EP1269025A1

EP1269025A1 - Thermo-kinetic compressor

Info

Publication number: EP1269025A1
Application number: EP01907689A
Authority: EP
Inventors: Joseph Haiun
Original assignee: Haiun Joseph
Current assignee: Thermokin
Priority date: 2000-02-16
Filing date: 2001-01-25
Publication date: 2003-01-02
Anticipated expiration: 2021-01-25
Also published as: ATE389811T1; DE60133268T2; CA2399580A1; US20030012658A1; DK1269025T3; RU2286483C2; ES2303524T3; FR2805008B1; DE60133268D1; PT1269025E; CA2399580C; WO2001061196A1; FR2805008A1; AU2001235598A1; US6935096B2; EP1269025B1

Abstract

A device for compressing gas using thermal energy. In a subsonic embodiment the heat gas passes through a convergent pipe C 1 where it is provided with operating velocity, a convergent pipe C 2 where it is simultaneously maintained at high speed and cooled by evaporation of liquid sprayed by nozzles R with adjustable position distributed in C 2. In a supersonic embodiment, the gas reaches sonic velocity at the throat of C 2 and supersonic velocity in a divergent DG, then compressed in a convergent CG 1 and simultaneously cooled by evaporation of sprayed liquid. In both embodiments, the gas is finally compressed in a subsonic divergent DG 1. Pipes with variable geometry enable to modify the cross-sections of the throats of the device. The device is essentially designed for thermoelectric power stations.

Description

THERMOCLNETIC COMPRESSOR

DESCRIPTION

The present invention relates to an air compressor or any other gas at low cost, whose primary energy used in the compression cycle is not mechanical or electrical energy as in most compressors, but directly thermal energy, this compressor has no moving parts subject to wear, and the energy losses due to friction as well as the excess heat from the cold source of the cycle can be recovered to be reused in the compression cycle or to generate pressurized steam which, mixed with compressed gas, increases the flow rate This device finds its application in the compression or partial vacuum of any industrial gas, but its thermal cycle predestines it particularly for the realization of power plants high efficiency thermo-energetics, energy saving systems such as mechanical vapor recompression, or rec uperation and conversion of residual thermal energy

Conventional compressors are traditionally made up of devices in which 1 gas compression energy is supplied in the form of mechanical energy (volumetric compressors, centrifugal or axial compressors,) or potential or kinetic energy of another gas (ejectors), such compressors require significant maintenance due to the mechanical friction and wear which result therefrom, and have low energy yields (see very low for the ejectors), mainly due

-At multiple energy conversions in the equipment used Thermal motors or Turbines to convert thermal energy into mechanical or electrical energy, possibly alternators and electric motors to transform electrical energy into mechanical energy, then finally compressors to transfer the mechanical energy with gas to be calculated,

-At relatively low temperatures used during the first transformation of thermal energy into mechanical energy, -At the heating of the gas to be compressed during its compression (which inevitably distances it from adiabatic compression), -Λux mechanical friction and kinetic energy losses of the gas to be compressed - In the non-recovery, in the total cycle, of thermal energies coming from compression, losses by friction, and from the cold source of the engine or the turbine - With mechanical wear,

-At deposits and fouling on air compressors, that even frequent washing (case 45 of gas turbine compressors) can only reduce

The device of the invention overcomes has most of these disadvantages by using a different cycle, consisting in pretreating the gas to compress and provide it directly to ^thermal energy if its temperature is not high enough , to relax the latter

^→ v) at a subsonic, sonic or supersonic speed through expansion nozzles, to take a heat sample at high speed (and therefore at low temperature) by controlled spraying (and evaporation) of liquid distributed in an expansion nozzle cooling (the nozzle making it possible to maintain a high speed), and finally to recompπmer this gas in an adiabatic compression nozzle in order to reduce its speed to a normal flow value the 5 expansion, expansion-cooling nozzles adiabatic compression can be fitted with a variable geometry system, allowing the sections of their inlet and / or outlet necks to be adjusted in order to regulate, among other things, the flow rate and the compression rate of the device. temperature causes a considerable entropy drop in the gas to be compressed, which results in a pressure at the outlet of the device much higher than the

60 inlet pressure

In this device, the energy losses due to the pressure losses of the gas to be compressed as well as the heat losses through the walls of the device are reinjected in the form of heat in the gas to be compressed, thereby reducing the initial thermal contribution Likewise, the excess heat from the cold source is dissipated by the evaporation of the liquid.

(> 5 sprays, thereby increasing the flow of compressed gas at the outlet of the device this increase in flow, which can be eliminated at the outlet of the device by condensation, is useful for certain applications of the device and in particular for the realization of thermoelectric power plants where it very advantageously replaces steam generators in steam power plants and especially in combined cycle power plants

"o The shock or compression waves which may possibly develop in the supersonic part of the flow can be suppressed or moved towards the outlet of the device, as described in the variants detailed below BASIC VERSION 1 In its simplest concept which we will call Basic version 1, represented on the

7 s in figure 1, the device according to the invention uses a subsonic or sonic flow, it includes a suction line equipped to pre-treat and reheat the gas to be compressed if necessary an optional intake chamber "C" intended to tranquilize the gas flow before its admission into an expansion convergent "C l" making it possible to increase its speed up to the sonic speed possibly, an optional transition zone "N", a convergent nozzle

80 Cooling Relaxation "C2", a cooling system "R" consists of set of nozzles for spraying water (or other liquid) with adjustable flow and / or position from 1 outside of the device distributed along zones "N" and "C2" and intended to extract heat from 1 air (or gas to be compressed) by evaporation of the injected liquid, and finally an adiabatic compression divergent "D" intended to compress the gas by reducing its speed 85 to a normal flow speed (of the order of 10 to 50 m / s) before being admitted to a “T” stilling chamber (Optional) and being discharged into an evacuation pipe

The transition zone "N" ensures a continuous connection between the ends of "C 1" and "C2" with a generator with a monotonous slope, and without angle

90 Depending on the requirement for the gas to be compressed, 1 suction can be fitted with the following additional optional elements Suction filter “F” Silencer “S” Primary compressor “CP” intended for commissioning the device or for a pre -compression of the gas to be compressed Heat exchangers “E l” “E2” “En” (using, directly or using an intermediate fluid, the residual heat contained in the compressed gas at the outlet of the device or any other heat source available elsewhere) and Burner "B" (supplies fuel) intended to heat the gas to be compressed if its temperature is not high enough at 1 inlet to the device, and finally "TB" expansion turbine intended to possibly transform 1 energy compression in mechanical energy Similarly, depending on the context of use of the device, the evacuation pipe can be fitted

100 of optional elements such as Hot gas recycling systems, “E '1” exchangers

"E ^' 2""En" allowing the residual heat contained in the compressed gas to be recovered from the Silent device "S'", this equipment can only be supplied with part of the compressed gas and can be installed downstream of a burner and a turbine if the device is intended for the production of mechanical or electrical energy

105 Reheating the gas upstream of “C” makes it possible to superheat it to move its temperature away from the saturation temperature with the sprayed liquid depending on the compression ratio and the desired yield, the superheating temperature can range from 100 ° C up to at more than 1500 ° C During its flow in the converging expansion / cooling nozzle "C2" the gas

1 lo is at each instant relaxed and set in speed in the converging tank, and simultaneously cooled by the evaporation of the sprayed liquid, which causes its contraction in sonic or subsonic regime and therefore a fall in speed (with fall in entropy and increase pressure) which attenuates or suppresses the tendency to increase speed due to the convergent distribution of spraying and evaporation along the neutral zone "N" and the tuvere

January 15 "C2" allows for ^a balance between the trends of increase and decrease speed and thus perform a heat removal while maintaining an optimum speed (sonic or subsonic) along the axis of "C2"

For this purpose the cooling system "R" allows to adjust the distribution of the cooling along 1 axis of "C2" by any moven allowing the adjustment of the flow rate and / or the position of

120 each nozzle an exemplary embodiment, represented in FIG. 1 1 shows nozzles arranged in radial fins distributed along the axis of "C2", with the possibility of adjusting manually or automatically from the outside the flow of liquid injected into each row of nozzles using external valves), a second preferred embodiment shown in Figure 1 2, shows spray nozzles distributed along the axis of the

