AU564335B2 - Creación de Inventos y Patentes con Inteligencia Artificial

AU564335B2 – Cryogenic storage tank with built-in pump
– Google Patents

AU564335B2 – Cryogenic storage tank with built-in pump
– Google Patents
Cryogenic storage tank with built-in pump

Info

Publication number
AU564335B2

AU564335B2
AU25743/84A
AU2574384A
AU564335B2
AU 564335 B2
AU564335 B2
AU 564335B2
AU 25743/84 A
AU25743/84 A
AU 25743/84A
AU 2574384 A
AU2574384 A
AU 2574384A
AU 564335 B2
AU564335 B2
AU 564335B2
Authority
AU
Australia
Prior art keywords
vessel
tube
pump
cryogenic
tank
Prior art date
1983-01-28
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)

Ceased

Application number
AU25743/84A
Other versions

AU2574384A
(en

Inventor
Eugene B. Zwick
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Individual

Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
1983-01-28
Filing date
1984-01-27
Publication date
1987-08-06

1984-01-27
Application filed by Individual
filed
Critical
Individual

1984-08-15
Publication of AU2574384A
publication
Critical
patent/AU2574384A/en

1987-08-06
Application granted
granted
Critical

1987-08-06
Publication of AU564335B2
publication
Critical
patent/AU564335B2/en

2004-01-27
Anticipated expiration
legal-status
Critical

Status
Ceased
legal-status
Critical
Current

Links

Espacenet

Global Dossier

Discuss

Classifications

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

F17C7/00—Methods or apparatus for discharging liquefied, solidified, or compressed gases from pressure vessels, not covered by another subclass

F17C7/02—Discharging liquefied gases

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

F04B41/00—Pumping installations or systems specially adapted for elastic fluids

F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C3/00—Vessels not under pressure

F17C3/02—Vessels not under pressure with provision for thermal insulation

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2201/00—Vessel construction, in particular geometry, arrangement or size

F17C2201/01—Shape

F17C2201/0104—Shape cylindrical

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2201/00—Vessel construction, in particular geometry, arrangement or size

F17C2201/03—Orientation

F17C2201/032—Orientation with substantially vertical main axis

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2203/00—Vessel construction, in particular walls or details thereof

F17C2203/01—Reinforcing or suspension means

F17C2203/014—Suspension means

F17C2203/015—Bars

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2203/00—Vessel construction, in particular walls or details thereof

F17C2203/01—Reinforcing or suspension means

F17C2203/014—Suspension means

F17C2203/018—Suspension means by attachment at the neck

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2203/00—Vessel construction, in particular walls or details thereof

F17C2203/03—Thermal insulations

F17C2203/0304—Thermal insulations by solid means

F17C2203/0308—Radiation shield

F17C2203/032—Multi-sheet layers

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2203/00—Vessel construction, in particular walls or details thereof

F17C2203/03—Thermal insulations

F17C2203/0304—Thermal insulations by solid means

F17C2203/0337—Granular

F17C2203/0341—Perlite

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2203/00—Vessel construction, in particular walls or details thereof

F17C2203/03—Thermal insulations

F17C2203/0391—Thermal insulations by vacuum

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2203/00—Vessel construction, in particular walls or details thereof

F17C2203/06—Materials for walls or layers thereof; Properties or structures of walls or their materials

F17C2203/0602—Wall structures; Special features thereof

F17C2203/0612—Wall structures

F17C2203/0626—Multiple walls

F17C2203/0629—Two walls

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2205/00—Vessel construction, in particular mounting arrangements, attachments or identifications means

F17C2205/01—Mounting arrangements

F17C2205/0153—Details of mounting arrangements

F17C2205/0188—Hanging up devices

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2205/00—Vessel construction, in particular mounting arrangements, attachments or identifications means

F17C2205/01—Mounting arrangements

F17C2205/0153—Details of mounting arrangements

F17C2205/0192—Details of mounting arrangements with external bearing means

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2209/00—Vessel construction, in particular methods of manufacturing

