhaust gases, since the only resistance which said masses encounter on their way through such a tube. is that offered by the inert gases inside said tube and that the latter contains the minimum tolerable volume of such inert gases per unit of;

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 wretchedness.
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 ':.: Jjaàe'] g..DOtiV #]; i!: E: rz9'n;:, lla.:hanlnre, d, a: t1tré, .1he passage of gae between the blades of the rotor, and the outlet are designed so as to form an extension of the exhaust tube and to ensure free passage of gases through the turbine.

   For this purpose, the cross sections of the inlet, the passage of gases through the rotor blades and the outlet are substantially equal to the cross section of the tube.
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 exhaust measured at its end connected to the: inlet of the turbine. Further, the rotor blades of the turbine and the walls of the inlet and outlet ports are designed in such a way that they do not present any surface on which gases which pass through the turbine could bounce back to the chamber.

   With such a device, the volume of inert gases displaced by the masses of exhaust gas per unit path of the latter through the tube and the turbine is practically constant, the inert gases offering almost minimum resistance to their displacement by the turbine. mass of the exhaust gases and the point of explosion of the discharge pressure front being located beyond the outlet of the turbine.



   The tank in which the exhaust gases are stored under pressure can be connected directly to the output of the impulse turbine, in which case '-the rotor must be installed inside the tank and the pressure front discharge internally explodes with gases contained in the tank beyond the outlet of the rotor. If preferred, the outlet of the turbine can be connected to the exhaust gas tank by a passage and, in this case, the discharge front can explode inside either the passage must of the tank.

   Such a passage connected to the outlet of the turbine does not

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 must not be designed so as to contain a greater volume of inert gases situated on the path of the masses of Exhaust gas which pass through it, and must, consequently, have a cross section substantially equal to the respective transverse sections of the inlet of the turbine, from the passage to. through the vanes ;, and the outlet of the, turbine.

   By analogy, the passage of the exhaust gases is preferably rectilinear, but it can be curved on condition that it does not present to the gases which pass through it any surface on which said gases could rebound towards the turbine or which could. Impede their movement through the passage which would cause the discharge pressure front to form internally at the passage through the rotor or at the outlet chamber of said rotor.



   One of the essential characteristics of the new installation is that the discharge pressure front explodes at such a dead point well beyond the turbine and that the exhaust pipe of gases from the combustion chamber of said cylinder , the inlet of the turbine, the passage through the rotor, the outlet of the turbine and the passage of the exhaust gases from said outlet are therefore all designed so as to allow free passage masses of exhaust gas.

   To this end, as already pointed out the exhaust gas pipe and the other elements mentioned above are all designed in such a way as to allow the displacement of the masses of exhaust gases through these different elements. with a minimum resistance offered by the inert gases on their path per unit length of this path.



   According to one of the embodiments of the invention, the turbine

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 pulse driven by the dynamic energy of the exhaust gas is used to drive a machine, such as a fan, an electric generator, etc. The gases collected in the reservoir beyond the impulse turbine are then used to actuate by their expansion a device, such as a turbine, and the second turbine can in turn be used to drive a fan, gen- erally. rator, or other machine.

   However, the impulse turbine can only be employed, if desired, for the purpose of storing and enclosing the exhaust gases under a selected pressure in a reservoir located beyond the turbine and for suck the inlet gases out of the exhaust tube between successive passages of the masses of exhaust gas. In the latter case, only a small fraction of the total dynamic energy of the exhaust gases leaving the combustion chamber is used to drive the impulse turbine and most of said dynamic energy sett to increase the pressure of the stored gases.

   The rotor blades of such an impulse turbine are arranged in such a way that the rotor is driven at a high peripheral speed by the impulse of the gases passing through it and the peripheral speed of the rotor is sufficiently high. to develop forces opposing the static pressure of enclosed gases -
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 beyond said rotor as well as the pressure; dynam31q'ùè'- gases discharged by the pressure front towards said rotor.



   In an installation in which the gases which have transmitted their dynamic energy to the rotor of the turbine at

 <Desc / Clms Page number 22>

 pulse are collected in a reservoir and then used to perform work by their expansion, the volume of the reservoir and the passage of exhaust gases connecting said reservoir to the outlet of the impulse turbine must be large enough so that the gases stored therein exert a damping effect on the oscillations produced by the pulsation of the successive masses of exhaust gases entering the tank at a high speed. Such damping is desirable so that the turbine actuated by the expansion of the stored gases can operate more regularly and thus have a better flow rate.

   The damping effect can also be produced using well known methods, for example using envelopes or perforated walls through which gases pass on their path from the point of explosion of the discharge pressure front. towards the impulse turbine.



   The amount of dynamic energy taken from the burns exploding out of the impulse turbine can vary depending on the construction of the turbine rotor. If desired, the. Most of the dynamic energy can be taken from the gases burnt by the turbine but the gases which have passed through said turbine still have sufficient energy to push the inert gases out of it. outlet of the turbine and the passage of the exhaust gases beyond it so that the discharge pressure front explodes beyond. It is evident that as the amount of energy absorbed by the impulse turbine increases, the. pressure and energy of the exhaust gases stored beyond the turbine decrease.

   Yes

 <Desc / Clms Page number 23>

 most of the dynamic energy of the flue gases is used to drive the impulse turbine and only a small portion of said energy remains to allow the mass of the exhaust gases to pass through the ro- tor of the turbine and the outlet of said rotor, said outlet can lead directly to the open air. The small fraction of energy retained by the gases can thus be dissipated without significantly reducing the efficiency of the installation.



   Due to the high displacement speed of the mass of the exhaust gases during the exhaust-explosion, the impulse turbine rotor operates at a high peripheral speed and therefore at a high rotational speed. The turbine can driving a centrifugal or axial fan or compressor directly coupled to said turbine and all or part of the compressed air thus produced can be used for overloading the combustion chamber or cylinder of the power recovery device. The exhaust gases stored beyond the impulse turbine can be used to drive a second turbine, the two turbines doing useful work.

