KR102047992B1 - Insulating elements for sealed and thermally insulated tank - Google Patents

Insulating elements for sealed and thermally insulated tank Download PDF

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Publication number
KR102047992B1
KR102047992B1 KR1020147026312A KR20147026312A KR102047992B1 KR 102047992 B1 KR102047992 B1 KR 102047992B1 KR 1020147026312 A KR1020147026312 A KR 1020147026312A KR 20147026312 A KR20147026312 A KR 20147026312A KR 102047992 B1 KR102047992 B1 KR 102047992B1
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South Korea
Prior art keywords
thermal insulation
tank
panel
wall
insulation layer
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KR1020147026312A
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Korean (ko)
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KR20140130712A (en
Inventor
모하메드 사시
게리 칸럴
줄리엔 올리버
알랭 비르글
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가즈트랑스포르 에 떼끄니가즈
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    • 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
    • F17C3/00—Vessels not under pressure
    • F17C3/02—Vessels not under pressure with provision for thermal insulation
    • F17C3/025—Bulk storage in barges or on ships
    • F17C3/027—Wallpanels for so-called membrane tanks
    • 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
    • F17C2201/0147—Shape complex
    • F17C2201/0157—Polygonal
    • 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
    • F17C2201/05—Size
    • F17C2201/052—Size large (>1000 m3)
    • 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
    • F17C2203/0304—Thermal insulations by solid means
    • F17C2203/0329—Foam
    • F17C2203/0333—Polyurethane
    • 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
    • F17C2203/0304—Thermal insulations by solid means
    • F17C2203/0354—Wood
    • 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
    • F17C2203/0304—Thermal insulations by solid means
    • F17C2203/0358—Thermal insulations by solid means in form of panels
    • 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
    • F17C2203/06—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
    • F17C2203/0631—Three or more walls
    • 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
    • F17C2221/00—Handled fluid, in particular type of fluid
    • F17C2221/03—Mixtures
    • F17C2221/032—Hydrocarbons
    • F17C2221/033—Methane, e.g. natural gas, CNG, LNG, GNL, GNC, 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
    • 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
    • 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
    • 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
    • F17C2270/00—Applications
    • F17C2270/01—Applications for fluid transport or storage
    • F17C2270/0102—Applications for fluid transport or storage on or in the water
    • F17C2270/0105—Ships
    • F17C2270/0107—Wall panels

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

As a sealed thermal insulation tank,
A sealing wall, a substantially parallel hexahedral shape, is provided with a rigid thermal insulation layer 32 and an upper panel 20 connected to the thermal insulation layer 32 and a rigid lower panel 31 connected to the lower portion of the thermal insulation layer 32. A heat insulation wall comprising a heat insulation element,
The upper panel and the lower panel are each provided to be able to generate bending stresses up and down in the insulation element by differential expansion when the tank wall is in a temperature gradient, each of which has a coefficient of thermal expansion that is smaller than the thermal expansion coefficient of the insulation layer. Equipped,
The panels 20 and 31 and the insulation layer 32 have mutually modified bending stresses caused by differential expansion to prevent deformation by bending of the insulation element when the tank wall is in a state of temperature gradient between the inside and outside of the tank. Arranged to be calibrated.

Description

INSULATING ELEMENTS FOR SEALED AND THERMALLY INSULATED TANK}

FIELD OF THE INVENTION The present invention relates to the field of making sealed thermal insulation tanks. In particular, the present invention relates to a tank containing a cold fluid, such as a tank for storing and transporting liquefied gas at sea.

Closed thermal insulation tanks can be used in many industries to store cold and hot products. For example, in the energy sector, liquefied natural gas (LNG) is a liquid that can be stored at atmospheric pressure of about -163 ° C in a storage tank on the ground or a floating structural tank at sea.

According to one embodiment, the present invention provides a hermetic insulated tank installed in a load-bearing structure and for receiving low temperature fluid,

The tank wall is a sealing wall intended to be in contact with the product received in the tank,

A thermal insulation wall consisting of a plurality of thermal insulation elements juxtaposed to form a substantially uniform support surface with respect to the sealing wall,

It is provided in a substantially parallelepiped shape and is connected to the rigid thermal insulation layer and the rigid thermal insulation layer, supports the sealing wall, and has a thermal expansion coefficient below the upper panel 20 and the rigid thermal insulation layer which is smaller than the thermal expansion coefficient of the thermal insulation layer. And a thermal insulation element having a rigid bottom panel connected and having a thermal expansion coefficient less than that of the thermal insulation layer.