F17C2209/22—Assembling processes

F17C2209/221—Welding

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

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

F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel

F17C2223/03—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the pressure level

F17C2223/033—Small pressure, e.g. for liquefied gas

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel

F17C2223/04—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by other properties of handled fluid before transfer

F17C2223/042—Localisation of the removal point

F17C2223/046—Localisation of the removal point in the liquid

F17C2223/047—Localisation of the removal point in the liquid with a dip tube

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel

F17C2225/01—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the phase

F17C2225/0146—Two-phase

F17C2225/0153—Liquefied gas, e.g. LPG, GPL

F17C2225/0161—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

F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel

F17C2225/03—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the pressure level

F17C2225/033—Small pressure, e.g. for liquefied gas

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel

F17C2225/04—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by other properties of handled fluid after transfer

F17C2225/042—Localisation of the filling point

F17C2225/043—Localisation of the filling point in the gas

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel

F17C2225/04—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by other properties of handled fluid after transfer

F17C2225/042—Localisation of the filling point

F17C2225/046—Localisation of the filling point in the liquid

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

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

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

F17C2227/0171—Arrangement

F17C2227/0178—Arrangement in the vessel

F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING

F17—STORING OR DISTRIBUTING GASES OR LIQUIDS

F17C2260/00—Purposes of gas storage and gas handling

F17C2260/03—Dealing with losses

F17C2260/031—Dealing with losses due to heat transfer

Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS

Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC

Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS

Y10S417/00—Pumps

Y10S417/901—Cryogenic pumps

Description

CRYOGENIC STORAGE TANK WITH BUILT-IN PUMP
BACKGROUND OF THE INVENTION
Field of the Invention
The present invention concerns generally cryogenic storage containers and is more particularly directed to a cryogenic tank having a built-in submerged pump for pumping the cryogen directly out of the primary storage tank without a cool down period preliminary to the pumping operation.
State of the Prior Art
A cryogenic fluid or cryogen such as liquid nitrogen is a substance which exists in the liquid state only at very low temperatures and consequently has a very low boiling point. Because of this low boiling point, two primary considerations when designing a system for storing and pumping a cryogen are the need for adequate insulation of the storage container to minimize losses of cryogen due to «boiloff», and the need to cool down the pump to the cryogen temperature before pumping.
In order to meet the first criterion, cryogenic tanks rely on good thermal and/or radiation barriers i.e. insulation, high vacuums between container w^lls, and construction techniques which minimize the thermal leak paths from the exterior environment into the cryogen. Typical thermal paths in cryogenic storage systems include conduction, convection and radiation between the inner and outer shells, fluid and gas lines which connect the inner shell to the outside, supports for the inner shell of a multi-shell container, and any connection to pumps for pumping the cryogen from the primary storage tank. Due to

its mass and its inevitable contact with the cryogen, a pump normally provides a high thermal leak path which in existing systems has led to unacceptably high losses of cryogen due to boiloff.
The solution to this problem generally adopted in the past as been to locate the pump outside the primary cryogenic storage tank where the pump is normally kept at ambient temperature. However, in order to keep the cryogen in the liquid state while being pumped, the pump must be cooled down to the cryogen temperature before pumping can begin. This therefore, introduces a delay in system start-up, as it usually takes at least five to ten minutes to cool down the pump sufficiently. When an auxiliary sump is used, the sump must also be cooled down in order to prepare the system for a pumping operation. Cooling down the pump and sump is wasteful of cryogen since a quantity of the liquid is lost in the cool down procedure by boiloff. In situations where a start-up delay is unacceptable, the pump must be kept in a stand-by condition in readiness for immediate operation. The pump must therefore be kept in a cooled down state by being submerged in the cryogen, either in the primary storage tank or in an auxiliary sump, and high rates of boiloff must be tolerated. The use of auxiliary sumps is common because the heat leak through the pump into the sump is isolated from the main storage tank, and the loss of cryogen can be reduced when standby is not required by shutting off the pump/sump from the main storage tank. Nevertheless,the use of sumps represents a compromise which increases the cost and complexity of cryogenic storage systems.
A continuing need exists for a cryogenic storage system with a built-in submerged pump which can be kept in a continuously cooled down state in readiness for immediate operation, but without excessive losses of cryogen by boiloff due to heat leakage through the pump into -the

