US3653225A - Gas-cooling system and its uses - Google Patents

Gas-cooling system and its uses Download PDF

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Publication number
US3653225A
US3653225A US845018A US3653225DA US3653225A US 3653225 A US3653225 A US 3653225A US 845018 A US845018 A US 845018A US 3653225D A US3653225D A US 3653225DA US 3653225 A US3653225 A US 3653225A
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United States
Prior art keywords
gas
jet
chamber
nozzle
gap
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Expired - Lifetime
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US845018A
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English (en)
Inventor
Philippe Albert Hippol Marchal
Jacques Louis Paul Simonnet
Jean Prudent Fernand R Verrien
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Entreprise de Recherches et dActivites Petrolieres SA
Bertin Technologies SAS
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Bertin et Cie SA
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Priority claimed from FR6918701A external-priority patent/FR2045603A2/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • F25B9/065—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders using pressurised gas jets
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10G—CRACKING HYDROCARBON OILS; PRODUCTION OF LIQUID HYDROCARBON MIXTURES, e.g. BY DESTRUCTIVE HYDROGENATION, OLIGOMERISATION, POLYMERISATION; RECOVERY OF HYDROCARBON OILS FROM OIL-SHALE, OIL-SAND, OR GASES; REFINING MIXTURES MAINLY CONSISTING OF HYDROCARBONS; REFORMING OF NAPHTHA; MINERAL WAXES
    • C10G5/00—Recovery of liquid hydrocarbon mixtures from gases, e.g. natural gas
    • C10G5/06—Recovery of liquid hydrocarbon mixtures from gases, e.g. natural gas by cooling or compressing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/06—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by partial condensation
    • F25J3/0605—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by partial condensation characterised by the feed stream
    • F25J3/061—Natural gas or substitute natural gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/06—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by partial condensation
    • F25J3/063—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by partial condensation characterised by the separated product stream
    • F25J3/0635—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by partial condensation characterised by the separated product stream separation of CnHm with 1 carbon atom or more
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/06—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by partial condensation
    • F25J3/063—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by partial condensation characterised by the separated product stream
    • F25J3/065—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by partial condensation characterised by the separated product stream separation of CnHm with 4 carbon atoms or more
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2240/00—Processes or apparatus involving steps for expanding of process streams
    • F25J2240/60—Expansion by ejector or injector, e.g. "Gasstrahlpumpe", "venturi mixing", "jet pumps"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2270/00—Refrigeration techniques used
    • F25J2270/90—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration
    • F25J2270/908—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration by regenerative chillers, i.e. oscillating or dynamic systems, e.g. Stirling refrigerator, thermoelectric ("Peltier") or magnetic refrigeration
    • F25J2270/91—External refrigeration, e.g. conventional closed-loop mechanical refrigeration unit using Freon or NH3, unspecified external refrigeration by regenerative chillers, i.e. oscillating or dynamic systems, e.g. Stirling refrigerator, thermoelectric ("Peltier") or magnetic refrigeration using pulse tube refrigeration