125 device in zones “N” and “C2” and arranged at the end of axially sliding concentric tubes, the tubes are supported by threaded bearings at the end of the intake chamber, the threads making it possible to adjust manually or automatically from outside the position of each spray nozzle, external valves allow the flow rate of each nozzle to be adjusted

PO Of course the device can be designed with a single spray nozzle, but it then has a degraded yield

In order to reduce the length of the zone "C2" and therefore to reduce the pressure losses of the gas to be compressed through the device, the spray nozzles used are preferably nozzles at high injection speed and with minimum droplet dimensions such only nozzles

P5 at high pressure with assistance with compressed air or steam, and optionally with ultrasound or microwave

For gas inlet temperatures of "C" below 300 ° C, parts "C", "C l" "N", "C2", "D", and "T" can be made of steel carbon, stainless steel or any other material compatible with the gas to be compressed and having good resistance

140 mechanical and good abrasion resistance at 300 ° C, for gas inlet temperatures of "C" above 300 ° C, these parts can for example be made of carbon steel coated internally with heat insulation or refractory, carbon steel or stainless steel with double jacket (cooled with water or compressed gas, the latter can be reused in the device), ceramic, or any other material with good mechanical resistance

145 and good resistance to abrasion at high temperatures

As an example of an embodiment, the device according to FIG. 1 makes it possible to compress from 1 bar A to 2.5 bar A nearly 30,000 Nm3 / hour of air, from the following elements - A suction line of air with an internal diameter of 0.6 m in carbon steel including a primary starting compressor capable of developing an overpressure of 100 mbar and a

Po burner running on natural gas with inner lining of the refractory concrete suction line at the burner and downstream, the burner preheats the air to a temperature close to 1200 ° C -A cylindrical intake chamber "C »Of length 1.5 m and diameter close to 1.2 m - A cylindrical expansion convergent" Cl "of length 0.6 m and outlet diameter 0 6 mp - A transition zone" N "cvlindπque in diameter 0.6 m and 0.3 m long

-A nozzle “C2 with an inlet diameter of 0.6 m, an outlet diameter of around 0.35 m and a total length of around 1 m - A divergent“ D ”with an inlet diameter of 0 35 m and a length of 0 , 3 m - A stilling chamber "T" of diameter 0 6 m and length 0 7 m

160 -A heat exchanger between the compressed air at the outlet of "T" and 1 air at the intake The intake chamber "C" is made of carbon steel coated entirely with refractory concrete, while "C l", "N", "C2", "D", and "T" are made of carbon steel a double jacket cooled by air circulation to be compressed before entering the air intake, the spray nozzles installed on (and supplied by) a system of tubes

165 concentric carbon steel slides with an outside diameter of 60 mm passing through the intake chamber, are distributed in "C2" and allow the injection of nearly 4.7 kg second of water at 200 m / second with average dimensions of droplets close to 10 μm VARIANT 2 A variant 2, concerning a sonic or subsonic flow, represented in the figures

170 2 1, 2 2, 2 3 and 2 4, makes it possible to adjust the flow rate of the gas to be compressed, the compression rate, and the energy efficiency of the device. In this variant, the zone "C2" (Expansion nozzle / cooling) and zone "D" (divergent adiabatic compression) of the basic version 1 are replaced by a converging nozzle and a diverging nozzle both with variable geometry which allows to adjust the outlet section of "C2" and the section input of "D" and

175 therefore the section of the neck between “C2” and “D”, the system of variable geometry, controlled from outside the device, is obtained by any mechanism making it possible to modify the section of passage of the neck of the device, such as the use of deformable walls on the nozzles “C2” and “D” as shown in the example in FIG. 2 1, or the addition of a profile core “K” or “Kl” which can slide axially in the areas “N "," C2 ", and" D "and fixed on a

180 shaft passing through one (or both) ends of the device making it possible to adjust the position of the core from the outside as in the examples in Figures 2 2, 2 3, and 2 4 The example in Figure 2.1 relates to a nozzle of circular section with deformable walls, the zone “C2” and the zone “D”, consist of overlapping flexible steel strips and regularly arranged on the generatπces of the dispositi and their ends are welded on the

185 edges of the transition zone "N" and the plenum of circular clamps or any other system (veπns, etc.) allow to modify the central section of the arrangement which then constitutes the neck of the zones "C2" and " D "

The other elements of the device are identical to those described in the basic version 1 The exemplary embodiment shown in FIG. 2 1 has the same performance as

190 the previous example concerning basic case 1, with the possibility of modifying the flow rate and the compression rate of the gas to be compressed

The example of figure 2.2 relates to a nozzle of rectangular section it is equipped with an adjustable system constitutes of a core "K" sliding axially in the zones "N" "C2" and "D, and whose axis is fixed on a shaft passing for example 1 one (or both) ends of the

195 device the axial position of the core "K" can be adjusted manually or automatically from 1 extender by a thread placed on a bearing, by an external veπn or by any other external system

The spray nozzles are distributed in the "N" and "C2" zones. The other elements of the device are identical to those described in the basic version 1 200 The new "K" is a piece of rectangular section, two opposite faces parallel to the axis are juxtaposed to the faces of the tu / er the other two faces of the core have an aerodynamic profile allowing to minimize pressure losses of the gas to compress, each of them consists of an upstream part "K '" of constant or increasing section in the direction of gas flow, of a downstream part "K'""of decreasing section in the direction of flow

205 of the gas, and an intermediate part "K" "whose continuous profile (without angle) ensures the link between the generator of" K '"and that of" K' ""

The parts "K" "of the core" K "slide in the neck between the expansion / cooling nozzle" C2 "and the adiabatic expansion divergent" D "Depending on the application sought for the device and according to the gas temperatures to compress to

210 1 inlet to the intake chamber "C", the core "K" can be made of carbon steel

(temperatures below 300 °), stainless steel, steel cooled by internal circulation of cooling fluid, ceramic, or any other material having good resistance to abrasion and to the temperatures used. Figure 2.3 concerns a circular section device, it is equipped with a

215 adjustable system consists of a core "K" sliding axially in the areas "N" "C2" and "D" the core being fixed on a shaft passing for example one (or both) ends of the device, the position axial of the core “K” can be adjusted manually or automatically from the outside by a thread placed on a bearing, by an external veπn, or by any other external system

220 The spray nozzles are distributed in zones "N" and "C2"

The other elements of the device are identical to those described in the basic version 1 The core “K” is a solid part of revolution whose aerodynamic profile makes it possible to minimize the pressure losses of the gas to be compressed, it is made up of a part upstream "K '" of constant or increasing section in the gas flow direction, of a downstream part "K'" "of

225 section decreasing in the direction of gas flow, and an intermediate part "K" "whose continuous generator (without angle) ensures the link between the generator of" K '"and that of" K' "

The part "K '" "of the core" K "slides in the neck between the expansion / cooling nozzle" C2 "and the adiabatic expansion divergent" D "

2 "> o According to 1 application sought for the device and according to the temperatures of the gas to be compressed at the inlet of the intake chamber" C ", the new" K "can be made of carbon steel (temperatures below 300 °), stainless steel, steel cooled by internal circulation of cooling fluid, ceramic, or any other material having good resistance to abrasion and at the temperatures used

2 ^" ! 5 The embodiment shown in FIG. 2 3 shows a through shaft" K "and supported by a bearing placed in the intake chamber, and by a second bearing at the end of the stilling chamber" T ", the latter including a thread for adjusting the position of the novau and spray nozzles During the flow of the gas to be compressed in the expansion / cooling convergent "C2",

240 the free space between "K '" "and" C2 "constitutes a converging nozzle which fulfills the same role as the converging compression / cooling chamber" C2 "described in variant 1, the neck (ie the minimum passage section) of this converging nozzle is located slightly upstream of the outlet neck of "C2" and its section Ss can be modified at any time from the outside by adjusting the axial position of the core "K"

