EP0586294B1 - Anlage für die Abgabe von cryogenen Flüssigkeiten an Vorrichtungen, die sie verwenden - Google Patents

Anlage für die Abgabe von cryogenen Flüssigkeiten an Vorrichtungen, die sie verwenden Download PDF

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Publication number
EP0586294B1
EP0586294B1 EP19930402120 EP93402120A EP0586294B1 EP 0586294 B1 EP0586294 B1 EP 0586294B1 EP 19930402120 EP19930402120 EP 19930402120 EP 93402120 A EP93402120 A EP 93402120A EP 0586294 B1 EP0586294 B1 EP 0586294B1
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Prior art keywords
pressure
valve
liquid
piston
fluid
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EP19930402120
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English (en)
French (fr)
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EP0586294A1 (de
Inventor
André Lermuzeaux
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Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C9/00—Methods or apparatus for discharging liquefied or solidified gases from vessels not under pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2201/00—Vessel construction, in particular geometry, arrangement or size
    • F17C2201/01—Shape
    • F17C2201/0104—Shape cylindrical
    • F17C2201/0109—Shape cylindrical with exteriorly curved end-piece
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2203/00—Vessel construction, in particular walls or details thereof
    • F17C2203/03—Thermal insulations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2205/00—Vessel construction, in particular mounting arrangements, attachments or identifications means
    • F17C2205/03—Fluid connections, filters, valves, closure means or other attachments
    • F17C2205/0302—Fittings, valves, filters, or components in connection with the gas storage device
    • F17C2205/0323—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2205/00—Vessel construction, in particular mounting arrangements, attachments or identifications means
    • F17C2205/03—Fluid connections, filters, valves, closure means or other attachments
    • F17C2205/0302—Fittings, valves, filters, or components in connection with the gas storage device
    • F17C2205/0338—Pressure regulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/01—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the phase
    • F17C2223/0146—Two-phase
    • F17C2223/0153—Liquefied gas, e.g. LPG, GPL
    • F17C2223/0161—Liquefied gas, e.g. LPG, GPL cryogenic, e.g. LNG, GNL, PLNG
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/01—Propulsion of the fluid
    • F17C2227/0121—Propulsion of the fluid by gravity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/01—Propulsion of the fluid
    • F17C2227/0128—Propulsion of the fluid with pumps or compressors
    • F17C2227/0135—Pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/01—Propulsion of the fluid
    • F17C2227/0128—Propulsion of the fluid with pumps or compressors
    • F17C2227/0135—Pumps
    • F17C2227/0142—Pumps with specified pump type, e.g. piston or impulsive type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/04—Methods for emptying or filling