Definitions

  • ABSTRACT A gas-cooling system wherein a pressurized gas jet delivered [30] Foreign Application Priority Data by an injector across a break in continuity is collected in one or more tubes whose inlet aperture faces the injector and in Aug.
  • SHEET 3 0F 6 PATENTEDAPR 4 m2
  • SHEET U 0F 6 mm m Q m m ml, H i H a mfl i H llll L f m w Q Ti njmiii i m w Q 9% E SW mm m m m T 2, R L L f? w NEE V m a QM m wv m m PATENTEDAFR 4 1972
  • SHEET 5 BF 6 PATH-HEBAPR M972 $853,225
  • This invention relates to improvements and variant embodiments of systems of the kind disclosed in U.S. Pat. No. 3,541,801 and which are adapted to subdivide a compressed gas flow at a certain temperature into a first flow of lower temperature and a second flow of higher temperature, the latter flow possibly being low or even zero, so that the systems behave in effect like gas-cooling apparatuses.
  • One of the main features of the systems to which the afore-mentioned patent relates is that they operate on pulsating gas flows, using the physical phenomena deriving therefrom; the pulsating flows can be produced from continuous initial flows by means of suitable control elements, inter alia aerodynamic bistables, operating by the periodic deflection of the initial continuous gas flow and the conversion thereof into pulsating flows, such bistables forming genuine fluid switches and if necessary dispensing with all mechanical moving members, as disclosed in Kadosch et al. U.S. Pat. No. 2,825,204.
  • a pressurized gas jet delivered by an injector across a break in continuity is collected in one or more tubes whose inlet aperture faces the injector and in which the collected gas is pulsated and heated by compressive wave phenomena to a temperature higher than that of the original jet, while impellent gas, removed at the level of the break in continuity via a suitable by-pass, is expanded in relation to the original jet and brought to a lower temperature than the latter.
  • the or each oscillatory hot" tube is disposed substantially in the line of continuation of the gas injector and has at its end opposite from the inlet aperture an advantageously adjustable obturating or at least constricting end;
  • the "cold by-pass comprises a chamber enclosing the break in continuity and the adjacent end portions of the injector and the or each hot tube.
  • two receiving tubes forming a fork extend from a chamber to which the injector delivers a jet which is deflected alternately to the arms of the fork by an aerodynamic fluid bistable, thus producing compressive wave phenomena in the tubes.
  • the expanded and cooled gas is taken from the chamber.
  • gas cooling can be substantially improved by substituting for the two forked tubes a plurality of receiving tubes which are disposed side-by-side, preferably in the shape of a fan, and whose inlet apertures are separated by sharp edges, the jet being oscillated at a predetermined frequency so that it sweeps the inlet apertures.
  • the injector comprises a nozzle in the form of a slot or rectangle extending perpendicularly to the sweeping plane of the jet; the receiving tubes comprise over a certain length of their inlets portions of straight section also in the form of a rectangle extending perpendicularly to the sweeping plane of the jet.
  • the oscillatory deflection of the jet is produced by an aerodynamic bistable comprising piloting circuits which determine the frequency of the oscillations.
  • the present invention also covers cold-producing uses of a system according to the invention, inter alia for the air conditioning of vehicles and the liquefaction of gases.
  • the most advantageous use seems to be for the removal of gasoline or the separation of the condensable products from natural gas, since a substantial proportion of such products is simply wasted at the excess gas burners, for want of an economical recovery means.
  • the present invention provides a recovery means which has the further advantages of being simply and robustly constructed, requiring substantially no maintenance, and using for its operation no other energy than the internal energy of the natural gas.
  • the natural gas when first emitted is delivered to the cooling system or more precisely its injector, the continuous pressurized gas flow being converted into a pulsating flow, gas being expanded and cooled in the cold by-pass chamber to produce appreciable condensation and gasoline recovery.
  • FIG. 1 is a diagrammatic sectional view showing the main constituent elements of the system according to the invention.
  • FIGS. 2-4 illustrate three variant embodiments of a constructional detail of the system shown in FIG. 1;
  • FIGS. 5-8 are diagrammatic sectional views of four variant embodiments using an aerodynamic bistable control system
  • FIG. 9 is an analogous view of a variant embodiment
  • FIG. 10 is a cross-section, taken along the line X-X in FIG.
  • FIG. 11 illustrates diagrammatically an improved expansion and cooling system according to the invention, taken in section along the line XI-XI in FIG. 12;
  • FIG. 12 is a sectional view, taken along the line XII-XII in FIG. 1 1;
  • FIG. 13 is a partial view analogous to FIG. 11, showing the chamber to an enlarged scale;
  • FIGS. 14-16 diagrammatically illustrate three methods of using the invention for the removal of gasoline.
  • FIG. 17 is a circuit diagram of an apparatus for the removal of gasoline comprising the system illustrated in FIGS. 11 and 12.
  • the system illustrated in FIG. 1 comprises a pressurized gas source 1 which is shown as a reservoir in the drawing, but could be anything else, for instance a compressor.
  • a pressurized gas source 1 which is shown as a reservoir in the drawing, but could be anything else, for instance a compressor.
  • the continuous gas flow is converted by a rotary needle valve 3 or some other suitable member into a pulsating flow which flows through an injector tube 4 discharging at its end 5 into a chamber 6 facing inlet aperture 8 of a receiving tube 7 terminating in an adjustable diaphragm 9.
  • One or more removal conduits 10 are connected to the chamber 6.
  • the relatively long receiving tube 7 is substantially coaxial, at least at its inlet end, with the injector tube, and the diameter of the receiving tube 7 is greater than that of the injector tube 4, so that the pulsating flux leaving the latter and passing across the break in continuity 5-8 is collected with the minimum loss.
  • the diaphragm 9 when the diaphragm 9 is in the completely obturated position, the receiving tube 7 has no flow and behaves merely like a heat generator, the whole flow passing through the by-pass 6-10 with a marked drop in temperature in comparison with the flow injected at 4.