According to one embodiment, such a tank may have one or more of the features described below.

According to one embodiment, when the top panel, the bottom panel and the insulation layer are in a temperature gradient between the interior and the exterior of the tank, the bending stresses caused by the differential expansion are substantially mutually interrelated to prevent deformation due to bending of the insulation element. Arranged to be calibrated.

According to one embodiment, the lower panel has a bending stiffness less than the bending stiffness of the top panel.

According to one embodiment, the lower panel has a thickness thinner than the thickness of the upper panel.

According to one embodiment, the lower panel has slots extending through a portion of the thickness of the lower panel but extending parallel to one side of the lower panel.

According to one embodiment, the tank wall also has a second sealing wall and a second insulating wall, the second sealing wall being formed of parallel strips made of sheet metal with raised longitudinal edges to protrude toward the interior of the tank. 2 comprising parallel welding flanges projecting towards the interior of the tank to form a joint welded and sealed with adjacent raised longitudinal edges between two strips of sheet metal supported by an insulating wall; The resulting strips and welding flanges extend in the longitudinal direction of the insulating elements of the first insulating wall disposed on the second sealing wall,

The longitudinal edges and the welding flanges penetrate the lower panel and extend in the thickness direction of the thermal insulation layer of the thermal insulation elements and protrude into the longitudinal lower grooves parallel to the longitudinal sides of the thermal insulation element,

The lower panel has transverse slots penetrating a portion of the thickness of the lower panel, the slots extending in a direction perpendicular to the longitudinal lower grooves.

According to one embodiment, the top panel is provided to be capable of generating bending stress upwards by differential expansion in the thermal insulation element when the tank wall is in a temperature gradient between the interior and exterior of the tank.

According to one embodiment, the lower panel is provided to be capable of generating bending stress downwards by differential expansion in the thermal insulation element when the tank wall is in a temperature gradient between the interior and the exterior of the tank.

According to one embodiment, the bottom panel has longitudinal bottom panel portions separated by longitudinal bottom grooves, the elongated shims spanning both sides between two adjacent longitudinal bottom panel portions to reinforce the bottom panel. The seams extend in the thickness direction of the insulating element and separate the spaces in which the longitudinal edges and the welding flanges extend.

According to one embodiment, the shims are connected by a base of shims on longitudinal lower panel portions, the bases of the shims having channels extending along the shims and separating the space.

According to one embodiment, the shims have the form of an element shaped into a U shape, the shims having a flange at each end of the U and the longitudinal lower panel portions are flanges of the element formed below the longitudinally lower panel portions. The outer surface to which they are connected.

According to one embodiment, the plurality of shims are connected in a state arranged side by side across both sides between two adjacent longitudinal panel portions.

According to one embodiment, the thermal insulation element has an upper thermal insulation layer which firmly contacts the lower side of the upper panel and an intermediate panel which firmly contacts the lower thermal insulation layer, and the rigid thermal insulation layer has a lower thermal insulation layer connected below the intermediate panel. The lower panel is connected under the lower insulating layer,

The thermal insulation element has transverse slots passing through the longitudinal lower grooves and the lower panel and extending through the thickness direction of the lower thermal insulation layer,

The longitudinal lower grooves extend parallel to the longitudinal side of the thermal insulation element, and the transverse slots extend perpendicular to the longitudinal side of the thermal insulation element.

According to one embodiment, the longitudinal lower grooves and the transverse slots completely pass through the thickness of the lower thermal insulation layer.

According to one embodiment, the tank wall comprises a second sealing wall and a second insulating wall, the second sealing wall being parallel strips made of sheet metal with raised longitudinal edges to protrude toward the interior of the tank and the second sealing wall. With parallel weld flanges projecting towards the interior of the tank to form a joint welded and sealed with adjacent raised longitudinal edges between two strips of sheet metal each time supported on an insulating wall; The resulting strips and welding flanges extend in the longitudinal direction of the insulating elements of the first insulating wall disposed on the second sealing wall,

The longitudinal edges and the welding flanges protrude into the longitudinal lower grooves of the lower insulating layer.

According to one embodiment, the lower panel has a coefficient of thermal expansion that is lower than the coefficient of thermal expansion of the upper panel.

Such tanks may form part of a terrestrial storage facility for storing LNG, for example, or may be floating structures on shore or deep water, in particular methane tankers, gas storage / regasification facilities (FSRUs), floating crude oil production / storage / It may be installed in an unloading facility (FPSO).