245 This adjustment of the section Ss at the neck, accompanied by an adjustment of the flow rate of the sprayed liquid, makes it possible to modify the flow rate of the fluid to be compressed, or else to modify the compression rate and the energy efficiency of the device by modifying the temperature for heating the gas at the inlet of the intake chamber The embodiment shown in FIG. 2 3 has the same performance as

250 the previous example concerning the basic case 1. with the following modifications allowing the flow rate and the compression rate of the gas to be adjusted to be adjusted -The diameter of the transition zone “N” becomes 0.45 m,

-The inlet and outlet diameters of the convergent expansion / cooling nozzle "C2" become 0.45m and 0.22m respectively,

255 -The inlet diameter of the divergent "D" becomes 0.22m,

-Rajout ^a kernel "K" stainless steel cooled by internal circulation of water maximum diameter of 0.3 m, minimum diameter O, lm at the output of "K", "and overall length 1.0m with position adjustment thread The example in Figure 2.4 also relates to a circular section device, the principle is

260 identical to that of variant 2 3, but here the core is installed downstream of the device

The device is equipped with a core "Kl" sliding axially in the areas "N" "C2" "D" and "T", and whose axis is fixed on a shaft passing for example one (or both) ) ends of the device, the axial position of the new "Kl" can be adjusted manually or automatically from the outside by a thread placed on a bearing, by an external veπn

265 or by any other external system

The spray nozzles are distributed in the “N” and “C2” zones. The other elements of the device are identical to those described in the basic version 1 The “Kl” core is a solid part of revolution whose aerodynamic profile makes it possible to minimize the pressure drops of the gas to be compressed, it consists of an upstream part “K l”

270 of increasing section in the direction of gas flow, of a downstream part "K '" 1 "of constant or decreasing section in the direction of gas flow, and of an intermediate part K' 1 including the generator continuous (without angle) ensures the link between the generator of "K 1" and that of "K '" l "The part" K' 1 "of the core slides in the neck compπs between the pressure vessel /

275 cooling "C2" and the adiabatic expansion divergent "D"

According to 1 application sought for the device and according to the temperatures of the gas to be compressed at 1 inlet to the intake chamber "C", the new "K l" can be made of carbon steel (temperatures below 300 °), steel stainless steel, in steel cooled by internal circulation of coolant, ceramic, or any other material with good resistance to

280 the abrasion and the temperatures used

The embodiment shown in FIG. 2 4 shows a shaft passing through the core “Kl” right through and resting on bearings placed in the intake chamber and in the stilling chamber, the latter including a thread for adjusting the position During 1 flow of gas to be compressed in zone "C2" 1 free space between

285 "K l" and the pipe "C2" constitutes a convergent nozzle which performs the same role as the converging cooling compression chamber "C2" described in the basic version 1 the neck (ie the minimum passage section ) downstream of this converging tuvere is generally located downstream of the exit neck of "C2", and its section Ss can be modified at any time from the outside by adjusting the axial position of the core "K l"

290 This adjustment of the section Ss at the neck, accompanied by an adjustment of the flow rate of the sprayed liquid, makes it possible to modify the flow rate of the fluid to be compressed, or else to modify the compression rate and the energy efficiency of the device by modifying the temperature for reheating the gas at the inlet of the intake chamber A. as an exemplary embodiment, the device represented in FIG. 2 4 has the same

295 performances as the example of realization concerning the basic case 1, with the following modifications making it possible to adjust the flow rate and the compression rate of the gas to be compressed -The inlet and outlet diameters of the convergent expansion nozzle / cooling "C2" becomes 0.60 m and 0.36 m respectively, -The diameter of the divergent inlet "D" becomes 0.36 m, and its length becomes 0.5 m ï o - Addition of a new "K »In stainless steel cooled by internal circulation of water with a maximum diameter of 0.35 m, a minimum diameter of 0.07 m at the inlet of“ K '”and at the outlet of“ K' ”with a total length of 10 m, supported by a 70 mm diameter shaft resting on bearings installed at “C” and “T”, with thread for adjusting its position -The spray nozzle system is identical to that of the example embodiment of the case of

"0 base 1 but the sliding tubes are housed in the support shaft of the new VA.RLANTE 3

A variant 3, concerning a supersonic flow in the cooling zone, is shown in FIG. 3, it makes it possible to improve the energy efficiency of the device as described in the basic version 1 by obtaining a large difference in temperature

"lo fluid between the inlet in the inlet chamber" C "and the cooling zone

The modifications compared to the basic version 1 concern on the one hand the use of the expansion convergent "C l" in which the fluid to be compressed is systematically expanded to the sonic pitch, and on the other hand the replacement of the parts "N" (transition zone) and "C2" (convergent expansion / cooling nozzle) by a divergent expansion nozzle

"1 supersonic" D l ", followed by a transition zone" NT "of a convergent cooling compression nozzle" C3 ", and of a converging adiabatic compression nozzle" C4 "(optional), the nozzle system spraying "R" identical to that of the version base 1 is installed in zone "C3" and possibly, as described below, in zones "D 1" and / or "NT" 20 The transition zone "NT" ensures a continuous connection between the ends of " D l "and" C3 "with a generator with monotonous slope, and without angle

The other elements of the device are identical to those described in the basic version l The fluid to be compressed is heated upstream of zone "C" to a temperature which can greatly exceed 1000 to 1500 ° C, then expanded throughout the "C l" and "Dl" zones which

"25 is a converging / diverging expansion nozzle supersonic (sonic velocity at the neck) ^until a pressure Pa one Go speed and a temperature Ta, and finally pressed (temperature elevation) in the converging tuvere cooling compression" C3 " with, simultaneously in the same nozzle “C3”, removal of heat by evaporation of pulverized liquid, the convergent adiabatic compression nozzle “C4” allows to bring back the fluid

"30 at sonic speed before its subsonic adiabatic compression in the divergent adiabatic compression" D "and its evacuation

The spraying system consists of a series of nozzles whose positions and / or flow rates can be adjusted manually or automatically from the outside, according to the same concept as in basic version 1, the evaporation of the droplets sprayed

"" 5 of heat) can be carried out in the zone "Dl" (cycle approaching an isobaric cooling), but this case presents little practical interest we will not mention in the continuation of the description that the withdrawal of heat carries out in the “NT” or “C3” zones (cycle approaching an isothermal transformation), the spray nozzles being distributed in the “C3” zone and possibly, in advance, in the “NT” transition zone (to hold

"ι40 counts the time lag between spraying and evaporation)

The theoπque energy efficiency of the device is higher the higher the temperature of the gas to be compressed at the entry of "C" and the lower the expansion temperature Ta, the latter remaining however higher than the saturation temperature Ts gas vis-à-vis the sprayed liquid (the temperature difference DT = Ta-Ts being necessary for 1 evaporation of the

"45 liquid sprayed at the entry of zones" NT "and" C3 ") in the particular case where Ta is less than Ts, the evaporation of the sprayed liquid (and therefore the removal of heat from the gas to be compressed) will not begin in "C3" that when, under the effect of compression, the actual temperature of the gas will have exceeded its saturation temperature Evaporation of the sprayed liquid and the removal of heat in the "NT" and "C3" zones

"50 will be all the more rapid the smaller the spray droplets and the higher the temperature difference DT = Ta-Ts, with the direct consequence of a reduction in the length of" C3 "and a reduction in the pressure drop gas to be compressed through "C3" in practice, droplet sizes of the order of 5 to 30 μm, and temperature differences DT = l a-Ts of the order of 10 ° C to 100 ° C , lead to dimensions of the

"ô5 device and has gas pressure losses through" C3 "quite acceptable

The dimensioning of the device obviously depends first of all on the flow rate and the characteristics of the gas to be compressed, as well as on the outlet pressure sought for these criteria. being fixed, the choices are the temperature of gas reheating upstream of “C”, the expansion rate through “C l” and “C2” (and therefore Pa, Va, Ta), and the dimensions of the droplets "60 the result ^of a compromise between the standard equipment available in the market (various types of spray nozzles, materials), the dimensions and the price of the device and its energy efficiency as an example embodiment, a compressor of air constitutes of a device according to the figure

3 makes it possible to compress from 1 bar A to 1.5 bar At nearly 20,000 Nm3 per hour of air, from the ^" 565 following elements