   The power developed by the two turbines can then be used separately or simultaneously and. the two rotors can be mounted on a common shaft. or on separate trees.



   The new power recovery device can take a single combustion chamber or cylinder connected by the intermediary of a gas exhaust tube to the rotor of a pulse turbine or, if desired, said rotor can be operated by the exhaust gases from several

 <Desc / Clms Page number 24>

 chambers or cylinders.

   As described in Applicant's prior U.S. Patent No. 2,130,721 and U.S. Application No. 588,188 filed April 13, 194b, two to four chambers or cylinders can be connected to a common exhaust manifold which, in its turn. tower, is connected by an exhaust tube. pement at the entrance of the rotor. turbinera impulse, provided that the operation of the chambers or cylinders is suitably distributed over time.

   If the power recovery device comprises an engine with multiple cylinders, for example 6 or 9 cylinders, said cylinders can be connected in groups to separate exhaust manifolds which are, in turn, connected by tube tubes. exhaust distint to separate inlet orifices of the turbine, or each chamber or cylinder can be connected by a separate tube to a separate inlet of the turbine In such installations, the inlet orifices of the turbine. the turbine must be arranged so as to avoid the passage (the exhaust gases from one tube to another or the transmission of the pulses of the exhaust gases from one of the tables to those of another tube.

   By a suitable arrangement of the inlet orifices of the turbine, the pulses of the exhaust gases from one of the tubes cannot be transmitted to those of another tube except along a path extending through an orifice. input and the rotor of the. turbine to the explosion point of the discharge pressure front and then back through the rotor to the adjacent inlet port and the corresponding exhaust gas pipe. The centrifugal or axial forces developed by the rotor of the turbine at a high speed of rotation then oppose the return of gases through said

 <Desc / Clms Page number 25>

 rotor and the passage of gases from one tube to another.



   In a power recovery plant with a constant volume turbine established in accordance with the invention and comprising a combustion chamber array, each of these chambers may have its own exhaust gas tube leading to the turbine. , in which case said turbine is provided with a separate inlet for each of said tubes and a separate gas passage between the blades of the rotor. This arrangement can also be used in an installation in which the exhaust gases are obtained from an engine of the star type.

   When the impulse turbine is actuated by the pulses of the masses of exhaust gases arriving through separate exhaust tubes and separate inlets ,. the corresponding passages of the gases through the rotor. between its blades and the outlets of the rotor must have respective cross-sections equivalent to the corresponding inlet ports so as to allow a free passage of the masses of gas through the rotor up to the explosion point of the - pressure front.

   If the turbine rotor is driven by: masses of exhaust gas arriving through separate inlet ports, said rotor may have a tendency to vibrate as a result of intermittent and unbalanced forces applied to it in this case. unwanted effect can be eliminated in. giving the rotor the shape of a slightly conical disc.



   The invention will be better understood on reading the detailed description which follows and on examining the accompanying drawings which represent, by way of nonlimiting examples, some embodiments of the invention.

 <Desc / Clms Page number 26>

 



     Fig. 1 is a diagram, partly in elevation and partly in longitudinal section of a power recovery installation according to the invention.



   Fig. 2 is a profile of the rotor of the turbine of the installation of FIG. 1 if we look at said installation from the left.



   Fig 3 is a view similar to, FIG. 1 showing a power recovery installation in which the exhaust gases actuated the. turbine are produced in the cylinder of a two-stroke internal combustion engine of the opposed piston type.



   Fig. 4 is a view similar to FIG. 1 showing an installation in which the impulse turbine is used to perform work.



   Fig. 5 is a view similar to FIG. 4 showing a different type of impulse turbine.



   Fig. 6 is a view showing the assembly of the rotor blades of the turbine used in the installation of the, FIG. 5
Fig. 7 is a longitudinal section of the installation in which the rotor of the turbine is of the axial type. - Fig. 8 is a view, partly in longitudinal section and partly in elevation, of an installation in which the impulse turbine is driven by the exhaust gases coming from two exhaust pipes from separate groups of cylinders of an engine.



   Fig. 9 is a front elevation of the rotor of the impulse turbine of FIG. 8, showing in section part of the wall of the inlet ports of the turbine.



   Fig. 10 is a view, partly in longitudinal section

 <Desc / Clms Page number 27>

 and partly in elevation, of a power recovery installation comprising several combustion chambers.



     . Fig. 11 is a diagram showing the operation of a typical power recovery installation according to the invention.



   Fig. 12 is another diagram illustrating the operation of an installation according to the invention comprising three combustion chambers or cylinders.



   Fig. 13 is a profile of a power recovery installation comprising a pulse turbine of different shape.



   Fig. 14 is a section through part of the turbine of FIG. 13
Fig. 15 shows the development of the passage through the turbine of FIG. 13
The apparatus shown in Figs. 1 and 2 is one. power recovery installation embodying the invention and comprising
 EMI27.1
 a chamber 20 of the elongated cylinder having intake ports 21 and exhaust ports 22 disposed at its opposite ends. The intake ports are controlled by a sliding sleeve
23 actuated by a connecting rod 24 connected to a crank 25 on. a suitable tree.

   The sleeve 23 has openings 26 which can be brought in front of the orifices 21 during the longitudinal displacement of the sleeve, thus establishing communication between said orifices and a channel 27 which surrounds the chamber and which is connected to the pipe. 'admission 28.



   The exhaust ports 22 are controlled by a sliding sleeve 29 actuated on a connecting rod 30 connected to a

 <Desc / Clms Page number 28>

 crank 31 on a suitable shaft. The shirt is provided with an opening 32 which can be arranged in front of the orifices during its longitudinal displacement. A channel 33 surrounding the chamber connects said orifices to an exhaust pipe 34.