Definitions

  • the present invention relates to a device for transferring cryogenic fluids in industrial establishments between a storage tank and at least one user device.
  • Cryogenic fluids are generally transported by truck to their place of use, where they are stored in insulated tanks; from there they are distributed to the user devices by a cryogenic piping or line, under the effect of the pressure which is established in the storage tank by the vaporization of a part of the cryogenic fluid. A balance is established in a few hours between the liquid and gas phases of the tank.
  • the circulation is two-phase.
  • the two-phase for a given mass flow, increases the pressure losses, makes necessary large diameters of line and accessories, and creates irregularities in operation.
  • lines of more than 50 meters may have a random walk, or a very high cost if they are isolated under vacuum in large diameter.
  • thermodynamic efficiency of the cryogenic fluid corresponds to the enthalpic variation of the fluid between its initial state, in the reservoir, and its final state, at the outlet of the user device, after vaporization and possible reheating gas produced; it is therefore interesting to find the lowest initial enthalpy, that is to say the lowest equilibrium pressure at the reservoir that can be reached in practice.
  • a third aspect is not negligible in terms of yield: maintaining the storage pressure means replacing the volume of liquid drawn off by the same volume of gas; however the insulation of industrial tanks is of high quality, and, in the case of nitrogen, if the contents of a tank are used in less than four days, the heat inputs to the tank will be insufficient to maintain the pressure, and 0.5 to 1.5% of the fluid should be vaporized by a "heater".
  • Some examples are known of raising the reservoir relative to the user station in order to benefit from the pressure of the column of fluid.
  • Known centrifugal cryogenic pumps are ill suited to small flow rates, variations in flow rate, vaporization by loss of hydraulic efficiency in the event of a reduction in flow rate, causing risks of cavitation.
  • Alternative submerged mechanical pumps are known, in installations for filling gas cylinders, pushing the liquid to more than 200 ⁇ 105 Pa in a vaporizer; however, these pumps are not suitable for suctioning the liquid at low pressure.
  • the pumping of a cryogenic fluid at low pressure with reciprocating piston, the inlet part of which is immersed in the liquid to be pumped is known from FR-A-2 613 034.
  • the object of the present invention is to provide a simple and effective cryogenic fluid pumping device, to raise its pressure to a constant and adjustable level, for variable flows, typically between a zero flow and a maximum depending on the size of the user device, this pumping device being advantageously supplemented by one or more reservoirs for accumulating the fluid under pressure.
  • This device allows a new mode of distribution of cryogenic fluids to user devices; taking the case of nitrogen, the filling on delivery will be at the lowest pressure, which constitutes a control of the quality of the fluid, without regulating the pressure at "unloading", an operation which is often a source of installation irregularities; the storage tank, at low pressure, can be lightened, without a pressure regulation system; the lines will be designed for the monophasic, allowing smaller diameters and / or longer lengths at lower costs.
  • cryogenic fluid will be understood to mean a liquefied gas such as nitrogen, argon, oxygen, CO2, etc., the user devices being able to be tunnels, baths, runoffs or spraying liquids, etc ..., but also evaporators, as well as carbon dioxide production devices.
  • Figures 1 and 2 respectively represent a part of a MOLLIER diagram of nitrogen and CO2, on which have been plotted the points representative of different distribution conditions of this fluid.
  • Figure 3 is a partial schematic view of a pumping device according to the invention.
  • FIG. 4 is a sectional view of the intake valve and of the piston of the pump in FIG. 3.
  • FIG. 5 is an overall diagram of a distribution of carbon dioxide, according to the invention.
  • the nitrogen diagram in Figure 1 shows the liquid / vapor equilibrium curve for relative pressures (PR) between zero (atmospheric pressure) and 3 x 105 Pa, along the vertical axis, the enthalpies (H) being carried on the horizontal axis.
  • PR relative pressures
  • H enthalpies
  • liquid nitrogen is normally delivered to its point of use at a pressure of 0.7 x 105 Pa: in fact, nitrogen is less than 0.05 x 105 Pa in the storage facilities of liquefaction.
  • Each pumping increases the enthalpy by 0.7 kcal / kg by loss of efficiency of the centrifugal pumps, which corresponds to an increase of 0.22 x 105 Pa in the pressure of the liquid in this pressure zone.
  • Transport, heat inputs and mechanical effects combined raises the pressure by 0.07 x 105 Pa for a journey of 100 km.
  • the nitrogen pressure in the tank will therefore be tiny, of 0.63 x 105 Pa. Note that the value rounded to 0.7 x 105 Pa translates the good quality of the fluid.