  • the opening of the diaphragm 9 produces an intensified degree of cooling in the chamber 6, this being of course at the expense of the cold" flow, which is reduced in relation to the initial flow by the hot fraction delivered by the diaphragm 9. Adjustment of the diaphragm 9 therefore enables the reduction in temperature and the cold" flow to be metered in the opposite direction.
  • the diaphragm 9 when fully open, the diaphragm 9 still has a substantially smaller flow section than the straight section of the receiving tube 7.
  • the receiving tube 7 has a widened enclosure or chamber 1 1 which increases the yield of the system, as experience has shown.
  • the overall length of the system can be reduced by constructing at least a portion of the receiving tube 7 in the form ofa coil, as shown at 12 in FIG. 3.
  • the tube 7 has over a section 13 thereof a section which first increases, then decreases.
  • the hottest portions of the receiving tube 7 can be formed with fins (not shown), to encourage heat exchanges with the surrounding medium.
  • the embodiment illustrated in FIG. has a forked double injector tube having arms 4a, 4b, a fluid bistable of a known type, as disclosed in the afore-mentioned French Pat. No. 1,55,617, being substituted for the rotary needle valve.
  • a bistable of 5 the kind specified mainly comprises a rectangular pipe 14 for accelerating the pressurized gas, the outlet of the pipe 14 having two opposite apertures interconnected by a loop 15.
  • the injector tube arms 4a, 4b are continued, with gaps 19a, 1%, by receiving tubes 7a, 7b terminating in adjustable diaphragms 9a, 9b, fins 18a, 18b being provided at suitable places. Disposed around the gaps 19a, 19b, at whose edges small so-called shock plates 24 are disposed which stop or reflect the shock waves propagated from the aperture of the tubes 4a, 4b, is a single chamber 17 to which a conduit 21 is attached for removing the cold flow.
  • the single chamber 17 can be replaced by independent chambers, as 17a, 17b in FIG. 6, each chamber having its gas-removing conduits 21a, 21b.
  • the gap 19 can be placed upstream of the forking of the receiving tubes 7a, 7b, in which case the injector tube is reduced to a very short section in the continuation of the pipe 14.
  • the deflection of the jet coming from the pipe 14 is not controlled by a single loop connecting the opposite apertures, as in the preceding embodiments, but by a pilot bistable 22 having a control loop 23 and receiving via a conduit 24 a continuous flow which can come inter alia from the source 1.
  • bistable can also be based on the natural properties of fluid flows which tend to stick to a convex wall (Coanda effect) and to be separated therefrom as a result of the formation of boundary layers at relative excess pressure.
  • F IG. 8 illustrates a variant embodiment of this kind.
  • a continuous flow is again converted into a pulsating flow by means of a mechanical moving member, in this case a rotary distributor 25 receiving the continuous flow in its axis and feeding radially into a plurality of injector tubes 4 which are disposed in the form of a star and followed by individual receiving tubes 27 with terminal adjustable diaphragm 9.
  • the gaps 19, having small shock plates 24 at their edges, are in the same cylindrical cold chamber 17 having a gas-removing conduit 21.
  • the pressurized gas inlet is made sealing-tight by a rotary gasket 26 interposed between the adjacent ends of a fixed duct 27 and a coaxial rotary duct 28, while the rotary assembly is driven by a chain 29 extending over a pinion 30.
  • the system illustrated in FIGS. 11-13 comprises an injector 31 to which a pressurised gas is supplied from a pipe 32 and which has rectangular nozzles 33 of small width e and height h.
  • the pressurised gas passing through the nozzle forms a sonic jet in a chamber 34 bounded, facing the nozzle 33, by the inlet apertures 35 of a bunch of receiving tubes 36.
  • the apertures 35 are also rectangular, of height h and width e; they are disposed side-by-side, forming an arc centred on the axis XX of the injector 1 and separated by sharp edges 37.
  • the tubes 38 forming the bunch 36 extend in the shape of a fan and each comprise a portion 38a of the same rectangular shape as its aperture 35, the portion 38a being connected to a portion 38b of circular section obturated at 380.
  • Two piloting circuits 39, 40 disposed on either side of the injector 31 each discharge into the chamber 34 via an aperture 41 separated from the noule 33 by a common wall 330 and separated from an outlet aperture 42 of the chamber by a wall 43 having a sharp edge 44.
  • Each of the piloting circuits comprises a tube 45 connected on the one hand to the aperture 41 and on the other to a chamber 46 and comprising a constriction 47. Extending from each of the outlet apertures 42 is a tube 48 which enables the expanded and cooled gas to be removed from the chamber 34.
  • the jet delivered by the nozzle 33 to the chamber 34 oscillates, a frequency determined by the piloting circuits 39, 40, between two limit positions shown diagrammatically at 49 and 50.
  • the jet sweeps the inlet apertures 35 and produces in the tubes 38 surges which compress and heat the gas initially at rest in the tubes 38.
  • the impellent gas drops in temperature and is then forced back, after passing the jet, into the chamber 34 and evacuated via the outlets 42 and the tubes 48.
  • This system enables a considerable proportion of the flow (for instance, percent) to be cooled as effectively as the whole flow.
  • the resulting drop in temperature is far greater than that which can be obtained with the systems described hereinbefore.
  • the frequency mainly depends on the conformation, arrangement and dimensions of the piloting circuits 39, 40, more particularly on the length of the tubes 45, the position and size of the constrictions 47 and the volume of the chambers 46.
  • other parameters also affect the value of the frequency and more particularly its stability, inter alia the length of the portions 380 of the tubes 38 and the temperature of the tubes 38, since a considerable rise in temperature in the tubes 38 corresponds to the strong drop in pressure and temperature of the impellent gas, and the Applicants have observed that this drop in temperature can be increased and the stability of the frequency improved by vigorously cooling the bunch 36 of tubes, for instance by means of a water-circulating apparatus shown diagrammatically at 51 with its water inlet and discharge pipes 51a, 51b respectively.