     The chamber is provided with a nozzle 35 for injecting fuel and an ignition device 36 which may be a spark plug. If desired, the fuel can be introduced with the fresh air and the combustible mixture thus introduced into the chamber can be ignited by other means than the spark plug represents.



   When the chamber have filled with combustible mixture and when this. mixture has been ignited and burnt, the valve 29 opens the exhaust ports 22 to the desired extent and within the appropriate time interval so as to produce the exhaust-explosion of the burnt gases therethrough. pipe 34 in an exhaust pipe 37 connected to said pipe.

   As explained previously, the tube has a section substantially equal to that of the pipe 34, which in turn has a section substantially equal to the total area of the orifices 22 open at a time when the exhaust gases leaving the chamber 20 as a mass at ballistic speed. The tube 37 thus provides free passage to the masses of exhaust gas and enters a reservoir 38. The end of the tube inside the reservoir is flared and forms part of the cowl of an impulse turbine.



   An impulse turbine rotor 39 is disposed inside the reservoir 38 in immediate proximity to one of its end walls and constitutes another part of the cowl.

 <Desc / Clms Page number 29>

 of the turbine. The rotor is mounted on a shaft 40 rotating in the bearings .41 fixed to the end wall of the tank and the rotor is provided on its inner face with blades 42 having the curved shape shown, FIG. 2. Said rotor is generally of conical section and the vanes are arranged near the surface of the flared end of the exhaust tube. The exhaust gases which pass through the tube enter the turbine inlet 43 which is annular in shape and which is bounded by the inner surface of the tube and the opposing surface of the rotor.

   From there, the gases pass between the blades. Beyond the vanes, the gases pass through the outlet 44 of the turbine which is annular in shape and limited by the flared part of the tube 37 and the inner wall of the tank and from there they reach the main body of said reservoir. Passage through the rotor consists of passing through adjacent vanes and these passages are of substantially uniform cross section from their inner ends to their outer ends to the cross section and their total cross sectional area is substantially equal to the tube 37 at its end 'connected to the inlet of the turbine 43.

   For this purpose, theabbes are closer together and more protruding - at their inner ends than at their outer ends and they are designed in such a way that they do not present any surface on which the masses of exhaust gases enter. the turbine could rebound towards chamber 20.



   In the device described, the successive masses of exhaust gas expelled from the chamber by explosion move through the exhaust tube 37 and the impulse turbine and, on their path, said masses accelerate, move

 <Desc / Clms Page number 30>

 and compress the inert gases inside the tube and the turbine. The rotor of the turbine maintains a high speed of rotation by virtue of the pulses received from the masses of exhaust gases t successibes which pass through it. The gases exit the turbine and enter the reservoir where a discharge pressure front explodes at a certain distance from the outlet of the turbine.

   From this pressure front, the gases are forced back towards the rotor of the turbine but cannot pass through it due to the centrifugal action of said rotor. The gases are therefore stored under pressure in the tank.



   The turbine rotor is arranged approximately at the point which has been reached by the acceleration front which passes through the inert gases in the exhaust pipe at the moment when the burnt gases in the combustion chamber have acquired their maximum acceleration. , ceased to react against the walls of the chamber, and began to leave said chamber in the form of a mass. The gases act! on the rotor, therefore, have the maximum dynamic energy.



     Although it is desirable that the rotor of the. turbine is placed at a distance from the. combustion chamber such that a pulse begins to be applied to the rotor as the mass of the burnt gases ceases to react on the walls of the chamber, the rotor can also be arranged a little closer or a little further from the chamber without loss appreciable yield. The optimum position of the rotor is that indicated above and, in general, its arrangement at this point does not present any difficulty.

 <Desc / Clms Page number 31>

 



   Between the successive pulses of the exhaust gases, the rotor continues its rotation at high speed under its mo- ment and turns from the tube 37 of the intake gases which have entered said tube as the intake valves and exhaust were both open. Said inlet gases are discharged by the rotor into reservoir 38. This suction effect of the rotor produces the desirable results set forth above in that it reduces the masses of inert gases in the tube which would otherwise provide. resistance to the acceleration of the burnt gases inside the chamber.



   In the power recovery facility discussed here, rotor 39 rotates freely and is used only. in order to. to prevent the gases discharged by the pressure front formed inside the reservoir 38 and the gases stored under pressure in said reservoir from pushing back into the tube 37, and also for the purpose of sucking the inlet gases out of tube 37. Actuation of the turbine rotor for said purposes uses only a small fraction of the dynamic energy of the exhaust gas and most of this energy is used to keep the tank full. of gas under pressure.



     From the reservoir 38, a tube 45 leads to a turbine; 46 which is actuated by the expansion of the gases coming from the tank. The outlet 47 of the turbine can lead either to the free air or to a second turbine. The turbine 46 can drive a fan, generator, or other device, and in the installation shown, the fan 48-and - the generator 49 are simultaneously driven by said turbine. The compressed air produced. by the compressor 48 is produced by a tube 50 to a tank!

 <Desc / Clms Page number 32>

 see 51 from where a tube 52 leads it to the intake pipe 28.



   In the operation of the power recovery installation described 1a, the intake jacket 25 opens the intake ports 21, to the extent and within the appropriate time interval so that the compressed air coming from the reservoir 51 is sucked into. the combustion chamber. The operation of the. intake liner is time-regulated in such a way that compressed air enters the chamber immediately after the burnt gases in said chamber have started to leave it as mass at high speed, leaving behind a vacuum in the vicinity of the intake ports.

   Although the combustion chamber can be charged with fresh air at atmospheric pressure, the use of compressed air from the tank 51 raises the pressure level in the whole system and thus makes a higher flow rate of the gas possible. turbine 46.



   The power recovery installation shown in FIG. 5 comprises the cylinder 53 of a 2-stroke internal combustion engine of the opposed piston type. The cylinder is provided with intake ports 54 controlled by the upper piston 55, which is connected to a crank shaft in the usual way. An intake tube 56 leads to a channel 57 which surrounds the cylinder and which is in communication with its interior part when the intake ports are open. The fuel can be introduced into the cylinder 53 either with the air or separately, for example by means of a nozzle similar to the nozzle 35 of, fig. 1.