  • Nitrogen at 0.7 x 105 Pa is represented in (A1) on the diagram, as well as, in A2, nitrogen in equilibrium at 2 x 105 Pa, very common in the current state of the art; if the point of use is higher than the storage, the pressure will often be 2.6 x 105 Pa, shown in A3).
  • Points A'2 or A'3 represent nitrogen at the arrival of a user station, the two-phase often representing 3 to 5% by weight, or 150 to 250% by volume.
  • increasing the pressure by pumping from 0.7 to 2.6 x 105 Pa, as shown in A'1 will allow much greater pressure losses and heat inputs, represented by A "1 without formation of vapor.
  • one With regard to the comparisons of the initial enthalpies H1, H2, H3, one must establish the variations, therefore the quantities of cold produced in kcal / kg, for 2 final states: one corresponds to the enthalpy of the gas at - 196 ° and atmospheric pressure, when only latent heat is used, such as immersion, i.e. 18.45 kcal / kg; the other corresponds to freezing tunnels, where the gas can exit at - 50 °, with an enthalpy of 55kcal / kg.
  • Nitrogen at 0.7 x 105 Pa will produce, in the case of immersion, respectively 7.2% and 9.8% more cold than nitrogen at 2 and 2.6 x 105 Pa, and therefore the 6.7% or 9% of the amount of liquid to be saved will be saved.
  • the recovery of the sensible heat of the gas, in tunnels for example, does not depend on the initial enthalpy, and the savings due to the use of nitrogen at 0.7 x 105 Pa will be between 3.7% and 5%, respectively, with respect to nitrogen at 2 x 105 Pa and 2.6 x 105 Pa.
  • the system according to the invention adds those resulting from the elimination of the pressure maintenance of the tank: even in the event of rapid emptying, the pressure of 0.7 x 105 Pa will drop only by 0.15 x 105 Pa, or 0.55 x 105 Pa in the end, without drawbacks.
  • FIG. 2 represents the states of carbon dioxide, plotted on a diagram, the absolute pressures being represented on the vertical axis, and the enthalpies on the horizontal axis; we will quote the analogies and the differences of CO2 compared to nitrogen.
  • a final state of CO2 can be the gas leaving a refrigeration tunnel at atmospheric pressure (PA) and -50 ° C ( HT); another state final will be, after production of snow and its sublimation, the "outlet" of gas at -78.5 ° C, represented by HN.
  • the enthalpy variation, or usable cold, essentially corresponds to latent heat; it is therefore all the more interesting to lower the initial enthalpy:
  • the usual initial state is the delivery of liquid CO2 at -20 ° C and 20 x 105 Pa, represented in D1), which can be stored completely in the manner of liquid nitrogen, in vacuum-insulated tanks; generally less efficient storages are used, the pressure of which is controlled at 20 ⁇ 105 Pa by a refrigeration unit; in the latter case, centrifugal pumps are known for looping the liquid CO C to keep the line cold, and not for the purpose of obtaining subcooling of the liquid by increasing pressure.
  • the gas formed by the losses in efficiency of the pumps and the heat inputs returns at the end of the loop to the tank, where it is condensed by the refrigeration unit.
  • the pumping device which is the subject of the invention makes it possible to use CO2 brought in the vicinity of the triple point, either by cooling, or by vaporization and reduction of the pressure, as represented by D3: the pressure can be increased to the point representative of D'3, so that in use (D "3) the risk of solid formation is reduced.
  • the pump admits the circulation of fluid loaded with particles, and if the low pressure tank is loaded on its inlet , we could even use a mixture of liquid and solid CO2 at the triple point.
  • FIG. 3 schematically illustrates the pumping device according to the invention: an isolated storage tank 1 contains the cryogenic fluid at the lowest possible pressure: for nitrogen, this tank is storage, receiving liquid nitrogen at 0.7 x 105 Pa; for CO2, it is a low pressure tank, generally separate from the delivery tank.
  • an isolated storage tank 1 contains the cryogenic fluid at the lowest possible pressure: for nitrogen, this tank is storage, receiving liquid nitrogen at 0.7 x 105 Pa; for CO2, it is a low pressure tank, generally separate from the delivery tank.
  • a line 2 is the liquid outlet from the reservoir, which feeds by gravity the pumping device via a stop valve 3; it is desirable to oversize the latter 3 ', and to reduce the horizontal distance during pumping.
  • the outlet of tank 1 must be 0.5 to 1 meter higher than the inlet of the pumping device.
  • the pumping device comprises at its lower part a small reservoir 4 used to supply liquid devoid of gas to the inlet valve 6 of the pump; for this it is provided with a vent tube 5 connected by an insulated tube to the gas phase (upper part) of the reservoir 1; the tube 5 is also used for cooling the pumping device in the case of the use of CO2. It can alternatively be replaced by a gas eliminator.
  • the pump is of the piston and valve type, vertical.
  • a tube 7 fixed by flanges to the reservoir 4 carries the cylinder 8 in which the piston 9, itself carrying a discharge valve, is actuated by a rod 10 passing through a set 11 and 11 'of seals, between which gas is injected under pressure from the discharge, through a heating tube 12.