According to one embodiment, a vessel for transporting cold liquid product comprises a double hull and a tank described above arranged in a double hull.

According to one embodiment, the present invention also provides a method for loading or unloading such a vessel, a method of conveying cold liquid product between a floating or above ground storage facility and a tank of a vessel via an insulated pipe.

According to one embodiment, the present invention provides a system for transporting cold liquid products, which system is insulated pipe designed to connect a vessel installed in the hull of the vessel to the vessel, floating storage or ground storage facility described above. And a pump for flowing a cold liquid product between the floating storage facility or the above-ground storage facility and the vessel of the vessel through the insulating pipe.

The present invention begins with the observation that when the closed adiabatic tank is filled with liquefied natural gas, the temperature difference between the outside of the tank and the inside of the tank produces a thermal gradient within the adiabatic elements. This thermal gradient can lead to differential expansion phenomena occurring in the insulating elements, whereby the fluid tight walls are also supported by bending. Such bending may occur, in particular, when the means for connecting the thermal insulation elements in the tank cannot absorb the bending stresses of the thermal insulation element. For example, a thermal insulation element is not connected to its peripheral area as well as to the central area of its lower surface.

An aspect of the present invention is to prevent deformation of the membrane of the tank wall supported by the insulating wall while keeping them substantially flat when they are in a thermal gradient caused by a tank full of cold product.

Aspects of the present invention seek to prevent bending of a thermal insulation element comprising a one-piece of rigid foam connected between a first panel and a second panel by correcting bending stresses occurring within the thermal insulation element by thermal shrinkage differences. Based on thought

Aspects of the present invention are based on the idea of correcting bending stresses by modifying the bending stiffness of a panel of an insulating element, for example, providing a slot in the panel or modifying the thickness of the panel.

Aspects of the present invention are based on the idea of correcting bending stress by ensuring a connection between a plurality of portions formed from one of the panels to ensure its continuity, for example by separating the plurality of separated panels of the panel by the shims. Connect the sites.

Aspects of the present invention are based on the idea of preventing deformation of the thermal insulation elements by dividing the thermal insulation elements beyond their thickness located below the middle panel disposed inside the thermal insulation foam layer, the intermediate panel being capable of reducing the bending stress of the thermal insulation elements. Arranged to calibrate.

Aspects of the present invention are based on the idea of preventing deformation of the thermal insulation element by selecting different heat shrink coefficients for each panel to compensate for the bending stresses generated within the thermal insulation element.

The invention will be clearly understood by different objects, descriptions, features and effects. In addition, these will become more apparent by various embodiments described below. However, these embodiments should not be construed as limited by the drawings and the reference numerals attached thereto.

1 is a partial perspective view of a cut in the tank wall.
FIG. 2 is a partial perspective view of the inside of a thermal insulation element suitable for forming the first thermal insulation wall of the tank wall of FIG. 1. FIG.
3 is an enlarged view of the region III including the transverse slots in FIG. 2.
4 is an enlarged view of a region IV including shims in FIG. 2.
FIG. 5 is a view similar to FIG. 4 showing a modification of the shim.
FIG. 6 is a perspective view of the underside of a thermal insulation element with shims such as shown in FIG. 5. FIG.
7 is a perspective view of the top of a variant of the thermal insulation element with the intermediate panel in FIG. 2.
8 and 9 are side views of the thermal insulation element shown in FIG. 7.
10 is a schematic view of the methane tank and the terminal for loading / unloading the tank.

The differential shrinkage phenomenon will be briefly mentioned through the simple example shown schematically in FIG.

Plywood panel 37 is firmly attached to the thick one-piece layer of polymer foam 36.

The layers of plywood panel 37 and polymer foam 36 are in a decreasing thermal gradient 38 state. This means that the temperature in the plywood panel 37 is lower than the temperature at the layer bottom 41 of the polymer foam 36.

Insulating foams have a higher coefficient of thermal expansion than plywood. In addition, the foam shrinks further by the ambient temperature than the plywood panel 37 in the thermal gradient 38 state. Since the layers of plywood panel 37 and polymer foam 36 are firmly attached and furthermore the layers of polymer foam 36 have greater bending stiffness than the plywood panels 37, panel 37 and polymer foam 36 The layer of) tends to bend along the convex curvature 39.