   The gas mixture. fuel inside the cylinder is ignited by all

 <Desc / Clms Page number 33>

 suitable means, such as, for example, a spark plug similar to the spark plug 36. At the end of the cylinder opposite the intake ports, said cylinder is provided with exhaust ports 58, which are controlled by the piston inferior
59 connected to a crank shaft in the usual way.



   The exhaust ports lead to a channel 60 which surrounds the cylinder and which is connected to an exhaust pipe 61, which in turn is connected to an exhaust tube 62.



   The tube 62 leads to a reservoir 63 and the rotor 64 of an impulse turbine is placed inside the reservoir at the end of the exhaust tube. Said rotor is mounted on a shaft 65 which rotates in bearings 66 disposed within a chamber 67 mounted internally of the reservoir on supports 68 and 69. The rotor 64 is provided with vanes 70 disposed. near the interior surface of one of the end walls of the tank.



   An expansion turbine 71 is mounted at the end of the reservoir 63 opposite to that where the exhaust tube ends.
62, and the gases stored under pressure in said reservoir pass through the expansion turbine and actuate it before being discharged through a tube 72. The expansion turbine can be used to drive any suitable machine and, in the device described, said turbine drives a fan 73 ..



   In the operation of the device shown in FIG.



  3, after the combustion of a charge inside the chamber
53, part of the energy of the burnt gases is subtracted from them for the extension of the chamber by moving the pistons away and to actuate the engine shafts to which said pistons

 <Desc / Clms Page number 34>

 . are related.

     The energy retained by the burnt gases after the ,. The driving strokes of the pistons is converted into dynamic energy, part of which is used to operate the rotor 64 of the impulse turbine. The energy which the gases still possess after having passed through said rotor, has the effect of forming a pressure front exploding beyond the rotor in the reservoir 63, and the rotor prevents the return of gases through it to the tube exhaust 62.

   In addition, the rotor draws intake gases into said tube between successive exhaust-explosions !, so that the gases which remain in said tube offer less resistance to the acceleration of the burnt gases produced by the combustion of the! next load. The gases stored under pressure inside the reservoir 65 perform work by their expansion in the turbine 71 and, in the installation shown, the expansion turbine drives a compressor. The compressed air can then be used for any desired purpose.



   The power recovery installation shown in FIG. 4 comprises an internal combustion engine comprising, a cylinder 74 provided, at one of its ends, with intake ports 75 controlled by a piston 76 and, at the other end,

   exhaust ports 77 controlled by flat head valves 78 actuated by any suitable means. The exhaust gases exiting through the ports 77 move through an exhaust tube 79, which enters a tank! 80 passing through one of its end walls, and which has a funnel-shaped end 81 disposed inside the reservoir and close to the opposite end wall.

   A

 <Desc / Clms Page number 35>

 rotor 82 of generally conical shape is arranged inside. , lying at the funnel-shaped end 81; it is provided with vanes 83 arranged in interior and exterior rows.



  A row of stator vanes 84 is mounted on the inner surface of the funnel-shaped portion 81 of the exhaust tube between the two rows of vanes 83. The rotor 82 is mounted on a shaft 85, rotating. in bearings 86 in a housing 87 fixed to the end wall of the reservoir 80. The rotor 88 of a blower is mounted on the outer end of the shaft 85 and rotates in a cover 89 comprising an inlet pipe 90 and an outlet pipe 91. A tube 92 connects the outlet of the fan 91 to a reservoir 93; hence another tube 94 leads to the intake pipe 95 of the engine. The air then passes through an annular channel 96 and ends at the intake ports 75.



   In the installation of fig. 4, the engine operates by exhaust-explosion, the gases escaping by explosion actuate the turbine rotor 82 and then, leaving the rotor, enter the reservoir 80, inside which the discharge pressure front explodes. The rotor opposes the return of gases from the tank to the exhaust tube and also serves to suck intake gases into said tube, thus improving the exhaust-explosion phenomenon, as explained above. The rotor also drives the rotor 88 of the blower and thus performs useful work, compressing the air used to charge the engine cylinder to a pressure above atmospheric pressure.

   The air thus compressed enters the cylinder by intake-suction. not

 <Desc / Clms Page number 36>

 
The gases stored inside the reservoir 80 are conducted through the tube 97 to the inlet of a turbine, expansion 98, mounted so as to drive a generator 99 or other suitable machine. So; in the installation shown in fig. 4, the two turbines are doing useful work. The rotor of the impulse turbine is established so as to use only part of the dynamic energy of the gases coming from the exhaust-explosion to actuate the fan connected to said turbine.

   The energy retained by the gases pst sufficient to produce the discharge pressure front exploding inside the reservoir 80 in the vicinity of the outlet pipe of the rotor. The passage of the cases through the rotor to the reservoir, which produces the pressure front exploding inside said reservoir, maintains the latter full of pressurized gas and these gases actuate the turbine 98 by their expansion through it.

   The rotor 82 is generally conical in shape and produces centrifugal effects opposing the return of gases therethrough. At the same time, it has sufficient structural rigidity to resist the vibrations produced by the pulsations of the masses of exhaust gases which pass through it successively.



   The installation shown in fig. 5 comprises a mild-stroke internal combustion engine 100 similar in arrangement and in operation to that shown in, FIG. 4.

   The exhaust gases, projected by explosion out of the engine cylinder, are conducted by an exhaust tube itself to an impulse turbine 102, comprising a rotor 103, the blades of which 104 sound! the opposite

 <Desc / Clms Page number 37>

 a row of stator blades 105, mounted on the inner surface of the turbine casing. The outlet pipe 106 of the turbine is connected by a tube 107 to the reservoir 108.