interior of the primary storage container, to thereby eliminate both the start-up delays as well as the loss of cryogen previously associated with the cooling down of an externally mounted pump.
Summary of the Invention
The present invention is a cryogenic storage container with a built-in submerged pump which is kept in a continuously cooled down state by the cryogen stored in the tank such that pumping may be commenced immediately. The loss of cryogen through boiloff is kept to a lower figure than has been previously possible by minimizing the heat leak path from the environment into the cryogen caused by the presence of the pump inside the tank.
In general, the quantity of heat leaking into the cryogenic tank by conduction is a function of both the distance that the heat must travel from the atmosphere or the environment into the cryogen, as well as the cross section or thickness of the material through which the heat flows into the thank. Thus, the heat leak into the tank due to the presence of a submerged pump can be minimized by reducing the surface area of the pump body which comes into contact with the cryogen and also by increasing the distance between the submerged portion of the pump and the exterior of the tank. This is a difficult objective since the pump intake must be positioned near the bottom of the tank so as to pump out all of the cryogen in the tank, and yet the pump body should be accessible from the exterior of the tank so as to allow removal of the pump from the tank. To meet both objectives the pump body would have to extend through the entire cryogenic storage space such that most of the pump would be submerged in the cryogen, resulting in a large contact area and high heat leak path into the tank.