  • Only the lower part of the pump is insulated, as shown by the dashed line 13: the liquid leaves the tube 7 is made by a nozzle 14, located just above above the cylinder 8 and the tube and pump fixing flange, so that the upper part of the tube 7 contains a volume of slightly conductive gas, and that the seals 11 and 11 ′ remain at room temperature.
  • the piston control rod 10 is connected to a motor 15 giving an adjustable reciprocating movement, a particularly advantageous embodiment using a motor with pneumatic or hydraulic cylinders.
  • a motor 15 giving an adjustable reciprocating movement, a particularly advantageous embodiment using a motor with pneumatic or hydraulic cylinders.
  • an important characteristic of the movement of the piston is that it must be slow during the ascent, which corresponds to the suction or admission phase of the pumping cycle, compared to the descent movement, which corresponds to the setting. in fluid pressure and in its discharge, and which can be as fast as it is mechanically possible.
  • the pressure of the working fluid actuating the engine 15 is regulated by a pressure reducer 17: the ratio of the active sections of the motor cylinder and the pump piston and the pressure setting of the pressure reducer define the maximum pressure to which the cryogenic fluid will be brought.
  • a possible adjusting member 18 conditions the flow of working fluid, and therefore the overall duration of an up / down cycle. This duration must be compatible with the operation of the motor fluid distributor 19, actuated by a double timer, or by a timer and a limit switch 21.
  • An adjustable unidirectional flow reducer 20 makes it possible to adjust the slow ascent rate (admission), the discharge being free or regulated by the member 18.
  • Another limit switch 21 ' can allow the control of the piston ascent rate.
  • the detector 21 can be used for counting and determining the instantaneous flow rates, means, or cumulative quantities of cryogenic fluid supplied to an item of equipment.
  • Two distribution systems can raise the pressure of counted and regulated quantities of two different liquefied gases, such as nitrogen and oxygen, so that after mixing in the liquid phase, the pressure is greater than the bubble pressure; liquid phase metering can also be used before vaporization and mixing in the gaseous state.
  • two different liquefied gases such as nitrogen and oxygen
  • FIG. 4 shows the details of the pump and in particular of the piston and of the intake valve: the body of the valve 6 is fixed on the cylinder 8; the valve itself is a flat disc with rounded edges, the lifting of which is limited by a rod 25; it rests on a seat 24, and is guided by the tie rods 26 for assembling the valve bottom 27.
  • the disc is preferably made of high density polyethylene or PTFE.
  • the piston is constituted by a tubular body 9 fixed on the control rod 10, and provided with windows 22 for passage of the pumped fluid; a hollow screw 28 fixed on the piston of the annular seals 30 with upward-facing lips, made of polyethylene, PTFE, or leather, by tightening spacers 29.
  • a ball 31 forms a sealing valve by resting on the screw 28; the rod 10 abuts the lifting of the ball.
  • the piston touches the intake valve 23 in order to reduce the "dead volume" of fluid between the piston and the valve: in fact, upon lifting, the acceleration of the valve is several times the gravity, by pressure by below, from the liquid column, and by vacuum from above, due to the upward movement of the piston; we limit this effect and the vaporization, reducing the volume of liquid concerned, by bringing the piston and valve as close as possible.
  • the liquid arrives from the storage tank through line 2 and completely fills the pump tank 4 with evacuation of any gas through the vent 5; the liquid descends through the space between the body of the valve 6 and the reservoir 4.
  • the valve 23 When the piston is raised, the valve 23 is lifted by pressure difference between the lower and upper faces: the valve must be as light as possible, and in the case of a seat diameter of 80 mm., It will be set to rest on a spider carried by an annular piece 27; the liquid must strictly follow the upward movement of the piston, since any vaporization must be avoided.
  • the pressure of the fluid on the discharge side, and the pressure of the gas contained in the tube 7, which are identical, are exerted on the upper face of the piston and on the ball 31.
  • the piston rise speed is 0.55 m / s: this is also the nitrogen rise speed.
  • the narrowest flow section is in the vicinity of the valve seat; this is also the highest speed of nitrogen, around 1.30 m / s, corresponding to a dynamic pressure of 700 Pa.
  • the ascent of the piston is the flow phase through the inlet valve; the piston ascent rate must typically have a maximum value of 0.5 m / s for the rise of the liquid to follow the rise of the piston.
  • the rate of rise of the piston conditions the flow rate, and it is desirable that, in a cycle, the descent phase is as brief as mechanically possible, since there is no thermodynamic drawback, and the flow will be optimum in chained cycles.
  • the flow rate is proportional to the active surface of the piston, ie the square of its diameter.
  • a pressure drop factor of less than 2.86 has been found; multiplied by the dynamic pressure of the highest speed of the fluid in the valve, it indicates its overall pressure drop.