  The rotor 103 is carried by one of the ends of a shaft 109, rotating on bearings 110 and carries, at its other end, the rotor 111 of a fan 112 comprising an inlet pipe 113. The air compressed by said fan is brought by a tube 114 to the intake port 115 of the engine 100.



   Although the power recovery installations of FIGS. 4 and 5 are broadly similar, it can be seen that the impulse turbine of the installation of FIG. 5 is connected by a tube 107 to the reservoir 108. The inlet pipe. of the turbine 116, the passages through the vanes of the rotor 103 and the outlet tubing of the turbine 106 are suitably proportioned as previously stated, so that the masses of exhaust gases which pass through these various components encounter a minimum of resistance per unit length of path of the inert gases located on said path.

   Tube 107 is also of suitable cross section for the same purpose and, in such an installation, the discharge pressure front may explode inside tube 107 or reservoir 108. ' The gases stored under pressure in reservoir 108 can be used for any desired purpose, for example to operate an expansion turbine similar to turbine 98.



   The power recovery installation shown in FIG. 7 includes an internal combustion engine with two

 <Desc / Clms Page number 38>

 
 EMI38.1
 t; ::; ps 117 of the type with opposed pistons and aU2.1oc.; ue in general terms in arrangement and in operation to that shown in fig. 3. Lan n. ecua.ppement projected j'c :: Y \, CJsence 1.1 19.,). CD.7- ct eCllapj) emen; ITOJ0 es pB.r explosion out of the engine cylinder are conducted, 8.through a flash Lube13.)) Om8nt lL8, s. a turbine 119 of the axis.1 type.



  This turbine comprises a rotor 120 comprising two rows
 EMI38.2
 spaced blades 121;) between which are dj5.:.10SeS stator vanes 122, mounted on the inner wall of the en-
 EMI38.3
 turbine bike. The gases, after their passage between the blades, enter a tub1l1uir'e c: de ;, 13IDtti e, .l23,: é t ",.; Dell. [" Are conducted to a reservoir, not shown, through a tube 124. The rotor is mounted on one end of a
 EMI38.4
 shaft 125, tournatltr. "da.118 suitable bearings and carrying at its other end the rotor 126 of a fan 127.

   The air compressed by the blower can be used for any suitable purpose :, such as loading the cylinder of the engine at high pressure, and the gases from the reservoir can be used as desired), for example to operate a high pressure turbine. relaxation.



   The turbine IL '.) Is established so as to use only part of the dynamic energy; exhaust gases
 EMI38.5
 Which pass through it, and said said, a..9 apecs their outlet of the turbine, form a discharge pressure front which explodes, either in the tube 124 or in the reservoir to which said tube terminates.



   The vanes 121 of the turbine 119 are arranged so
 EMI38.6
 a develop axial deflection forces in the masses of k:; l1 ;;; which cross them, forces which: 'o; losetl; when the

 <Desc / Clms Page number 39>

 gas, through the turbine, to the exhaust pipe 88.



   The power recovery installation shown in fig. 8 comprises a two-stroke internal combustion engine 128, comprising 6 cylinders 128a arranged in two groups of 3, the exhaust ports of the cylinders of each group being connected to one of the two exhaust manifolds 129 and 129a , which lead to respective exhaust pipes 130 and 130a. The gases projected by explosion out of the cylinders of each group are conducted by one of the collectors 129; 129a, and one of the exhaust tubes 130, 130a, connected to said manifolds, to one of the two passages 131, 13113.,. of Input isolation 132 of a pulse turbine.

   The passages 131 and 131a are limited in part by the wall of said inlet element and in part by a transverse wall relating to said passages 131 and 131a leading inside a casing 134, inside which is disposed a pulse turbine rotor 135 provided with blades 136. Said rotor is mounted on one of the ends of a shaft 137, rotating on suitable bearings arranged in a
 EMI39.1
 extension of the envelope 134. At the periphery, Ltduc.JZotor'J11 '. .- 'the casing is arranged so as to provide an outlet pipe 138 for the gases leaving the rotor and a tube 139 leads from said outlet to the reservoir 140. A tube 141 leads from said reservoir to the inlet pipe of a expansion turbine 142, the casing of which can be, if desired, an integral part of the casing 134.

   The expansion turbine comprises a rotor 143, mounted on a shaft 137 and provided with rows of vanes 144 alternating with rows of vanes :, stator 145 mounted on

 <Desc / Clms Page number 40>

 the. inner wall of the turbine casing, expansion.



  The gases which have passed through said turbine are. evacuated through the outlet pipe 146.



   In the power recovery installation of the, fig.



  8, the rotor of the expansion turbine is coupled], by means of a shaft 147 mounted on suitable bearings, to the rotor 148 of a compressor 149. Said roton is provided with rows of blades 150 alternating with rows of blades. stator vanes 151, mounted on the inner wall of the compressor casing. The compressor has an inlet tubing 152 and an outlet tubing 153, and its rotor can be connected by a shaft 154 to the shaft of a generator 155.



   As represents at the. fig. 9, the. transverse wall 156 relating to the inlet element divides the unit into two inlet pipes 131 and 131a, each of which leads to the vanes carried by each of the rotor halves 155. The total section of the passages between 7¯'one of the halves of the rotor blades is a, then substantially equal to the section, of one of the inlet pipes 131, 1310., and the section of each of these is substantially equal to the corresponding section of the end of the tube d 'exhaust 130 or 130a which is connected to it.

   Each of the tubes 130, 130a has, at its other end, a section approximately equal to that of the manifold 1;.; 9 or which is connected to it and the section of each of said manifolds is substantially equal to the area of the orifice. - exhaust from one of the cylinders connected to the side manifold, open when the burnt gases start to. to leave - . said cylinder in the form of a mass.

   Accordingly each of the * manifolds, the exhaust pipe connected to it, the,

 <Desc / Clms Page number 41>

 lure inlet of the turbine to which said tube ends and the blades of the corresponding half of the rotor, constitute a permanent free passage for the masses of exhaust gases? The outlet pipe of the turbine 138 and the tube 139 are of similar shape and proportions so as to allow the free passage of masses of exhaust gas.