This invention overcomes these problems by providing an insulated cryogenic storage vessel with a pump mounting tube extending into the vessel and immersed in the cryogen. The outer surface of the pump mounting tube within the vessel is insulated so as to minimize the heat leakage from the pump mounting tube to the cryogen surrounding the tube. The upper end of the pump mounting tube may extend through the cryogenic vessel wall and is open at the upper end for receiving the cryogenic pump. The lower end of the pump mounting tube is also open and terminates short of the bottom of the cryogenic vessel. The pump includes a pump drive head which is mounted to the upper end of the pump mounting tube exteriorly to the insulated vessel so as to seal the upper end of the pump mounting tube to the atmosphere. A pump extension tube of relatively small cross section extends through the sealed upper end of the pump mounting tube into the vessel and supports at its lower end the pump intake valve and piston assembly suspended above the bottom of the insulated vessel. The pump mounting tube is in contact with the pump drive head and also with the exterior wall of the insulated vessel and thus establishes a heat leak patch into the storage vessel.
The cryogen rising into the pump mounting tube within the vessel is heated by contact with the inner surface of the pump mounting tube and with the pump extension tube. As a result, the liquid cryogen vaporizes to form a gas pocket trapped within the sealed pump mounting tube. The trapped gas will not allow additional cryogen to rise into the pump’mounting tube such that in an equilibrium condition a liquid/gas interface is established near the lower end of the pump mounting tube. The gas is a poor conductor of heat and so serves to insulate the liquid cryogen from the inner surface of the pump mounting tube as well as from the pump extension tube extending within the pump mounting tube. The cryogen is thus in contact only with the lower rim of the pump mounting tube and the
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submerged lower end of the pump body which includes a relatively small pump/piston unit and intake valve. The length of the heat leak path into the cryogen includes the full length of the pump mounting tube and heat flowing through the pump itself must also travel nearly the full length of the pump extension tube and the pump drive shaft before coming into contact with the cryogen near the bottom of the tank. Heat leakage is further minimized by making both the pump mounting tube and the pump extension tube of thin walled tubing so as to minimize the cross section, and therefore the mass of heat conductive material.
The inner surface of the pump mounting tube must be adequately insulated against the cryogen in the storage vessel, such as by a vacuum jacket surrounding the tube. Without such insulation the cryogen surrounding the pump mounting tube would cool the gas trapped inside the tube, causing it to condense. This would reduce the volume of gas inside the pump mounting tube and allow liquid cryogen to rise into the tube, shortening the heat leak path distance as well as increasing the area of contact of the liquid cryogen with the relatively warm inner surface of the pump mounting tube and pump extension tube. With adequate insulation around the pump mounting tube, the liquid cryogen level can be kept at the lower end of the pump mounting tube by the trapped gas. In an equilibrium condition a temperature gradient exists along the inner surface of the pump mounting tube, and pump extension tube which^are at or below the cryogen boiling temperature at the bottom of the pump mounting tube and close to ambient temperature at the top of the pump mounting tube.
In a presently preferred embodiment of the invention, the cryogenic container comprises an inner shell or vessel including an inner vessel wall which is in contact with a cryogen, and an outer vessel including an outer vessel wall which is exposed to the environment. An
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insulation space is defined between the outer vessel wall and the inner vessel wall which may be evacuated to avoid transmission of heat by conduction or convection between the two vessels. The pump mounting tube is double-walled and includes an inner tube and an outer tube with an annular space in between. The upper end of the inner tube is attached to the outer vessel wall and is open for receiving the extension tube of a cryogenic pump. The outer tube is connected at its upper end to the inner vessel wall such that the annular space between the inner and outer tubes of the pump mounting tube communicates with the insulation space between the inner and outer vessel walls. Thus, when the insulation space is evacuated, the annular space of the double walled pump mounting tube is also evacuated and forms a vacuum jacket around the inner tube. The inner and outer tubes are preferably joined only along their lower rims so as to seal the annular space between the tubes.
The pump mounting tube preferably extends vertically into the cryogenic container through the top of the outer vessel. The upper end of the inner tube is secured to the outer vessel. The weight of the inner vessel is borne by the outer tube which in turn is supported at the lower end of the inner tube, such that the inner vessel is suspended by the pump mounting tube from the top of the outer vessel. The outer tube is thus in compression by the weight of the inner vessel while the inner tube is in tension between the outer vessel and its joint to,..the outer tube at the lower end. Since the relatively warm inner tube is in tension, its walls can be made relatively thin so as to minimize its thermal conduction. The outer tube being in compression requires greater wall thickness to avoid buckling under the weight of the inner vessel. This greater wall thickness does not increase the thermal conduction along the pump mounting tube however, since the outer tube is only in contact with the cold inner vessel and the cold lower end of the inner tube and is insulated from the inner

tube by a vacuum jacket. Given that all or a substantial portion of the weight of the inner vessel can be thus suspended, little additional support is required between the two vessels which is a desirable objective in order to minimize heat leak paths through such internal supports.
These and other characteristics of the present invention are better understood by reviewing the following figures which are submitted for the purposes of illustration only and not limitation, wherein like elements are referenced by like numerals in light of the detailed description of the preferred embodiment.
Brief Description of the Drawings
Figure 1 is an elevational cross section of the novel cryogenic tank with built-in submerged pump.
Figure 2 is a cross section taken along line 2—2 in Figure 1.
Figure 3 is a longitudinal section of the pump mounting tube of the cryogenic tank of Figure 1, the pump mounting -flange being shown in alignment with the pump mounting tube.
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DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
With reference to Figure 1, a cryogenic tank 10 includes an outer vessel 12 which encloses an ‘inner vessel 14. The outer vessel wall is spaced from the inner vessel wall so as to define an insulation space 16 surrounding the inner vessel. The outer shell 12 is provided with an evacuation valve 18 through which the air in the insulation space may be evacuated so as to create a vacuum in the space 16 and thereby prevent heat flow into the inner vessel by conduction or convection. The inner vessel is also wrapped in a reflecting material such as aluminized mylar which prevents the transfer of thermal energy by radiation. The radiation barrier may consist of a multi-layered blanket 20 consisting of forty sheets of one fourth (1/4) mil aluminized mylar which has been crinkled so that adjacent sheets are spaced from each other by the irregular ridges of the crinkled surfaces. The crinkling reduces the area of contact between sheets and establishes relatively long heat flow paths through the multi-layer blanket, thus minimizing conduction of heat through the mylar material. While only a fragment of the insulating blanket 20 is illustrated in Figure 1, it will be understood that the entire inner tank is covered by such a blanket within the insulation space 16.
A pump mounting tube 34 extends vertically through the top of both the outer vessel 12 and inner vessel 14 and is aligned with the vertical axis of the tank assembly. The pump mounting tube 34 is open at its lower end -36 to the interior of the inner vessel 14 and is also open at its upper end 38 for admitting a pump extension tube/drive shaft 62.
As better understood by reference to Figs. 2 and 3, the pump mounting tube 34 is double walled and comprises an inner tube 42 and an outer tube 52. The inner