-An air intake with an internal diameter of 0.47 m made of carbon steel coated internally with refractory concrete with a primary starting compressor capable of developing an overpressure of 500 mbar and a burner operating on natural gas and allowing to heat up. 370 -one inlet chamber "C" with a diameter of 0.97 m and a length of 1.16 m,

-a converging subsonic expansion nozzle “C l” with a diameter at the neighboring neck of 0.295 m, and a length of 0.670 m, -a diverging supersonic expansion nozzle “Dl” with a neighboring inlet diameter of 0.295 m with a neighboring outlet diameter 0.388 m, and 0.2 m long in which the air is relaxed 375 up to 0.1 bar A at around 370 ° C and 1160 m / s,

-a converging compression / cooling nozzle “C3” and a converging adiabatic compression nozzle “C4” with an inlet diameter close to 0.388 m, a diameter at the nearby neck of 0 209 m, and a length of 1 m, -a divergent adiabatic compression "D" with an inlet diameter of 0.209 m, an outlet diameter of 80 near 0.7 m, and a length of lm,

-a tranquilization chamber "T" with a diameter of 0.7 m and a length of 0.84 m,

- a system of ultrasonic spray nozzles with compressed air assistance, capable of spraying 1.22 kg per second of water, with a droplet diameter close to 5 μm, - a heat exchanger for cooling the compressed air at the outlet of "T", and from 385 reheat the air before it enters "C" to nearly 480 ° C

The intake chamber "C" is made of carbon steel coated internally with refractory concrete, while "Cl", "Dl", "C3", "C4", "D", and "T" are made of steel carbon double casing cooled by a flow of ^air to be compressed prior to its entry to the air suction, the spray nozzles has ultrasound, installed on (and supplied by) 90 sliding tube system concentπques steel carbon with an outside diameter of 40 mm passing through the intake chamber, are distributed in "C3" VARL NTE 4 A variant 4, also concerning a supersonic flow, is shown in the figure

4, it derives from variant 3 and allows to simplify the design by replacing the system 395 of spray nozzles distributed along ^the axis of the device by a single axial nozzle or radial nozzles, PLACED (s) has the entry of the “C3” zone or in the “NT” transition zone (the latter arrangement making it possible to anticipate the time difference between spraying and evaporation of the injected liquid), the flow rate and the axial position of these nozzles can be adjusted manually or automatically from outside the device The other elements of the device are identical to those described for variant 3

FIG. 4 represents an exemplary embodiment with a single nozzle situated on the axis of the device at the end of a shaft passing through the intake chamber, and the flow rate and the position of which can be adjusted (manually or automatically) a from the outside, FIG. 4 1 represents another example of embodiment with several axial nozzles of the same type, and FIG. 4 2 represents a third example of embodiment with nozzles with adjustable flow rate arranged on radial fins. The example of the figure 4, which is the most practical, will be mentioned alone in the rest of the description

In this variant, the entire flow rate of sprayed fluid is injected at the start of the heat removal cycle, in the “NT” zone or at the inlet of “C3”. The gas to be compressed is quickly saturated at the inlet of “ C3 "by the evaporation of part of the droplets, the rest of the droplets remaining in suspension in the gas flow, as it advances in the compression / cooling nozzle" C3 ", the gas is compressed with rise in its temperature and distance from the previous state of saturation, which allows the additional vaporization of droplets, this continuous equilibrium makes it possible to extract heat from the gas to be compressed throughout the zone "C3" or until total evaporation of the droplets injected, and this while maintaining the gas to be compπmer in a state very close to its saturation along the axis of "C3" at each point of this axis, the difference in temperature DT between the actual temperature of ga z and its saturation temperature will balance to its minimum, depending on the size of the droplets and the coefficients of heat exchange and gas diffusion, variant 4 therefore makes it possible to optimize the thermodynamic cycle of the device by maintaining the cold source a the minimum temperature compatible with the process

By way of example of an embodiment, the device represented in FIG. 4 has the same elements and has the same performance as the example of embodiment of variant 3 except for the replacement of the spray nozzle system by an axial nozzle. unique VARIANT 5

A variant 5, concerning a supersonic flow, follows from variants 3 or 4 and makes it possible to adjust at any time the flow rate of the gas to be compressed, the compression rate, and the energy efficiency of the device, in this variant, the convergent "Cl" and the divergent "D l" of variants 3 and 4 are replaced by a converging nozzle followed by a diverging nozzle both with variable geometπes, which makes it possible to adjust the section of the neck included between these two nozzles, the geometry system variable, control from outside the device is obtained by any mechanism making it possible to modify the pass section of the neck between “C l” and “D l” such as those described in the examples below In the example of the Figure 5, the variable geometry system is obtained by replacing “C l” and “D l” with a converging nozzle “CG” with variable geometry followed by an optional transition zone “NT1” then a separate nozzle "DG" manager with variable geometry, also the three with deformable walls so as to modify the section of the neck between the two nozzles the deformable wall system can be of the same type as that described in chapter 2 1 and represents in Figure 2 1 for example According to the conditions of use of the dispositi the nozzle “DG” can be equipped with a system of variable geometry also allowing it to be slightly convergent, in order to facilitate the commissioning of the device under subsonic conditions

The transition zone "NT 1" ensures a continuous connection between the ends of "CG" and "DG" with a generator with a monotonous slope, and without angle The speed of the gas to be compressed must be sonic in the first neck of the device (and in the second as far as possible), the ability to change its section to make it independent ^of one another, the temperature and the gas flow to compress the output of the intake chamber, while respecting the constraint sonic flow in this neck this makes it possible to modify either the flow rate of the gas to be compressed, or its temperature at the inlet of the first neck (and possibly the flow rate of sprayed liquid, which results in a modification of the compression ratio of the device and of its efficiency), ie both simultaneously The other elements of the device are identical to those described in variants 3 or 4 In the preferred example of figure 5.1, the zone "D l" (divergent nozzle of supersonic expansion) of variants 3 or 4, is replaced by an adjustable system consisting of an optional transition zone "NT '" followed by a slightly divergent "N2" conduit preferably with the addition of a profile core "K2" sliding axially in the subsonic expansion convergent "C 1", in the transition zone "NT '", and in the conduit "N2", the core is fixed on a shaft passing for example one (or both) ends of the device, the axial position of the core "K2" can be adjusted manually or automatically from outside the device by a thread placed on a bearing, by an external veπn, or by any other system allowing it

The spray system can be housed in the "NT" zone, in the "C3" zone or at the downstream end of "K '" 2 "(see below). The" K2 "core is a part whose aerodynamic profile allows to minimize the pressure drop of the gas to be compressed, it consists of an upstream part "K'2" of constant or increasing section in the direction of flow of the gas, of a downstream part "K '" 2 "of decreasing section in the direction of gas flow, and an intermediate part "K" 2 "whose continuous generator (without angle) ensures the link between the generatπce of" K'2 "and that of" K '"2 »The part" K '"2" of the nucleus "K2" is housed in the convergent subsonic expansion "C l" in the transition zone "NT" ", and in the conduit" N2 "

According to 1 application sought for the device and according to the temperatures of the gas to be compressed at the entry of the combustion chamber "C", the core "K2" can be made of carbon steel (temperatures below 300 °), steel stainless steel, cooled by internal circulation of cooling fluid, ceramic, or any other material having good abrasion resistance and at the temperatures used

The embodiment shown in Figure 5 1 shows a new "K2" supported by a shaft which passes axially, resting itself on a bearing placed in the room intake including a position adjustment thread, in this example, a single spray nozzle is installed at the downstream end of the part "K '" 2 "of the core" K2 "

480 During the flow of the gas to be compressed in the expansion convergent "C l", the free space between "K'2" and "C l" constitutes a converging nozzle of subsonic expansion which performs the same role as the convergent subsonic expansion nozzle "C l" of variants 4 or 5 and the free space between "K '" 2 "," NT' ", and" N2 "constitutes a diverging supersonic expansion nozzle which ensures the same role as the nozzle "D l" of variants 3