  • the receiver capacity which is defined by the number and volume of the tubes 38, must be in relation to the flow of gas treated. if this chamber is too small, the drop in pressure and temperature is reduced at high flow rates.
  • an apparatus adapted to treat a gas flow of the order of g/s comprising a nozzle 33 having a width 2 3 mm and height h 21.3 mm and disposed 25 mm away from receiving apertures 35 of width e 3.8 mm enables a drop in temperature of the impellent gas of the order of 40 C to be obtained at the optimum oscillation frequency of about 500 cycles, on condition that the bunch 36 comprises seven tubes 38 having a length of 3 meters and aportion 38a having a length of 30 centimeters.
  • An odd number of tubes 38 is preferably provided, to encourage the instability of the jet and therefore start the oscillatrons.
  • the sharp edges 44 co-operate with the wall 33a of the injector to form the inlets of the resonators 39, 40.
  • Their position in relation to the injector and the receiving apertures 35 has a decisive effect on the starting of the oscillations of the jet and on its extreme positions 49, 50.
  • the Applicants have observed that a slight displacement of the edges 44 in relation to their optimum position as shown in FIG. 13, which is drawn to scale, substantially reduces the drop in temperature.
  • the present invention can be used in many ways. That use will now be described by way of example which seems to be particularly advantageous for the removal of gasoline in oil installations.
  • FIG. 14 diagrammatically illustrates an installation of the kind specified. All the gas leaving the well at high pressure is fed via a conduit 60 to one or more thermal separators according to the invention, shown diagrammatically at S, preferably after passing through an apparatus 62 adapted to separate from the gas the liquid fractions which it may contain. In the thermal separator S, the gas is partly expanded thus bringing its pressure down, for instance, from 150 bars to 120 bars. At the outlet from the thermal separator S, the gasoline condensed by cooling is collected at 63, while the portion which is still gaseous leaves at 64 to be burnt or used in some other way.
  • the installation can be improved as shown in FIG. 15, by using the cooled gas taken at 61 from the outlet 64 to pre-cool the gas from the well before it enters the thermal separator S.
  • the cooled gas taken at 61 passes through an exchanger 65 through which the gas coming from the well also flows.
  • a first condensed fraction is therefore collected at 66, upstream of the thermal separator S.
  • FIG. 16 shows a variant comprising a number of thermal separators S disposed in cascade and in which only a fraction of the gas coming from the well passes through the thermal separators S, so that the other portion of the gas can be recovered at 64 at a pressure close to the outlet pressure of the well; this is an advantage if the gas is to be reinjected into the well. Only that fraction of the gas which passes through the thermal separator will be expanded, for instance, to atmospheric pressure. The level of temperature reached under these conditions will be much lower than that in the preceding systems. If the flow used for cooling is low enough, for instance percent, it can be considered lost. The expansion rate being much higher, a number of thermal separators are conveniently disposed in series.
  • FIG. 17 illustrates diagrammatically an apparatus for the removal of gasoline from natural gas, comprising a device 122 similar to that illustrated in FIGS. 11-13, whose gas-removing tubes 48 discharge into an enclosure 123.
  • the natural gas introduced via tube 32 into the device 122 leaves cooled via tubes 48, so that a substantial proportion of the liquid products which it contains is condensed and drops at 124 into the bottom of the enclosure 123, where it is recovered via a duct 125 having a constant-level valve 126.
  • the expanded gas is taken at the top of the enclosure 123 by ducting 127 having a valve 128 controlled by a manostat 128a and is passed to a heat exchanger 129, where it cools the gas coming from the well at 320.
  • This cooling condenses a small proportion of the gasoline in a separator 130; the condensed product drops into the chamber 123 via a duct 131 having a scavenging valve 132.
  • the exchanger 129 can be put out-ofcircuit by a by-pass 133 controlled by a valve 134. If the gasoline is too viscous at 124, it can be heated by a coil 135 supplied via ducting 136 with hot gas taken from the pipe 320.
  • a gas-cooling system of the pulse tube type wherein a gas undergoes intermittent temperature raising compression and temperature lowering expansion comprising a nozzle supplied with gas under pressure and from which issues a gaseous jet, at least one pulse tube having a gas collecting end portion which is adjacent to but spaced from said nozzle by a free gas unductedly traversed by said jet and a hot body portion which extends said end portion outward from said gap, a cool chamber communicating with said gap and having wall portions spaced therefrom whereby said gap extends within said chamber at a distance from said wall portions thereof, and means for tapping fluid from said chamber.
  • System as claimed in claim 1 comprising a plurality of pulse tubes having gas collecting end portions which are juxtaposed in fan-wise arrangement with sharp leading edges separating adjacent end portions, means for permanently supplying gas under pressure to said nozzle whereby a continuous jet issues therefrom, and means for periodically oscillating said jet in the plane of said fan-wise arrangement to sweep said end portions.
  • jet oscillating means comprises a fluidic switch-valve, and pilot means for controlling the same.
  • pilot means comprise ducts extending on both sides of said nozzle and opening into said chamber at opposite sides of said gap, an enclosure communicating with each of said ducts opposite from said opening thereof, and a constriction in each of said ducts intermediate said opening thereof and said enclosure communicating therewith.
  • System as claimed in claim 8 further comprising an aperture in said chamber adjacent said opening of each of said ducts and separated therefrom by a sharp edge.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Organic Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Production Of Liquid Hydrocarbon Mixture For Refining Petroleum (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
US845018A 1968-08-05 1969-07-25 Gas-cooling system and its uses Expired - Lifetime US3653225A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR161906 1968-08-05
FR6918701A FR2045603A2 (en) 1969-06-06 1969-06-06 Expansion cooling natural gas