pump tube 42 is attached at its upper end to the outer vessel 12, as by welding. The upper end of the inner tube 42 includes a flange 44 to which is fastened the mounting flange 46 of a cryogenic pump 40. The mounting flange 46 is provided with a number of mounting bolts 48 which thread into corresponding bores 49 in the tube flange 44. Both the pump flange 46 and the tube flange 44 may be provided with circular grooves 47 for seating a resilient 0-ring 50 to ensure a gas-tight seal at the upper end 38 of the pump mounting tube 34 when the pump flange 46 is mounted to the tube flange 44.
The lower ends of the inner tube 42 and outer tube 52 are joined in an air tight seal 36 achieved e.g. by welding together the lower rims of the coaxial tubes 42 and 52. The upper end 55 of the outer tube 52 is connected also as by welding to the wall of the inner vessel 14. The inside diameter of the outer tube 52 is somewhat greater than the outside diameter of the inner tube 42 so as to define a jacket space 54 between the two tubes. This jacket space is open at the top of the outer tube 52 and is thus in communication with the insulation space 16 between the outer vessel 12 and the inner vessel 14. As the insulation space 16 is evacuated, the jacket space 54 between the inner and outer tubes is also evacuated and forms an insulating vacuum jacket around the inner tube 42.
The upper end of the inner tube 42 is ^n thermal contact with the outer vessel wall 12 and a temperature gradient is therefore established along the inner tube which ranges from close to ambient temperature near the flange 44 at the top of the tube down to the boiling point of the cryogen at the lower end 36 of the pump mounting tube 34. The outer tube 52 is submerged in the cryogen and is in thermal contact at its upper end only with the inner vessel wall 14 which is, of course, near cryogen temperature. The

only contact between the inner and outer tubes occurs at their joint lower rims 36.
The cryogenic pump includes a pump drive head 60 which is external to the cryogenic tank and thus readily accessible for repair or maintenance. A pump extension tube 62 extends downwardly from the drive head 60 and supports at its lower end a pump piston and intake valve unit 64. Tie pump piston is reciprocated by a drive shaft enclosed in the extension tube 62 and not visible in the drawings. The length of the pump extension tube 62 is such that the pump piston and intake valve unit 64 is suspended near the bottom of the inner vessel 14* so as to draw in cryogen from the bottom of the vessel. A pump output tube 66 extends upwardly from the cryogen intake unit 64 through the inner pump mounting tube 42 adjacent to the pump extension tube 62, passes through the pump mounting flange 46 and terminates in an external cryogen discharge port 68 which delivers the cryogen output of the pump 40.
When the inner vessel 14 of the cryogenic tank is initially filled with cryogen, the liquid tends to rise into the inner tube 42. However, as was earlier explained, this tube is relatively warm so that some of the cryogen within the pump mounting tube vaporizes. The upper end of the tube 42 is scaled by the pump flange 46 so that a pocket of trapped gas is formed in tube 42. An equilibrium condition will be reached in which the entire interior of the pump mounting .tube is filled with a pocket of gas whicn prevents additional cryogen from entering the tube. As a result, a gas liquid interface is established near the lower end 36 of the pump mounting tube 34. The gas within the pump mounting tube is a poor conductor of heat and thus serves to effectively insulate the cryogen at the bottom of the pump mounting tube. The inner tube 42 is insulated from the liquid cryogen filling the vessel 14 by means of the vacuum jacket defined by the outer tube 52 in order to prevent