  • the same speed must be kept in the smallest section of the valve, namely in the vicinity of the seat, the valve lift being always in practice limited to 5mm; keeping the same fluid speed requires that the diameter of the valve seat be proportional to the square of the piston diameter. If a smaller valve is used, the piston ascent rate must be reduced: the diameter of the piston will be oversized, causing greater pressures of the working fluid.
  • the transition times from rise to fall, and vice versa, of the piston are between 25 and 50 ms, and the average speed of the piston is little different from the instantaneous speed during a movement of the cycle. Therefore, the stroke length is not an essential factor of flow, but frequency, with a mechanical interest.
  • the pump described above, with piston diameter 45 mm, valve seat 40 mm, stroke 100 mm, can be industrially used at a rate typically of around 125 to 130 cycles / min, corresponding to a flow rate of 1100 to 1200 liters / hour of cryogenic fluid, suitable for many applications.
  • a double flow pump i.e. 2200 to 2400 liters / hour, would have a piston diameter multiplied by ⁇ 2, or approximately 65 mm, a valve seat diameter proportional to the flow rate, ie 80 mm, and an operating rate of about 125 to 130 cycles / min. if the stroke is 100 mm, and about 85 cycles per minute, if the stroke is 150 mm.
  • the present device provides a solution by the use of accumulators under pressure, either at the point of use, or online.
  • the reservoir 1 receives the CO2 from a delivery reservoir 32, at a pressure P1 of the order of 20 ⁇ 105 Pa, via a line 33; a float 34 controls a filling means 35 to keep a constant level; the liquid at 20 ⁇ 105 Pa is introduced into the tank by means of a phase separator 36.
  • a demister 37 placed in the tank 1, is located at the intake of a single-stage compressor 38 associated with a gas-gas exchanger 39.
  • the compressor 38 raises the pressure of the CO2 gas in the tank 1 from 6 to 22 ⁇ 105 Pa, to reliquefy it by the condenser 40, connected at 41 and 42 to a refrigeration circuit (not shown).
  • the tank pressure can be lowered by refrigeration to -53 ° C.
  • the discharge line 14 of the pumping device ensures a flow of liquid CO2 at -53 ° C, at a pressure of 10 x 105 Pa, for example, (therefore sub-cooled relative to the equilibrium temperature at 10 x 105 Pa, which is - 40 °), until the use represented by a solenoid valve 48.
  • a gas trap 53 for example with float 54, ensures that the line is kept cold, even if it is not there is no traffic.
  • the gas at 10 x 105 Pa, leaving the trap 53 is brought through a pipe 55, to the gas phase of the tank 1, or to the reliquefaction. This arrangement advantageously replaces the technique of keeping cold by loop of liquid with circulation pump.
  • an isolated accumulator tank 43 allows operation if the average flow rate is lower than the nominal flow rate of the pumping device: the latter fills the accumulator 43 up to the level defined by a detector 44; as long as the level is not reached, a valve 45 in a line connecting the upper parts of the tanks 1 and 43, is open, and the gas repelled by the liquid in the tank 43 joins the tank 1, passing through a spillway 46 set to maintain an upstream pressure of 8 x 105 Pa for example; this spillway can also be replaced by simple rolling.
  • the pumping device 7 When the accumulator tank 43 is full, without use, the pumping device 7 maintains the pressure at zero flow, by the adjustment established on the pressure of its working fluid.
  • a solenoid valve 49 for pressurizing the accumulator tank 43 disposed in a line connecting the upper parts of the tanks 43 and 32 is also opened; the pressure of the pressurization gas coming from the storage tank 32 is adjusted by the pressure reducer 50 which ensures, for example, a downstream pressure of 11 x 10, Pa, so that the fluid reaching use 48 comes first from the accumulator 43; on the contrary, it will be possible to adjust the downstream pressure of the regulator 50 to a value lower than the pumping pressure, for example 9.5 x 105 Pa, so that the flow rate of the pumping device is used as a priority, and the accumulator 43 only as a backup.
  • a level control 47 can be used in the accumulator tank 43 stopping the supply of fluid supplied for use 48 in the event of excessive draining of the accumulator, the size of the latter having to be adapted to Requirement ; one can also use a pressure switch P3 to check that the pressure in the accumulator 43 is always at a certain level above that of the triple point.
  • This accumulator system can optionally be adapted to fluids such as liquid nitrogen; in this case, the evacuation of the gas from the accumulator takes place in the atmosphere, and the pressurization can be carried out by increasing the size of the vaporizer 12 of FIG. 3, and by connecting it to the solenoid valve 49.
  • valve 56 For the record, the usual safety and purging devices have been shown, respectively a valve 56 and a valve or solenoid valve 57; a drain valve for the pump reservoir 4 must also be provided when the installation is stopped.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Jet Pumps And Other Pumps (AREA)