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CA (1) CA917937A (zh)
DE (1) DE1938935C3 (zh)
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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3828574A (en) * 1971-10-15 1974-08-13 Bertin & Cie Rotary-injector type distributor
US3904514A (en) * 1968-08-05 1975-09-09 Bertin & Cie Gas-cooling process and its uses
US4383423A (en) * 1980-04-02 1983-05-17 Nouvelles Applications Technologiques Thermal separators employing a movable distributor
WO1990008929A1 (en) * 1989-01-31 1990-08-09 Tselevoi Nauchno-Tekhnichesky Kooperativ 'stimer' Method and device for converting heat in relation to lower potential into heat in relation to higher potential
WO1990009511A1 (en) * 1989-02-20 1990-08-23 Tselevoi Nauchno-Tekhnichesky Kooperativ 'stimer' Steam-power plant
EP0511422A1 (en) * 1991-04-30 1992-11-04 International Business Machines Corporation Low temperature generation process and expansion engine
US5412950A (en) * 1993-07-27 1995-05-09 Hu; Zhimin Energy recovery system
US6089026A (en) * 1999-03-26 2000-07-18 Hu; Zhimin Gaseous wave refrigeration device with flow regulator
EP1313988A1 (en) * 2000-04-18 2003-05-28 Zhimin Hu Gaseous wave refrigeration device with flow regulator
EP2226595A2 (en) * 2009-03-06 2010-09-08 Linde Aktiengesellschaft Thermoacoustic refrigerator for cryogenic freezing
CN103861748A (zh) * 2014-03-11 2014-06-18 大连理工大学 推挽外激励式射流振荡发生器
CN105758051A (zh) * 2016-03-16 2016-07-13 大连理工大学 中部阻波腔隔离式气波管