cooling of the inner tube 42 along its entire length. Such cooling would occur if the inner tube 42 were immersed directly in cryogen and would sufficiently lower the temperature of the inner surface of the inner tube 42 to cause condensation of the trapped gas. This would reduce the volume of the gas pocket and allow liquid cryogen to rise into the pump mounting tube 34, thereby shortening the length of the thermal path established by the inner tube 42 as well as increasing the area of the cryogenic pump in direct contact with the liquid cryogen. The pump mounting tube 34 also serves to insulate the pump extension tube 62 against contact with the liquid cryogen since the portion of the pump extension tube within the pump mounting tube extends through the trapped gas pocket. Only the lowermost portion 64 of the cryogenic pump is actually in contact with the cryogen.
The length of the pump mounting tube 34 is made as long as possible in order to extend the thermal path established by the inner pump mounting tube 42. The wall of the inner tube 42 is made as thin as possible, e.g. of 0.065 inch stainless steel tubing, in order to minimize the cross section of the thermal path established by the inner pump mounting tube and minimize conduction of heat to the lower end 36 of the pump mounting tube. The outer tube 52 may be made of thicker walled tubing since it is not in thermal contact with the exterior environment. The inner surface of tube 52 and the outer surface of tube 42 are desirably highly polished in order to improve the thermal insulation characteristics of the vacuum jacket defined between the two tubes.
The thickness of the tubing used for the pump extension tube 62 and drive shaft is also kept to a minimum so as to minimize the cross section of the thermal path established thereby. Very thin materials can be used for the pump extension tube since it is in tension and only

supports the relatively small weight of the piston and intake unit 64.
Preferably, the inner tube 42 is stabilized relative to the outer tube 52 and inner vessel 14 by means of an insulating spider 70 which includes a collar 72 encircling the inner tube 42 below the flange 44 and three or more radial arms 73, extending from the collar 70 and secured at their outer ends to the inner vessel 14 by means of suitable fasteners 74. The insulating spider may be made of a material such as laminated plastic having good thermal insulating properties in order to avoid heat leakage from the relatively warm upper end of the inner pump mounting tube 42 to the cold inner vessel wall 14.
A further improvement in efficiency of the cryogenic tank is realized by using the double walled pump mounting tube 34 to support the inner vessel 14 in spaced relationship to the outer vessel 12. The flange 44 at the upper end of the inner tube 42 is secured as by welding to the wall of the outer vessel 12, and the upper end 55 of the outer tube 52 is secured to the rim of a suitably sized opening 57 in the top of the inner vessel 14. The joint between the upper end of the outer tube 52 and the inner vessel 14 may be reinforced by means of an annular corner brace 76 welded to both the outer tube 52 and the inside surface of the inner vessel wall 14 as best illustrated in
Figure 3. Assuming no other support for the inner vessel 14, it will be appreciated that the weight of the r inner vessel bears down on the upper end of the outer tube 52 which transmits the weight to the joint 36 between the inner and outer tubes at their common lower end. The inner vessel 14 and outer tube 52 in turn are suspended from the top of the outer vessel 12 by the inner tube 42. In this arrangement, the outer tube 52 is in a state of compression under the weight of the inner vessel 14, while the inner tube 42 is in a state of tension because -the