   In the power recovery installation of FIG. 8, the impulse turbine rotor is located approximately at the point reached by the acceleration front moving through the inert gases, in one of the manifolds 129, 129a and in one of the tubes d 'exhaust 130, 130a connected to said manifolds, during each exhaust-explosion of the middle cylinder 128a of one of the groups, when the gases burnt inside said cylinder cease to react against its walls and begin to leave it in form. massive.

   As a result, the turbine rotor begins to receive an impulse, transmitted by the inert gases, as the burnt gases begin to leave the cylinder:. As a mass and all of each of the masses of exhaust gas passes through the rotor. The distances traveled by the masses of exhaust gases between the extreme cylinders of each group and the rotor, are, respectively, shorter and longer than the corresponding distance relative to the middle cylinder but, as a result of the speed of displacement of the front of acceleration through the inert gases, the variations between said distances are insignificant.



   In the operation of the installation shown in FIG. 8, the gases projected by explosion through the tubes,

 <Desc / Clms Page number 42>

   exhaust 130 and 130a are conducted, through the respective inlet pipes 131 and 131a, to the rotor of the impulse turbine 135 and impart part of their dynamic energy to it. After having passed through the rotor, the gases have
 EMI42.1
 a cner, ie sufficient dynamics for them. allow it to enter tube 139 and form a discharge pressure front which explodes, either in said tube well beyond the outlet of the rotor, or in reservoir 140.

   The action cen-
 EMI42.2
 tri; f: LlC; 8 of the rotor is such that it prevents L'.Z backflows because the explosive pressure front or 0.1; , r. :: siné ;: inside the tube 19, the tank 140 and the tube 11L to retract the rotor towards the exhaust tubes 130,1 ::, 08. and, following the GD.7, are stored under pressure from the tubes and into the tank. The ;;: -. 2. c; lc: 1'L ';' f ', inr: 3 lelzUr¯1; ; ECilCi) i) 87 "" from tubes 139 and 141 and from tank 14u 1 #. through the expansion turbine 142, then, on leaving said turbine, they are evacuated through a tube 146 into the outside air or used for
 EMI42.3
 h or r, Uf3cl, L:; 8 de sire.



  Impulse and trigger turbines work together
 EMI42.4
 ; 7oa drive the rotor 1 "± the compressor and also, if it is d: [sire, the <'llcre.tor 1- = b.Ji the Totors to the impulse and expansion turbines etc. 7.' inst;: a..¯: .tâc: n are. ".J.i1 :: '1 couples the izll 3 .L?, ütlC and at oL0r the r'.OÜ11T' (-: ;; lfary the s z. o 1 or of the 1; 1 = ': 711îe: expansion and the compressor i.oix-ei; 1 be established to operate at high speed.
 EMI42.5
 With the device represents, a frél.ctiol1) lub or
 EMI42.6
 . i <; 1, n :: ..; r:.: Ncl8 of 1 '¯cr, ic: c1Jnnmiq, e (; 0; ..; 1;

   G a.z assets pcuL be .a # .. ili;. <The .îOLtY .. 'cti..onnol' 1. ''. 1.irbis <; 1, momentum and energy

 <Desc / Clms Page number 43>

 then available to allow the gases stored under pressure to operate the expansion turbine varies accordingly? The reservoir 140 is of such dimensions that the gases which are contained have a damping effect on the explosive gases from the discharge pressure front to the expansion turbine. Such a damping effect makes it possible to obtain smoother operation of the expansion turbine.



   The power recovery installation shown in FIG. 10. comprises two combustion chambers 157 and 158 comprising inlet ports 159 and exhaust ports 160 disposed at both ends of said chambers, said ports being controlled. by flat-head valves 161, which can be actuated in a suitable timing over time by members driven by a common shaft 162. Fresh air under pressure is supplied to the chambers from tanks 163 and 164 by the intermediate tubes 165 and 166 and the respective inlet ports.

   Fuel is introduced into the chambers by any suitable means, such as, for example, the nozzles, injection 167, 168 and the combustible mixture thus produced inside each of the chambers can be ignited, for example by spark plugs 169. and 170. The exhaust ports 160 of the two chambers lead to exhaust pipes 171 and 172 which are connected by respective exhaust tubes 175 and 174 to inlet passages 175, 176 leading to passages between them. vanes of the respective halves of an impulse turbine rotor 177 disposed within a reservoir 178. The ends of the exhaust tubes 173, 174 within the

 <Desc / Clms Page number 44>

 
 EMI44.1
 tank are flared so as to form an envelope for
 EMI44.2
 the turbine rotor,

   and said rotor is provided with rows
 EMI44.3
 vanes L & '9, arranged between the stator vanes 180). climbs
 EMI44.4
 on the. inner wall of said envelope. This one is
 EMI44.5
 for '! éo of an a.nnular outlet la1 condLisv.rlt tubing of the rotor.'. inside the tank 178. The rotor 177 is =;: # :. nt; 1 on a shaft 182) carries by suitable p: J..l.iers and. reli, -S;) .. 1 rotor lU3 of an axia.l type compressor. The latter rotor is made up of rows d .'.-., Ikies 184, between which are arranged d.e..sto.tal blades:, 7noittcs. on lu,]) 8, king 1 <.il; erit; are do the envelope of the corlpr.e7sor. The compressor is, nllni of an inlet pipe 18G and two outlet pipes 167, 168 respectively connected by tubes J, 1 (, l (JO to tanks 1G3 and 164.