485 or 4, the neck (that is to say the minimum passage section) between these two nozzles of FIG. 5 1 is generally located between the maximum section of "K2" and the outlet section of "C 1" and its section S's can be modified at any time from the outside by adjusting the axial position of the core "K2" Depending on the conditions of use of the device the conduit "N2" can be slightly

490 converge, in order to facilitate the commissioning of the device under subsonic conditions. As an example of an embodiment, a device according to FIG. 5 1 has the same performances as the example of embodiment concerning variant 4, with the following modifications allowing to adjust the flow rate and the compression rate of the gas to be compressed - Replacement of the supersonic expansion divergent "Dl" by a transition zone "NT '"

495 and a divergent duct “N2”, the assembly having an inlet diameter close to 0 295 m, an outlet diameter close to 0.388 m, and a length of 0.2 m, the air there being expanded to 0 , 1 bar A, the transition zone "NT '" and the diverging part "N2" are made of carbon steel with a double jacket, - Addition of a core "K2" of stainless steel cooled by internal circulation of water of diameter

500 maximum 0.293 m, minimum diameter 0.04 my entry of "K'2" and at the exit of "K" 2 "of total length 0.9 m, supported by a 40 mm diameter shaft resting on an installed bearing at "C", with thread for adjusting its position -The spray nozzle is identical to that of the embodiment of variant 4 but the sliding tube allowing it to be supplied with water is housed in the support shaft of the novau K_2

505 VARIANT 6

A variant 6, concerning a supersonic flow, follows from the variants 3 or 4 decπtes above and also makes it possible to modify at any time the compression ratio and / or the yield of the device (just like variant 5), it allows by elsewhere to suppress or move to the output of the device any pressure waves or shock waves which may in some cases develop in the zones "D 1""NT", or "C3" of variants 3 or 4, the principle of this variant is identical to that of variant 5, but the variable geometry concerns the second neck of the device, in this variant, the zones "C3""C4" and "D" of variants 3 and 4 are replaced by a system a control variable geometry from ^outside the device and for modifying the section of the neck between "C3" and

515 “D” the variable geometry system is obtained by any mechanism allowing the section of this neck to be modified, such as those described in the examples below. In the example of FIG. 6, the variable geometry system is obtained by replacing "C3""C4" and "D" by a nozzle <CGI "with deformable walls which can be adjusted to be preferably slightly divergent during the commissioning of the device then

520 converging thereafter (this nozzle then acting as convergent expansion / cooling nozzle “C3” and converging adiabatic compression nozzle “C4”), followed by a diverging nozzle “DG1” with deformable walls also, the nozzle “ DG1 "then acts as a divergent adiabatic compression nozzle" D "The system of deformable walls can be of the same type as that described in chapter 2 1 and represents in the figure

525 2 1 for example

The speed of the gas to be calculated should preferably be sonic in the second neck of the device, this possibility of modifying its section makes it possible to make the temperature, the pressure independent, and the flow of the gas compressed at the outlet of the convergent of adiabatic relaxation while respecting the sonic flow constraint in this neck, this allows

530 modify either the flow rate of the gas to be compressed or its temperature at the inlet of the second neck (by modifying the temperature in “C” or by modifying the flow rate of sprayed liquid, which results in a modification of the compression ratio of the device and of its output), or both simultaneously Finally, when the dispositi is put into service, the first nozzle with variable geometry is

535 maintained in a slightly divergent position, until the compression ratio of the device is high enough for the pressure wave which can develop in "D 1" to have moved into the second divergent nozzle "DG" after this discharge of one pressure wave, the two nozzles has variable geometπe can gradually take their operating position, the pressure wave ^moving away toward the outlet of the device as the

540 two variable geometry tuveres approach their service position

The other elements of the device are identical to those described in variants 3 or 4 In the preferred example of figure 6.1, the convergent compression / cooling nozzle “C3” and the convergent adiabatic supersonic compression nozzle “C4” of variants 3 or 4 are replaced by a slightly divergent "N3" conduit preferably

545 with an inlet diameter slightly greater than that of "D l" preferably inside which can slide axially a profile core "K3" fixed on a shaft passing for example one (or both) ends of the device and allowing to adjust the position of "K3" the position of the core "K3" can be adjusted manually or automatically from outside the device by a thread placed on a bearing, by a veπn, or by any other

55o external system allowing it

The spray nozzle is housed in the "NT" or "N3" zone

In a more simplified concept, the divergent duct “D” and possibly the plenum “T” can simply be formed by an extension of the slightly divergent duct “N3”

555 The other elements of the device are identical to those described in variants 3 or 4 The core "K3" is a part whose aerodynamic profile makes it possible to minimize the pressure losses of the gas to be compressed, it is made up of an upstream part "K '3" of increasing section in the direction of gas flow, d 'a downstream part "K'" 3 "of constant or decreasing section in the direction of gas flow, and an intermediate part K" 3 whose continuous generator 560 (without angle) provides the link between the generator of " K '3 "and that of"K'"3" The part "K'3" of the core "K3" is housed in the conduit "N3"

Depending on the application sought for the device and according to the temperatures of the gas to be compressed at the outlet of the supersonic expansion divergent "D l", the core "K3" can be made of carbon steel (temperatures below 300 °), steel stainless steel, cooled by internal circulation 565 of coolant, ceramic, or any other material having good resistance to abrasion and to the temperatures used

The embodiment shown in Figure 6 1 shows a shaft passing through the core "K3" right through and resting on bearings placed in the intake chamber and in the stilling chamber, the latter including an adjustment motor position, the spray nozzle 570 is placed at the end of a sliding tube on the shaft

During the flow of the gas to be compressed in the pipe "N3", the free space between "K'3" and the pipe "N3" constitutes a converging nozzle which performs the same role as the converging cooling compression nozzle " C3 "and the convergent supersonic adiabatic compression nozzle" C4 "of variants 3 or 4, and the free space comprised 575 between" K '"3" and "D" constitutes a diverging nozzle which performs the same role as the converging nozzle of adiabatic compression "D" described in variants 3 or 4, the neck (ie the minimum passage section) between these two nozzles is generally located between the outlet of the duct "N3" and the maximum diameter of "K" 3 », And its section Ss can be modified at any time from the outside by adjusting the axial position of the core« K3 », this 580 adjustment of the section at the neck allows

During commissioning, completely remove the core "K3" from the pipe "N3" so that the initial pressure wave, which can develop in supersonic regime in a diverging nozzle when the overpressure provided by the primary compressor starting point is sufficiently high, is located downstream of the outlet of the duct "N3", this 585 overpressure and the maximum diameter of "K3" are selected so that, when the core "K3" is gradually introduced into the duct "N3", the area where the pressure wave is always remains divergent and the pressure wave is stationed there until "K3" finds its final place in "N3"

During normal operation, making the temperature 590 the pressure independent of each other, and the flow rate of the gas to be compressed at the outlet of the second neck, which gives the device the same advantages as those of the example of the Figure 6 (possibility of adjusting the flow rate, compression ratio, or efficiency) By way of example of an embodiment, a device according to FIG. 6 1 has the same performances as the example of embodiment concerning variant 4, the following modifications 595 making it possible to adjust the flow rate and the compression rate of the gas to be compressed

-Replacement of the converging nozzles “C3” and “C4” by a pipe “N3”, having an inlet diameter close to 0.388 m, an outlet diameter close to 0.390 m, and a length of 1.0 m, the pipe "N3" is made of double-walled carbon steel, - Replacement of the divergent "D" with an inlet diameter of 0.209 m by a divergent "D" of 600 with the same design but with an inlet diameter of 0.390 m,

- Addition of a “K3” stainless steel core cooled by internal circulation of water with a maximum diameter of 0.388 m, a minimum diameter of 0.04 m at the inlet of “K'3” and at the outlet of “K '” 3 ” total length 1.2 m, supported by a 40 mm diameter shaft resting on a bearing installed at “T” (with thread for adjusting its position) and on a second bearing installed at 605 at the end of “C”,