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1086319A1 (ru) * 1980-09-08 1984-04-15 Всесоюзный научно-исследовательский институт гелиевой техники Расширительное устройство дл получени холода
IT1215632B (it) * 1983-06-01 1990-02-22 Bcs Spa Condizionatore di foraggio.
HU193122B (en) * 1985-07-30 1987-08-28 Olajipari Foevallal Tervezoe Method and arrangement for decreasing the evaporation losses of storage spaces containing evaporating material and recovering the vapours from gas-vapour mixture

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2952982A (en) * 1955-08-24 1960-09-20 Spalding Dudley Brian Pressure exchanger apparatus
US3237421A (en) * 1965-02-25 1966-03-01 William E Gifford Pulse tube method of refrigeration and apparatus therefor
US3314244A (en) * 1966-04-26 1967-04-18 Garrett Corp Pulse tube refrigeration with a fluid switching means
US3339635A (en) * 1965-10-22 1967-09-05 Clarence W Brandon Method and apparatus for forming and/or augmenting an energy wave
US3526099A (en) * 1967-03-01 1970-09-01 Bertin & Cie Heat exchanging apparatus

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2952982A (en) * 1955-08-24 1960-09-20 Spalding Dudley Brian Pressure exchanger apparatus
US3237421A (en) * 1965-02-25 1966-03-01 William E Gifford Pulse tube method of refrigeration and apparatus therefor
US3339635A (en) * 1965-10-22 1967-09-05 Clarence W Brandon Method and apparatus for forming and/or augmenting an energy wave
US3314244A (en) * 1966-04-26 1967-04-18 Garrett Corp Pulse tube refrigeration with a fluid switching means
US3526099A (en) * 1967-03-01 1970-09-01 Bertin & Cie Heat exchanging apparatus

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3904514A (en) * 1968-08-05 1975-09-09 Bertin & Cie Gas-cooling process and its uses
US3828574A (en) * 1971-10-15 1974-08-13 Bertin & Cie Rotary-injector type distributor
US4383423A (en) * 1980-04-02 1983-05-17 Nouvelles Applications Technologiques Thermal separators employing a movable distributor
WO1990008929A1 (en) * 1989-01-31 1990-08-09 Tselevoi Nauchno-Tekhnichesky Kooperativ 'stimer' Method and device for converting heat in relation to lower potential into heat in relation to higher potential
WO1990009511A1 (en) * 1989-02-20 1990-08-23 Tselevoi Nauchno-Tekhnichesky Kooperativ 'stimer' Steam-power plant
EP0511422A1 (en) * 1991-04-30 1992-11-04 International Business Machines Corporation Low temperature generation process and expansion engine
US5412950A (en) * 1993-07-27 1995-05-09 Hu; Zhimin Energy recovery system
US6089026A (en) * 1999-03-26 2000-07-18 Hu; Zhimin Gaseous wave refrigeration device with flow regulator
EP1313988A1 (en) * 2000-04-18 2003-05-28 Zhimin Hu Gaseous wave refrigeration device with flow regulator
EP1313988A4 (en) * 2000-04-18 2003-07-09 Zhimin Hu GAS WAVE REFRIGERATION DEVICE PROVIDED WITH A FLOW REGULATOR
EP2226595A2 (en) * 2009-03-06 2010-09-08 Linde Aktiengesellschaft Thermoacoustic refrigerator for cryogenic freezing
EP2226595A3 (en) * 2009-03-06 2014-12-24 Linde Aktiengesellschaft Thermoacoustic refrigerator for cryogenic freezing
CN103861748A (zh) * 2014-03-11 2014-06-18 大连理工大学 推挽外激励式射流振荡发生器
CN103861748B (zh) * 2014-03-11 2016-02-24 大连理工大学 推挽外激励式射流振荡发生器
CN105758051A (zh) * 2016-03-16 2016-07-13 大连理工大学 中部阻波腔隔离式气波管
CN105758051B (zh) * 2016-03-16 2018-09-04 大连理工大学 中部阻波腔隔离式气波管

Also Published As

Publication number Publication date
NL145662B (nl) 1975-04-15
NL6911932A (zh) 1970-02-09
GB1239166A (zh) 1971-07-14
NO126494B (zh) 1973-02-12
DE1938935C3 (de) 1978-04-27
DE1938935B2 (de) 1977-09-01
OA03330A (fr) 1970-12-15
CA917937A (en) 1973-01-02
DE1938935A1 (de) 1970-03-05

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