  Un: 9D.GS; "L8 de Cél, Z el 'úch: J.Pl1oJùcnt 191 leads from the reservoir 178 k to the inlet pipe of a Lurbinn a. Expansion type.%; L = .1 10'7, . The rotor L95 of the lR.di tr .: turbine is fitted with r;:, ncécs d '..., nc 104) between which are arranged blades of:' t "bor lLi..5, nothces on the wall interior, dj the envelope of 1 ;. turbine. The rotoy 1911 is mounted on a shaft 1? 6, carried by COl1Veno bearings, 11lles, and said shaft can be coupled to a suitable machine, such as a dynamo 1 ± '7.



  In the operation of the installation recuper'a-trise c> power of 18 ... Lit ;;. 10, the j ', Z cl'écllapp,.;, 16l1t produi-ts--, z ns 1e.sché) .mbreG' of combustion are expelled from said ehaM'b'ï'es "<: ri;) explosion and operate the rotor of the turbine- L-1:., \ l; LoiEH'1 177 which drives 0, son 1.0111 'the rotor 195 of the cOlil-pres-BG! u.: r.'q101.i .jio <ijil:>:

  <ie i'i, ir coiaprime used to power the li chambers

 <Desc / Clms Page number 45>

 combustion. The dynamic energy retained by the gases leaving the rotor of the expansion turbine causes the formation of a pressure front which explodes inside the tank
178 and, given that the gases discharged by the explosive pressure front and stored inside the tank
178 cannot, as a result of the centrifugal action of the rotor, cross the latter again, these stored gases are kept under pressure and are capable of activating, by their expansion, the turbine 192.

   The exhaust tubes 173 and 174 lead through the inlet tubes 175 and 176 to the separate halves of the impulse rotor rotor, so that the gases from one of the tubes are not affected by those from the chambers. combustion chambers 157 and 158 operate so as to use both the intake-suction and the exhaust-explosion, so that said chambers are self-evacuating and self-sucking and, if said chambers of pressurized fresh air from reservoirs 165 and 164, the pressure level in the assembly rises, and both pulse and expansion turbines have greater flow.



   The operation of a typical power recovery plant comprising a combustion chamber saddle, established and operated in accordance with the invention is shown in the form of curves in Fig. 11 of the drawings. In this figure, the ordinates of. some 'of the curves represent gas pressures' and the ordinates of the other curves represent the surfaces of the exhaust and intake ports, opened by the corresponding valves, expressed

 <Desc / Clms Page number 46>

 sounds form reports of open surfaces day perform the exhaust-explosion and the intake-suction to the cross section of the. combustion chamber.

   The abscissas represent times expressed in thousandths of a second or in degrees of rotation of mechanical parts) such as shaft 162 (fig. 10) which makes a complete revolution to open and close the exhaust ports - and admission.



   In fig 11, the ine 198 represents the atmospheric pressure or the. average pressure in an air tank, such as tank 51 (Fig. 1) from which air is supplied to the combustion chamber. Curve 199 is a time-area diagram showing the opening area and the opening and closing times of the exhaust ports. of the combustion chamber, the start of opening of the exhaust ports being indicated (in EO and the total closure of said ports being indicated in EC. Curve 200 is a similar curve) representing the opening surface ' and the durations of opening and closing of the inlet ports of the. bedroom .

   The beginning of the opening of the inlet ports is indicated in AO and the total closure of said ports is indicated (-, il AC.



   Curve 201 represents the apparent gas pressures,. '. the interior of the combastioin chamber, during the cycles, of operation and the curve 202 indicates the apparent gas pressures in the exhaust tube, at a point close to the exhaust ports ,. Therefore,) curves 201 and 202 represent the pressure conditions at the respective positions indicated, during the exhaust-explosion and the admission.

 <Desc / Clms Page number 47>

 sion-aspiration. The gas pressures within the chamber and the exhaust tube can be determined by any known method, such as, for example, using a cathode beam oscillograph.



   As indicated by the curve '199 in fig. 11, the chamber exhaust port begins to open approximately when the gas pressure inside the chamber is at its maximum due to the explosion or combustion of the charge. During the opening of the orifice, a sudden pressure pulse and shock occurs at the assumed measuring point inside the exhaust tube, as indicated by the tip 202a of curve 202. When the The exhaust port opens fully and remains open, the apparent pressure inside the tube falls below the inlet pressure and remains below this pressure until the curve becomes drops abruptly from point 202b as a result of the following exhaust explosion.



  The pressure inside the tube is kept relatively low as a result of the displacement of the mass of the exploded flue gases beyond the measuring point in the tube, by the action of the impulse turbine rotor, which acts by inertia to draw gases out of the tube.



   In the installation whose operation is represented by the curves, the pressure in the combustion chamber, after reaching the maximum 201a, drops rapidly as a result of the exhaust-explosion, until the maximum depression apparent inside the chamber, represented by point 201b is reached. When this depression appears

 <Desc / Clms Page number 48>

 te is established inside the chamber, the inlet openings are opened in such a way that the inlet-aspiration is obtained. The control elements of the intake ports
 EMI48.1
 are established and actuated èlec, ma.nièrc 'to: Close said orifices after the closing of the exhaust ports.

   This results in a rise in pressure inside the chamber and the chamber is overloaded :, as indicated by the, higher and flattened part of the curve bearing the reference 201c.



  The average pressure in the exhaust gas tank beyond the impulse turbine is indicated by line 203.



  The actual pressure inside the tank is variable due to the intermittent introduction into said tank of masses of exhaust gas.



   The operation of a typical power recovery installation according to the invention, comprising the three cylinders of an internal combustion engine connected to a single exhaust pipe is shown in FIG. 12 on which curve 204 represents the pressures in the tube, at a point close to the combustion chambers. The operation of the intake and exhaust ports of each cylinder is expressed in degrees of rotation of the engine crankshaft.