-The spray nozzle is identical to that of the embodiment of variant 4, but the sliding tube enabling it to be supplied with water is housed in the support shaft of the core "K3" VARIANTE 7 610 A variant 7, for supersonic flow, resuite of simultaneous application of the variants 5 and 6 on the same device, and to adjust from the exteπeur ^{independently} of one another and at any time the sections of two necks of the device and therefore to modify the air flow (or gas) to be compressed, the compression rate of the device, and its energy efficiency, while also allowing to suppress or move towards its output any 615 pressure waves or shock waves can in certain cases develop in the supersonic divergents of variants 3, 4, or 5, in this variant, the zones “C3” “C4” and “D” of variant 5, are replaced as for variant 6 by a nozzle a geometπe v ariable can be set to be slightly divergent when the device commissioning then converges thereafter, followed by ^a divergent nozzle has variable geometry O2O the diameter of the neck between the two nozzles can continuously adapt to the diameter of the first neck of the device (that is to say at the flow rate and at the physical conditions of the gas to be compressed on intake) and at the physical conditions at the outlet of the device (that is to say at the flow rate of liquid sprayed, therefore at the compression ratio and device performance)

The other elements of the device are identical to those described in variants 5 625 this variant therefore has the combined advantages of variants 5 and 6

In the example of FIG. 7, the systems of variable geometry are obtained by the use of tuveres with deformable walls of the same type as that described in Chapter 2 1 and represented in FIG. 2 1 for example

In the preferred example of FIG. 7.1, the convergent compression / cooling nozzle 630 “C3” and the convergent adiabatic supersonic compression nozzle “C4” in FIG. 5 1 are replaced by a duct “N3” preferably slightly divergent with an inlet diameter slightly larger than that of "D l" preferably, inside which can axially slide a core “K3” whose axis is fixed on a shaft passing for example one (or both) ends of the device, the axial position of the core “K3” can be adjusted

635 manually or automatically from outside the device by a thread arranged on a bearing, by an external veπn, or by any other external system allowing it In a more simplified concept, the zones "N2", "NT", " N3 "," D "and" T "can be grouped into a single duct of slightly divergent section The core" K3 "is a solid part of revolution whose aerodynamic profile allows

640 minimize pressure losses of the gas to be compressed, it consists of an upstream part "K'3" of increasing section in the direction of gas flow, of a downstream part "K '" 3 "of constant section or decreasing in the direction of gas flow, and an intermediate part K "3 whose continuous generator (without angle) provides the link between the generator of" K'3 "and that of" K '"3"

645 The part “K'3” of the core “K3” is housed in the conduit “N3”

The spray nozzle is housed in one of the “N2”, “NT”, or “N3” zones between

"K '" 2 "(downstream end of" K2 ") and" K'3 "(upstream end of" K3 ")

The other elements of the device are identical to those of variant 5

Depending on the desired application for the device and according to the temperatures of the gas to be compressed in

650 outlet from the supersonic expansion divergent "Dl", the core "K3" can be made of carbon steel (temperatures below 300 °), stainless steel, steel cooled by internal circulation of cooling fluid, ceramic, or in any other material having good resistance to abrasion and to the temperatures used. The embodiment shows in FIG. 7 1 shows a shaft passing right through the

655 novau "K2" and the core "K3", and resting on bearings placed in the combustion chamber and in the stilling chamber, each bearing includes a motor for adjusting the axial position of each of the cores, and the nozzle spraying is installed directly on the downstream end of "K '" 2 "As in the example in Figure 5 1, the free space between" K2 "" C 1 "," NT "and o6o" N2 "has a first neck of section S's adjustable from the outside by adjusting the axial position of the core "K2"

Similarly, as in the example in FIG. 6 1, the free space between "K3" "N3" and "D" comprises a second neck of section Ss adjustable from the outside by adjusting the axial position of the "K3" core

665 These possibilities of adjustment of the section of each neck give 1 example of FIG. 7 1 the combined advantages of the examples of FIGS. 5 1 and 6 1 decπts above As an exemplary embodiment, a device according to FIG. 7 1 making it possible to compress nearly 20,000 Nm3 of air from 1 bar A to 2.5 bir A- and making it possible to adjust the flow rate and the compression rate of the gas to be compressed, can be obtained by making the following modifications to the embodiment of variant 5

-Replacement of "NT '" and "N2" by a divergent nozzle of the same inlet diameter but of length 1 5 m and of outlet diameter close to 1.034 m, making it possible to relax the air to 0 004 bar A -Replacement converging nozzles “C3” and “C4” via a pipe “N3”, having an inlet diameter close to 1.034 m, an outlet diameter close to 1.036 m, and a length of 2.07 m, the pipe “N3” is made of double-walled carbon steel, -Replacement of the divergent "D" with an inlet diameter 0.209 m by a divergent "D" of the same design but with an inlet diameter equal to 1.036 m, with an outlet diameter equal to 1,176 m, and length 2.0 m, - Replacement of the "T" chamber with a chamber of the same design, but with a diameter of 1,176 m and a length of 1.41 m, - Addition of a "K3" core »In stainless steel cooled by internal circulation of water with a maximum diameter of 1,034 m, a minimum diameter of 0.06 ma entry of“ K'3 ” and at the outlet of "K '" 3 "of total length 3, 1 m, supported by a 60 mm diameter shaft resting on a bearing installed in a" T "(with thread for adjusting its position), on a second bearing installed at "C" and on a third intermediate bearing, -The spray nozzle is of identical design to that of the embodiment of variant 4, but the flow of water spray is reduced to 1.0 kg per second and the nozzle is fed by a sliding tube housed in the support shaft of the core "K3" VARIANT 8

A variant 8, concerning the spray nozzles of the basic option 1 or of the variants 2 to 7 described above, is shown in FIG. 8, it consists in using as spraying fluid part of the compressed air (or gas) generated by the device or steam generated by heat recovery from the compressed gas downstream of the still chamber This variant makes it possible to reduce the size of the droplets of liquid spray and increase their speed initial without additional external mechanical energy, and therefore improve the energy efficiency of the device

The example of FIG. 8 relates to the same type of installation as that of FIG. 7 1, but it is equipped with assistance with spraying from compressed air taken at the outlet of the device.

\ as an example of an embodiment, a device according to FIG. 8 making it possible to compress nearly 20,000 Nm3 of air from 1 bar A to 2.5 bar A, and making it possible to adjust the flow rate and the compression rate of the gas to compress, can be obtained by making the following modifications to the embodiment of variant 7 - The outlet diameter of "C l" becomes 0 322 m -Replacement of "NT '" and "N2" by a divergent nozzle of the same design but with an inlet diameter of 0.322 m, an outlet diameter of 1.042 m, and a length of 1.439 m allowing the air to be relaxed to 0.004 bar A - Replacement of conduit “N3” with a new conduit of the same design but

710 inlet diameter close to 1.042 m, outlet diameter close to 1.044 m, and length 2.086 m -Spraying is assisted by the use of 0.26 kg / second of “compressed air-vapor” mixture sampled at the outlet of the device - The flow of water spray is reduced to 0.61 kg / second

715 -Replacement of the core “K3” by a new core of maximum diameter 1043 mm, minimum diameters 137 mm at the ends of “K'3” and “K '" 3 ", and of length 3 1 m, supported by a shaft diameter 140 mm al ^inside which circulates the spray water and assist air to the spray 9 vARIANT

720 A variant 9, concerning the spray nozzles of the basic option 1 or of the variants 2 to 8 described above, is shown in FIG. 9, it consists in reheating the liquid used in the spray nozzles before its introduction in the nozzles, by using the heat recovered from the compressed gas downstream of the stilling chamber "T" (recovery possibly going as far as condensation of the vapor of liquid spray), during

725 the expansion of the liquid to be sprayed, this overheating makes it possible to reduce the size of the droplets and to increase their initial speed by minimizing the supply of external mechanical energy, and therefore improving the energy efficiency of the device

If necessary, failing this or in addition to this heat recovered downstream from the stilling chamber, any other internal heat source (heat recovered in the double "o envelopes") or external to the device can be used

The example of FIG. 9 relates to the same type of installation as that of FIG. 8 in which the liquid to be sprayed is previously heated in a heat exchanger installed on the discharge line of the compressed gas. As an example of embodiment, a device according to FIG. 9 having the same