Claims (7)

  1. Abgabevorrichtung für eine Kryoflüssigkeit an Verbrauchsstellen, wobei die Flüssigkeit bei niedrigem Druck in einem Vorratsbehälter (1) gespeichert ist, der eine Hubkolbenpumpe (9) speist, deren Einströmöffnung (6) in die zu pumpende Flüssigkeit eintaucht, dadurch gekennzeichnet, daß die Pumpvorrichtung Antriebsmittel umfaßt, die eine langsame Aufwärtsbewegung des Kolbens, vorzugsweise kleiner 0,5 m/s entsprechend dem Ansaugen der Flüssigkeit, und eine schnelle Abwärtsbewegung entsprechend dem Förderdruck, sicherstellen.
  2. Vorrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß die Bewegung des Kolbens (9) durch wenigstens einen Arbeitszylinder bewirkt wird.
  3. Vorrichtung gemäß Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Pumpvorrichtung ein Sperrventil (23) umfaßt, wobei der Kolben (9) an seiner tiefsten Position mit dem Ventil (23) in Kontakt kommt.
  4. Vorrichtung gemäß Anspruch 3, dadurch gekennzeichnet, daß die Pumpvorrichtung dicht mit einem Reservoir (4) verbunden ist, welches das Sperrventil (23) umschließt und eine Gasevakuierungsöffnung umfaßt.
  5. Vorrichtung gemäß einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß diese eine Einrichtung zum Zählen der Arbeitszyklen der Pumpvorrichtung umfaßt, um das geförderte Flüssigkeitsvolumen, das in einer Anlage verbraucht wurde, zu bestimmen.
  6. Vortichtung gemäß einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß diese wenigstens einen isolierten Behälter (43) umfaßt, der mit dem Förderausgang der Pumpvorrichtung verbunden ist, wobei die Auffüllung dieses Behälters durch die Evakuierung von Gas über ein Ventil (45) bewirkt wird, und die Entleerung während der Verbrauchszeiten mit einem Überdruck durch geregelte Gaszufuhr über der angesammelten Flüssigkeit erfolgt, wobei die Gaszufuhr über ein Ventil (49) gesteuert wird.
  7. Abgabevorrichtung gemäß einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Flüssigkeit kohlendioxid ist, das durch die Pumpvorrichtung unter Druck gesetzt und in einem isolierten Röhrensystem (14) transportiert wird, wobei das Kohlendioxid durch mindestens einen Gasabscheider (53) in flüssigem Zustand gehalten wird und das Gas, das diese Gasabscheider verläßt, in den Vorratsbehälter (1) zurückgeführt wird.
EP19930402120 1992-09-01 1993-08-30 Anlage für die Abgabe von cryogenen Flüssigkeiten an Vorrichtungen, die sie verwenden Expired - Lifetime EP0586294B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9210449A FR2695188B1 (fr) 1992-09-01 1992-09-01 Dispositif de distribution de fluides cryogéniques à leurs appareils d'utilisation.
FR9210449 1992-09-01