weight of the inner vessel 14 depends from the lower end of the inner tube. Since the tube 42 is in tension, it is possible to maintain the wall thickness of the inner tube 42 relatively thin so as to minimize the cross section of the thermal path along this tube, without compromising the strength of the tube wall required for supporting the weight of the relatively heavy inner vessel 14. The outer tube 52 however, is in compression and is thus made of a thicker walled tubing to prevent buckling under the weight of the inner vessel 14.
Preferably, the inner vessel 14 is supported at two additional points against rotation and oscillation, respectively, relative to the outer vessel 12. For example, a bottom support 78 may include a second insulating spider 80 which has a number of radial arms fastened at their outer ends 81 to the bottom of the inner vessel 14 and an apertured center portion 83 which receives a tubular stub 82 mounted to the bottom of the outer vessel 12. The inner vessel 14 is thus kept from oscillating within the outer vessel 12 as would occur if the inner vessel were simply suspended by means of the pump mounting tube 34. The inner vessel can be further restrained against rotation within the outer vessel 12 by means of an insulating side support 84. As the entire weight of the inner vessel can be suspended from the outer vessel 12 by means of the pump mounting tube 34, the bottom support 78 and side support 84 can be made of relatively light materials such as^laminated plastics which have good thermal

The inner vessel 14 may be formed by welding together along a seam 25 two elliptical end portions having a major ellipse axis which is two times the length of the minor ellipse axis in a vertical plane. In a horizontal plane the cryogenic tank may be circular. The outer shell may be made by welding a straight cylindrical middle portion between dished top and bottom portions along seams 27

and 29, respectively. The outer vessel 12 may be made of relatively thin sheet metal sufficiently rigid for supporting the combined weight of the inner tank and the stored cryogen. The inner vessel 14, however, will normally be made of thicker gauge plate in order to withstand the internal pressures of the cryogen. The insulation space 16 may be approximately one to two inches in width between the inner and outer vessels at the equator of the tank and will normally be evacuated to one micron of mercury. In addition to or in lieu of the radiation shield formed by the reflecting blanket 20, the insulation space 16 may be filled with a radiation inhibiting powder such as the material commercially known as Pearlite. In this case, the width of the insulation space may have to be increased to approximately six to eight inches.
The pump drive head 60 may be of the gas driven type known in the art which may be driven by the boiloff gases of the cryogenic storage tank itself through suitable conduits.
The outer tank 12 can be further provided with one or more lifting rings 22 affixed to the upper surface of the outer tank. A circular base flange 24 is welded about the lower end of the outher tank 12. The flange 24 supports the tank 12 when it is mounted on a platform provided with an opening for receiving the bottom of the cryogenic tank such that the base flange 24 rests on the platform* and the cryogenic tank is supported above or within the opening in the base. The insulated tank 10 can be further» provided with a gas phase fill tube 26 and a liquid phase fill tube 28 connected to the top and bottom respectively of the inner tank 14 and extending through the insulation space 16 to the exterior of the cryogenic tank. The tank is further provided with suitable instrument and full trycock tubes and other conduits leading into the inner vessel 14 as may be needed and are known in the art.
CMPI ?°

It must be understood that many alterations and modifications can be made by those having ordinary skill in the art to the structure of the present invention without departing from the spirit and scope of the invention. Therefore the presently illustrated embodiment has been shown only by way of example and for the purpose of clarity and should not be taken to limit the scope of the following claims.
OMPI

Claims (12)

1. A low boil-off cryogenic tank for use with a with built-in pump comprising: an insulated vessel; and a pump mounting tube extending through the wall of said insulated vessel, said pump mounting tube having an inner surface thermally insulated from both said vessel and cryogen stored within said vessel.

2. The cryogenic tank of Claim 1 further comprises a cryogenic pump extending into said vessel through said pump mounting tube.

3. The cryogenic tank of Claim 1 wherein said pump mounting tube is sealed against gas leakage from said vessel.

4. A cryogenic storage tank for use with built-in submerged pump comprising an outer vessel, an inner vessel and an insulation space therebetween, an outer tube within said inner vessel connected at its upper end to said inner vessel, an inner tube within said outer tube connected at -its upper end to said outer vessel a sealed annular space defined between said inner and outer tubes communicating with said insulation space, such that said inner tube is in thermal contact with the relatively warm outer vessel and said outer tube is in thermal contact with the coider inner vessel and connected to said inner tube only at ‘its lower r end.