   Curve 204 represents the pressures in the exhaust pipe
 EMI48.2
 near the cylinders and it can be seen j .-- that when the pressure in the tube has fallen below the base pressure shown by line 205, it remains below
 EMI48.3
 said pressure following the part of.1R.00be.represented-in zou, until the exhaust-explosion - daM & the-.second- "'. cylinder begins. The. vacuum inside the tube , rep-

 <Desc / Clms Page number 49>

 felt by part 204a of the pressure curve is that which the mass of exhaust gas leaves behind its passage in said tube and is maintained by the action of the rotor of the turbine which opposes the return of the gases through said rotor and which sucks inlet gases out of the tube.



   The power recovery installation shown in fig. 13 to 15 inclusive, comprises a two-stroke internal combustion engine comprising a cylinder 205 provided with exhaust ports and an exhaust manifold at its upper part. An exhaust tube 207 leads from said pipe to the inlet pipe 208 of an impulse turbine whose casing 209 surrounds a rotor '210, driven on a shaft 211, rotating in suitable bearings. The rotor is provided on one of its faces with a row of blades 212 and the gases entering the casing of the turbine ^ through the inlet pipe pass through the blades to the pipe outlet 213, which is connected by a tube 214 to a reservoir. 215. A tube 216 leads from said reservoir, for example to an expansion turbine.

   The impulse turbine rotor shaft is coupled to the rotor of a compressor (not shown), by means of which compressed air. is supplied, through tube 217, to the intake ports of cylinder 206 of the engine.



   It should be noted that the inlet pipe 208 of the turbine,. is spiral-shaped and of an imperceptibly decreasing section. and that the outlet nozzle 213 of the turbine is also spiral-shaped, but of imperceptibly increasing section. The sections of the ends of the outlet tubes

 <Desc / Clms Page number 50>

 and inlet are equal and, between the ends, the sum - of the sections of the inlet and outlet pipes taken along any transverse plane is equal to. the sum of the sections of their ends.

   The passages between adjacent blades of the rotor of the turbine have a uniform section from end to end and said blades are of such a shape that they do not present to the masses of exhaust gas arriving on them any surface on the , which said masses could rebound towards the combustion chamber ..



   In each of the variants of the new power recovery installation, the impulse turbine ensures a free passage to, ux masses of exhaust gases which meet, therefore, only a minimum of resistance offered by the inert gases on their path through the turbine per unit length of this path. The impulse turbine receives the active gases at full speed from the source of said gases and the turbine uses part of the dynamic energy of said gases, always leaving them with sufficient dynamic energy so that the masses of exhaust gases can push the inert gases out of the turbine outlet pipe.

   In this way, it is ensured that virtually all of each mass of exhaust gas passes through the turbine and that the explosion site of the discharge pressure front is located beyond the outlet pipe of the turbine. turbine. Said turbine operates, in each of the variants of the power recovery installation of the invention, in such a way, on the one hand, to oppose the return to. through it gases driven back by the exploding pressure front and gases stored under pressure beyond the turbine and, on the other hand, to be sucked out.

 <Desc / Clms Page number 51>

 of the exhaust pipe of the fresh admission gases which have entered said pipe during the period during which the. ,,. exhaust and intake ports were open.

   In addition, in each variant of the new installation, the rotor of the impulse turbine is located in such a way on the path of the masses of exhaust gases leaving the combustion chamber, that said masses act on the rotor. of the turbine when they have their maximum speed and dynamic energy.


    

Claims (1)

ABSTRACT. The invention relates to power generating systems, making up a gas turbine of the constant-volume explosion type. It aims, in particular, to use the energy of the exhaust gases produced by the combustion of successive charges of a combustible mixture in a compartment the volume of which remains approximately or absolutely constant during the course of the process. 'exhaust of the burnt gases and the admission of fresh gas charges. It uses the exhaust-explosion and intake-suction phenomena and, consequently, the above-mentioned compartment itself performs its own evacuation and its own charge, without the need for a pressurized gas supply for sweeping. and the load. The dynamic energy of the burnt gases is used to drive a turbine, the operation of which, far from hampering that of said compartment, facilitates the use of the phenomena mentioned. At the exit of the turbine, the gases are collected and used to accomplish a new job. <Desc / Clms Page number 52> In order to use the dynamic energy of the exhaust gases projected by explosion, the invention provides for the installation of a special impulse turbine on the path of said gases, driven at a high speed by the passage of the gases. The turbine is disposed between the exhaust port of the compartment and the explosion region of the discharge pressure front and, in a preferred arrangement substantially at, a point reached by said front in the exhaust tube at, l 'instant when the burnt gases stop reacting against the walls and begin to. leave the compartment as an explosive mass. As a consequence of this arrangement of the turbine, the mass of the exhaust gases, burnt gases and inert gases located in the exhaust tube, pass through the entire rotor of the turbine, acting on it with its entire energy ;; without reaction against the walls of the compartment. For the aforementioned purposes, the turbine according to the invention is constructed and arranged so as to develop, in the masses of gas passing through it, centrifugal forces opposing it. the pressure of the gases trapped inside the expansion chamber and in the tubing which terminates therein, preventing said gases from exerting a retroactive action, through the turbine and the exhaust tube, towards the combustion chamber. These centrifugal forces are produced at the high rotational speeds of the rotor of the turbine, thanks to the arrangement of the inlet opening to said rotor, towards its center of rotation and to the general radial arrangement of the interstices between the blades, up to the output of the rotor. <Desc / Clms Page number 53> The entire passage reserved for gases through the turbine is designed in such a way that it constitutes the extension of the exhaust tube and allows said gases to pass freely. For this purpose, the section of said passage remains constant and practically equal to that of the exhaust tube. In addition, the blades of the rotor and the walls of the tubes which terminate thereon are of such a shape that they do not present to the gases in transit any surface liable to cause them to rebound towards the compartment. Under these conditions the volume of inert gases displaced per unit path of the exhaust gases remains practically constant, their resistance to displacement is. minimum and the discharge point of the discharge pressure is located beyond the outlet of the turbine. In general, the invention expressly envisages, as new industrial products, power generating devices comprising, separately or in combination, the stated improvements. 3 crossed out words-Null 4 words spaced.