735 dimensions and the same performance as ^the embodiment of the variant with 8 in addition an air outlet temperature compresses increased by 20 ° C, can be obtained by adding the drain line heat exchanger "E '1 ”to preheat VARIANTE 10 spray water to 40 ° C

740 A variant 10 relates to the installation in parallel or in series of several of the devices described in basic option 1 and variants 2 to 9 in order to facilitate its realization, to achieve compression ratios which cannot be achieved by a single device, to improve the overall yield of 1 installation, or to facilitate the commissioning of the installation, the devices can be distinct from each other as in the example of FIG. 10 described below. after or

745 nested one inside the other as in 1 example of figure 10 1 which relates to two devices installed in parallel in the same enclosure, or as in the examples in FIGS. 10 2, 10 3 and 10 4 or two devices according to claims 2 and 9 are installed in series and nested one inside the other with line of suction, intake chamber “C”, converging “C l” and “C2” and common inlet core acting as core “K” for the first 50 subsonic device and core “K2” for the second supersonic device L example of FIG. 10 allows the commissioning of a supersonic air compression device with high compression ratio, using an inefficient starting compressor It consists of two separate devices installed in series one first sonic device according to FIG. 2 3 with upstream core allowing an adjustment of air flow and whose

755 suction line includes a filter, silencer, compressor, and an oil burner followed by a supersonic downstream device according to FIG. 9 with upstream and downstream novals, the suction line of which includes an air heat exchanger at l using a thermal fluid, the discharge line of the downstream device includes a recovery exchanger allowing to heat the thermal fluid followed by a second recovery exchanger allowing to heat 1 water of ⁿ βo spraying

The first upstream device is only used during the commissioning of the installation, to ensure sufficient overpressure to allow the start of the second device, after which the first is stopped The second downstream device (according to FIG. 9), use in normal operation and therefore must be

765 efficient, additionally includes a heat recuperator for heating the air at the intake, a second recuperator for heating the spray water, and assistance with spraying using compressed air taken from the outlet 'installation The example in Figure 10.1 allows the realization of a compressor of very large capacity by the use in parallel of two devices identical to that shown in Figure 8, both

77o devices installed in parallel are nested one inside the other, the cores of each of them being installed in a common envelope, this arrangement makes it possible to reduce the dimensions of the cores, which would become too large on a single device of very large capacity The example in figure 10.2 is a simplified version of the example in figure 10 in which

7 "5 the two devices are nested, it consists of a supersonic device according to FIG. 9 in which the conduits" N2 "," NT "" N3 "and" D "are grouped in a single slightly diverging conduit, and in which the zone “C l” can play the role of the zones “C l” and “C2” of the sonic device represented in FIG. 2 3, the novel “K2” of the supersonic device comprises spray nozzles distributed throughout its axis, and can play the role of the 80 core “K l” of the sonic device represented in FIG. 2 3

When the installation is put into service, the new "K3" is completely withdrawn in the still chamber "T", the compressor, the burner, and the spray nozzles of the new "Kl" are put into service, and the part only upstream of the device is used, as a sonic installation when the pressure downstream of "C2" is sufficiently high, the

⁷ 85 compressor is stopped the downstream supersonic part of the device is also switched on and when the pressure in the stilling chamber is sufficiently high, the atomizing nozzles of the core “K1” (that is to say those of the sonic device) are gradually stopped the entire installation then operates as a supersonic device alone, and settings for flow rate, compression ratio, and installation efficiency can be

790 perform by adjusting the burner, the flow rate of liquid sprayed, and the positions of "K2" and "K3"

The example in Figure 10.3 is also a simplified version of a sonic device ιmbπ.; Eu in a supersonic device to facilitate commissioning it consists of a supersonic device according to Figure 7 with variable geometπe nozzles by walls

795 deformables in which the convergent "CG" of the supersonic device can play the role of the convergent "C l" and "C2" of the sonic device represented in FIG. 2 3 the convergent "CG" of the supersonic device comprises in addition spray nozzles "R" distributed along its axis, which play the same role as the spray nozzles distributed in the area "C2" of the sonic device

800 When the installation is put into service, the “CGI” pipe is put in the “start” position, slightly divergent, the compressor, the burner, and the spray nozzles of the sonic device are put into service, and the part only upstream of the device, as a sonic installation, when the pressure downstream of "C2" is sufficiently high, the compressor is stopped, the downstream supersonic part of the device is also put into service and

805 when the pressure in the stilling chamber is sufficiently high, the sonic device's spray nozzles are also gradually stopped, the entire installation then operates as a supersonic device alone, and the flow rate adjustments compression rate, and installation efficiency can be achieved by adjusting the burner, the flow rate of liquid sprayed, and the sections of each of the two necks of the device

810 The example of figure 10.4 allows, in a very simplified way, to obtain the same result as the examples of figures 10 and 10 2, that is to say that it allows the putting into service of a compression device supersonic air with high compression ratio, using a low-performance starting compressor, it consists of a supersonic device according to FIG. 8 and a sonic device according to FIG. 2 4 installed in series and nested one in the other

815 In this installation, the conduits “NT '”, “N2” “NT” and “N3” are combined into a single weakly converging conduit, and the new “K3” and the spray nozzle “R” of the supersonic device are also used as the core “K l” and as the nozzle “R” of the sonic device when the latter is used During the commissioning of the installation, the sonic device is only used (the new “K2”

820 is then entirely withdrawn in “C”) until a sufficient pressure gain is obtained to allow the commissioning of the supersonic device (that is to say the introduction of “K2” in “C l” for create a divergent)

As an example of an embodiment, a device according to FIG. 10 2 making it possible to compress nearly 20,000 Nm3 of air from 1 bar A to 2 5 bar A-, and making it possible to adjust the flow rate and the rate of

825 compression of the gas to be compressed, can be obtained with a starting compressor developing an overpressure of KO mbar only, making the following modifications to the embodiment of the van ιnt3 ij

-The convergent “C l” is replaced by a convergent of the same design (fulfilling the role of “C l” vis-à-vis the supersonic functioning and of “C l” + “C2” vis-à-vis the 830 functioning sonic), with the same inlet and outlet diameters, but 1.5 m long

-Replacement of the input core “K2” by a new core (fulfilling the role of “K2” vis-à-vis the supersonic operation and “K” vis-à-vis the sonic operation) of the same diameters but length total 1.3 m, its downstream part "K '" ", which slides in" C l ", has on its periphery the spray nozzles necessary for sonic 835 operation

INDUSTRIAL APPLICATIONS OF THE INVENTION

The device according to the invention finds its applications in industrial processes using compressed gases, compressed air, or water vapor, with particular interest with regard to thermoelectric power plants (see examples 5, 6, 7, 8, and 9 below (840 below), it allows for example the following installations to be carried out with equipment costs, maintenance costs, and competitive energy yields

1 - Installations for the production of compressed air or gas intended to meet industrial needs and making it possible to generate very high flow rates (from 1000 Nm3 / ha to several million Nm3 / h), at pressures between 1.5 barA and 20 bar A, see beyond 845 2-Vacuum systems implementing large air or gas flow rates to meet the needs of industrial processes, the needs of thermodynamic test benches (Aeronautics, Air conditioning, etc.)