5. The cryogenic tank of Claim 4 further comprising a pump drive head mounted externally to said outer vessel, a pump extension tube and body extending into said inner vessel through said inner tube and connected to a pump intake assembly positioned for pumping cryogen from said inner tank through an output conduit extending through said inner tube.

6. The cryogenic tank of Claim 4 wherein said inner vessel is suspended from said outer vessel by said outer and inner tubes, said outer tube being in compression while said inner tube is in tension such that said inner tube may be thus thin walled relative to said outer tube to minimize thermal flow into said inner vessel.

7. The cryogenic tank of Claim 4 wherein said insulation space and said annular space are evacuated to create a vacuum jacket about said inner tube and said inner vessel.

8. The cryogenic tank of Claim 4 further comprising thermal radiation barrier means disposed within said insulation space.

9. The cryogenic tank of Claim 4 further comprising means supporting said inner vessel against rotation and oscillation relative to said outer vessel.

10. The cryogenic tank of Claim 4 further comprising thermally insulating support means supporting the upper end of said inner tube against radial displacement within said outer tube.

11. The cryogenic tank of Claim 3 wherein said r cryogenic pump is provided with mounting means including means for sealing the upper end of said pump mounting tube.

12. A cryogenic storage tank for use with a built-in pump comprising an insulated vessel, a pump mounting tube extending through the wall of said insulated vessel, said pump mounting tube having an inner surface thermally insulated from both said vessel and the cryogen stored with said vessel, and a cryogenic pump extending into said vessel through said pump mounting tube, said pump mounting tube being sealed against gas leakage from said vessel.
y
OMPI »

AU25743/84A
1983-01-28
1984-01-27
Cryogenic storage tank with built-in pump

Ceased

AU564335B2
(en)

Applications Claiming Priority (2)

Application Number
Priority Date
Filing Date
Title

US06/462,102

US4472946A
(en)

1983-01-28
1983-01-28
Cryogenic storage tank with built-in pump

US462102

1983-01-28

Publications (2)

Publication Number
Publication Date

AU2574384A

AU2574384A
(en)

1984-08-15

AU564335B2
true

AU564335B2
(en)

1987-08-06

Family
ID=23835176
Family Applications (1)

Application Number
Title
Priority Date
Filing Date

AU25743/84A
Ceased

AU564335B2
(en)

1983-01-28
1984-01-27
Cryogenic storage tank with built-in pump

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US
(1)

US4472946A
(en)

EP
(1)

EP0135550B1
(en)

JP
(1)

JPS60500509A
(en)

AU
(1)

AU564335B2
(en)

CA
(1)

CA1235056A
(en)

DE
(1)

DE3470934D1
(en)

IL
(1)

IL70803A
(en)

WO
(1)

WO1984002969A1
(en)

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1983

1983-01-28
US
US06/462,102
patent/US4472946A/en
not_active
Expired – Lifetime

1984

1984-01-26
CA
CA000446127A
patent/CA1235056A/en
not_active
Expired

1984-01-27
IL
IL70803A
patent/IL70803A/en
unknown

1984-01-27
EP
EP84900922A
patent/EP0135550B1/en
not_active
Expired

1984-01-27
AU
AU25743/84A
patent/AU564335B2/en
not_active
Ceased

1984-01-27
JP
JP59500910A
patent/JPS60500509A/en
active
Pending

1984-01-27
WO
PCT/US1984/000110
patent/WO1984002969A1/en
active
IP Right Grant

1984-01-27
DE
DE8484900922T
patent/DE3470934D1/en
not_active
Expired

Also Published As

Publication number
Publication date

US4472946A
(en)

1984-09-25

DE3470934D1
(en)

1988-06-09

AU2574384A
(en)

1984-08-15

IL70803A
(en)

1987-11-30

JPS60500509A
(en)

1985-04-11

EP0135550B1
(en)

1988-05-04

CA1235056A
(en)

1988-04-12

WO1984002969A1
(en)

1984-08-02

EP0135550A1
(en)

1985-04-03

EP0135550A4
(en)

1985-07-01

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