Publications (2)

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EP0586294A1 EP0586294A1 (de) 1994-03-09
EP0586294B1 true EP0586294B1 (de) 1996-03-20

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EP (1) EP0586294B1 (de)
DE (1) DE69301882T2 (de)
ES (1) ES2088247T3 (de)
FR (1) FR2695188B1 (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5537828A (en) * 1995-07-06 1996-07-23 Praxair Technology, Inc. Cryogenic pump system
US5858934A (en) * 1996-05-08 1999-01-12 The Lubrizol Corporation Enhanced biodegradable vegetable oil grease
DE19646664A1 (de) * 1996-11-12 1998-05-14 Linde Ag Verdichten von CO¶2¶ oder Lachgas
DE19839233A1 (de) * 1998-08-28 2000-03-02 Linde Ag Verdichten von Flüssigkeiten und Gasversorgungsanlage
DE19915853A1 (de) * 1999-04-08 2000-10-12 Linde Tech Gase Gmbh Pumpensystem zum Fördern von kryogenen Flüssigkeiten
GB9913071D0 (en) * 1999-06-04 1999-08-04 Boc Group Plc Cryogenic refrigeration of goods
SE519091C2 (sv) * 2000-05-03 2003-01-14 Aga Ab Anordning och förfarande för pumpning av flytande gas, pumpsystem för pumpning av flytande gas samt system och förfarande för cyklisk framställning av polymerprodukter
WO2013178315A1 (en) * 2012-05-31 2013-12-05 Cern - European Organization For Nuclear Research Cryogenic cooling pump and method
WO2015153631A1 (en) * 2014-04-01 2015-10-08 Trinity Cryogenics, Llc Dual pressure-retaining manway system

Family Cites Families (3)

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Publication number Priority date Publication date Assignee Title
GB573383A (en) * 1943-05-27 1945-11-19 Air Prod Inc Improvements in the transference of and manufacture of liquid oxygen
DE3710363C1 (de) * 1987-03-28 1988-12-01 Deutsche Forsch Luft Raumfahrt Verfahren und Vorrichtung zum Foerdern einer Fluessigkeit
FR2672942A1 (fr) * 1992-02-14 1992-08-21 Ebara International Corp Procede et appareil de pompage de gaz liquefies.

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Publication number Publication date
ES2088247T3 (es) 1996-08-01
DE69301882D1 (de) 1996-04-25
DE69301882T2 (de) 1996-09-19
FR2695188B1 (fr) 1994-10-28
FR2695188A1 (fr) 1994-03-04
EP0586294A1 (de) 1994-03-09

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