3-Use of the residual heat of the fumes in power boilers to achieve the partial vacuum of their combustion chambers, which avoids the permanent use of 50 draft fans and saves several hundred or thousands of kW of electric energy

4- mechanical recompression of steam at low pressure (water vapor for example, the injected liquid then being water) to obtain steam at higher pressure, in this example the suction line comprises if necessary an exchanger thermal enabling 55 low pressure steam to overheat

5-Thermoelectric steam power stations in which the high pressure steam boilers would be replaced by the same device as that described in the previous example, in such power stations, the recomprtmee steam is superheated and then expanded through turbines before be returned to the input of the device, the steam condensers no longer being 860 necessary except for condensing at low temperature a flow of steam equal to the flow of water injected into the device. In such plants, the hot source of the thermodynamic cycle, close to 500 to 700 ° C, is much higher than that of conventional power plants (250 ° C to 3 10 ° C, corresponding to the boiling of steam at 40 to 100 bar), and therefore allows significantly higher energy yields , which can exceed 45% 865 6-Thermoelectric power stations with gas turbines, in which a device according to FIG. 9 for example but without a burner, installed on the smoke circuit downstream of the turbine, uses the latent heat of the smoke to recompπmer part of the smoke before reinjecting them downstream of the compressor of the gas turbine, making it possible to reduce the flow rate and therefore the power consumed by this compressor, such a cycle makes it possible, for example, to wear

870 27% to almost 45% the efficiency of a gas turbine, with of course the appropriate adaptations 7-Thermoelectric power stations with gas turbines, in which a device according to FIG. 9 for example but without a burner, is installed on the smoke circuit downstream of the turbine, uses the latent heat of the smoke to create a vacuum to improve the power of the turbine

875 gas, such a cycle also allows to increase from 27% to almost 45% the output of a gas turbine, with of course the corresponding adaptations of the 8-power thermoelectric turbine using the compression cycle of the dispositi and consist for example of the device of Figure 10 plus 1 with a turbine air "TB" installed downstream of the burner of the ^suction line and air-steam turbines installed on the line

880 evacuation, such a cycle makes it possible to achieve yields greater than 56%, taking into account the various losses of the system heat losses, pressure losses of the device friction losses, isentropic efficiency of the tubine, etc. 9- Thermo power stations -electnques using the compression cycle of the dispositi and constituted for example of the device according to FIG. 10 1 without burner "B" on the suction line, but with

885 a burner and an air-steam turbine installed on the evacuation line upstream of the exchanger "E '1" such a cycle makes it possible to achieve yields greater than 60%, taking into account the various losses of the system losses thermal, pressure drop of the device friction losses, isentropic efficiency of the tub, etc.

890

Claims

895

1) Device for compressing air or any gas which is characterized in that it comprises the following elements intended to pre-treat the gas to be compressed and to supply it with thermal energy if its temperature is not high enough, to relax the latter at a subsonic or sonic speed through an expansion nozzle, to take a heat sample

900 at high speed and low temperature by controlled spraying (and evaporation) of liquid distributed in an expansion-cooling nozzle (the nozzle allowing to maintain a high speed), and finally to recompπmer this gas in an adiabatic compression nozzle in order to bring back its speed has a normal flow value a suction line including if necessary additional equipment such as suction filter "F", silent

905 "S", primary compressor "CP", heat exchangers "El", "E2",, "En", burner

“B”, and expansion turbine “TB”, an optional Admission Chamber “C”, a Converging of Relaxation “Cl” allowing to increase its speed up to the sonic speed possibly, a Transition Zone “N” optional, a Converging Cooling Expansion Nozzle “C2”, a Cooling System “R” consists of a set of nozzles for spraying water (or other liquid) with adjustable flow and / or position from the extender of the device and distributed along the zones “N” and “C2”, an Adiabatic Compression Divergent “D” intended to compress the gas by reducing its speed to a normal flow speed, a Tranquilization Chamber “T "(Optional) and an Evacuation Line including if necessary additional equipment 15 such as hot gas recycling systems," E '1 "recovery exchangers,

"E'2",, "E'n", and Silent "S '", this equipment being able to be supplied only by a part of the compressed gas, and being able to be installed downstream of a burner and a turbine if the device is intended for the production of mechanical or electrical energy

2) Device according to claim 1 caracteπse in that the zone "C2" (expansion nozzle / cooling 20) and zone "D" (divergent adiabatic compression) are replaced by a convergent nozzle and a divergent nozzle both has geometne variable, which allows to adjust the exit section of "C2" and the entry section of "D", and therefore the section of the neck between "C2" and "D", the variable geometry system, command from the outside of the device is obtained by any mechanism making it possible to modify the passage section of the neck 25 of the device such as the use of deformable walls on the nozzles “C2” and “D”, or

1 addition of a profile core "K" or "K l" which can slide axially in the areas "N" "C2" and "D", this core itself being fixed on a shaft passing through one (or both) ends of the device and making it possible to adjust the position of the news from the outside

3) Device according to claim 1 caracteπse by obtaining a supersonic flow 930 in the cooling zone using the expansion convergent "C l" to relax systematically the fluid to be compressed up to the sonic speed, and by replacing the parts “N” (transition zone) and “C2” (convergent expansion / cooling nozzle) by a diverging supersonic expansion tube “D l”, followed a transition zone "NT", a convergent compression / cooling nozzle "C3", and a convergent adiabatic compression nozzle "C4" (optional), the identical spray nozzle system "R" to that of the basic version 1, is installed in the zone "C3" and possibly in the zones "D l" and / or "NT"

4) Device according to claim 3 characterized by the replacement of the system of spray nozzles distributed along the axis of the device by a single axial nozzle or by

940 radial nozzles, placed at the entrance to the “C3” zone or in the “NT” transition zone

(this latter arrangement making it possible to anticipate the time difference between spraying and evaporation of the injected liquid), the flow rate and the axial position of these nozzles being able to be adjusted manually or automatically from outside the device

5) Device according to claims 3 or 4 characterized in that the convergent "C l" and the divergent 945 "D 1" of variants 3 and 4 are replaced by a convergent nozzle followed by a diverging nozzle both with variable geometπe, which makes it possible to adjust the section of the neck included between these two nozzles, the variable geometry system, controlled from the outside of the device is obtained by any mechanism making it possible to modify the section of passage of the neck comprised between "C l" and "D l" such as replacing "C l" and "D 1"

950 by a convergent nozzle “CG” followed by an optional transition zone “NT '” and by a diverging nozzle “DG” the three with deformable walls, or the replacement of “D l” by an optional transition zone “NT” »Followed by a slightly divergent" N2 "conduit preferably with the addition of a profile core" K2 "sliding axially in" C 1 ", in" NT '", and in the conduit" N2 ", the core being for example fixed on a tree

955 passing through one (or both) ends of the device and making it possible to adjust its position from the outside Depending on the conditions of use of the device, the variable geometry system can allow the “DG” nozzle to be slightly convergent during the commissioning of the device, for the same reason, the "N2" conduit may be slightly convergent

6) Device according to claims 3 or 4 characterized in that the areas "C3" "C4"

960 and "D" of variants 3 and 4 are replaced by a variable geometry system controlled from outside the device and making it possible to modify the section of the neck between "C3" and "D", the variable geometry system is obtained by any mechanism allowing to modify the section of this neck such as the replacement of "C3", "C4", and "D" by a nozzle "CGI" with deformable walls which can be adjusted to be preferably slightly

965 diverging when the device is put into service, then converging thereafter followed by a diverging nozzle “DG1” with deformable walls also, or by replacing the nozzles “C3” and “C4” with a slightly “N3” conduit preferably di erent with an inlet diameter slightly larger than that of "D l" preferably, inside which an axially sliding core "K3" fixed on a shaft passing through one (or the

970 two) ends of the device and allowing to adjust the position of "K3" from the outside ; in a more simplified concept, the divergent duct “D” and possibly the plenum “T” can simply be constituted by an extension of the duct “N3”.

7) Device according to claims 5 and 6, characterized by the simultaneous application of

975 claims 5 and 6 on the same device and making it possible to adjust from the outside, at any time and independently of one another, the sections of the two necks of the device.

8) Device according to claims 1 to 7, characterized in that the spray nozzles use as spray assistance fluid a part of the compressed air (or gas) generated by the device, or steam generated by heat recovery on the

980 compressed gas downstream from the stilling chamber.

9) Device according to claims 1 to 8, characterized in that the liquid used in the spray nozzles is heated before its introduction into the nozzles, by using the heat recovered from the compressed gas downstream of the stilling chamber "T »And if necessary, failing this or in addition to this heat recovered, by any other source of

985 internal heat (heat recovered in the double envelopes, etc.) or external to the device

10) Device according to claims 1 to 9 characterized by the installation in series or in parallel of several of the devices described above, the devices can be distinct from each other or nested one inside the other such as two devices according to claim 8 wherein the cores are installed in parallel in the same envelope, or even such that two

990 devices according to claims 2 and 9 installed in series and nested one inside the other with suction line, inlet chamber "C", converging "C l" and "C2", and common inlet core acting as nucleus “K” for the first subsonic device and nucleus “K2” for the second supersonic device.