The same phenomenon can be observed in the second example schematically shown in FIG. 12, where the plywood panel 37 is firmly attached under the layer of the polymer foam 36. In this case, however, the polymer foam 36 and the panel 37 tend to bend along the convex curvature 40 opposite to the convex curvature 39 shown in the first example. Moreover, since the plywood panel 37 is located under the layer of the polyfoam 36, this panel 37 has a higher temperature than the first example for the same temperature gradient 38. In conclusion, the panel 37 shrinks less than the first example, resulting in a larger convex curvature 40 than the convex curvature 39 of the first example. This is because the difference in thermal shrinkage between the layer of polymer foam 36 and the panel 37 is greater than in the first example.

1 shows a partial view of the tank wall of a methane tanker. For convenience, the "top" refers to the case where it is located closer to the interior of the tank, and the "bottom" refers to the case where it is located closer to the load-supporting structure 8, and the It is independent of direction. The load-bearing structure 8 consists of an inner wall and a double hull of a ship.

The tank wall comprises a second insulating wall 1 supporting the second fluid tight wall 2. The second fluid tight wall 2 itself supports the first heat insulating wall 3 and is supported by the first fluid tight wall 4.

The second thermal insulation wall 1 and the first thermal insulation wall 3 consist of second thermal insulation elements 5 and first thermal insulation elements 6, respectively. The anchoring member 7 holds the second insulating elements 5 against the load-bearing structure 8. Such anchoring members can be manufactured by various methods, and in particular can be made with reference to French patent application 1162214. Other anchoring members are disclosed in FR2887010. It is not limited to this example. The anchoring members 7 can be connected to the load-bearing structure 1 by, for example, a stud (not shown) welded to the load-bearing structure 8.

The second elements 5 have grooves 9 having an inverted-T shaped cross section. The grooves 9 receive the welding support 9 in the form of metal strips bent in an L shape in a sliding manner. Strikes 10 with raised edges are welded to this welding support (not shown). Strikes 10 made of steel or nickel having such a low coefficient of expansion form a second fluid tight wall 2.

The first elements 6 are supported on the second fluid tight wall 2. The first elements 6 have grooves 11 for receiving raised edges 12 of the strokes 10 which are welded to the welding supports.

The first fixing member 13 holds the first insulating elements 6 with respect to the second insulating wall 3.

These first fastening members 13 are in particular disclosed in French patent application 1250214. However, the present invention is not limited to this type of fixing member, and for example, the fixing members disclosed in FR2887010 may be used. It is not limited to this example.

The first thermal insulation elements 6 and the second thermal insulation elements 5 have a parallelepiped shape. The first heat insulating cases 6 and the second heat insulating cases 5 are arranged in a respective rectangular grid pattern on the respective heat insulating walls 1, 3.

Like the second insulating elements, the first insulating elements 6 have inverted-T shaped grooves 14. The grooves 14 receive an L-shaped welding support 14 welded to the strakes 15 with raised edges 16. These strikes 15 form the first fluid tight wall 4.

The second elements 5 of the second insulating wall 3 are supported by the load-bearing structure 8 by the beads of the mastic 17 forming parallel lines.

2 shows in more detail first insulating elements 6 suitable for a first insulating wall 3. The first thermal insulation element 6 has a lower panel 18 made of plywood which is supported on the second thermal insulation wall 1. The layer of insulation foam 19 made of polyurethane reinforced with glass fibers is firmly attached to the upper surface of the lower panel 18 and extends inwardly of the tank. The top panel 20 made of plywood is firmly attached to the top surface of the layer of foam 19. Two grooves 11 having a width of 8 mm penetrate the lower panel 18 in the longitudinal direction corresponding to the direction extending to the longitudinal side 23 of the panel. The grooves 11 extend in each situation at equal intervals on each longitudinal side 23 and partition the lower panel 18 into an intermediate panel 21 and two side panels 22.

The first thermal insulation element 6 comprises a housing formed in the thickness direction of the thermal insulation layer 19 and the lower panel 18. The housing extends in the longitudinal direction of the thermal insulation element at the center of the width of the thermal insulation element. Two fixing supports 41 are arranged in the housing of the first insulating element 6 in the central region of the insulating element 6. In particular, the fixing supports 41 are in each case centered on one quarter of the length of the thermal insulation element 6 from the short side of the thermal insulation element 6. The fixed supports 41 are connected to the lower panel 18.

Returning to FIG. 1, it can be seen that studs 42 are connected to the second insulating elements in a sealed manner through the second fluid tight wall 2 and extend along the direction of the first insulating wall 3. . The studs 42 are connected to the fixed support 41 in the first thermal insulation element 6 such that the first thermal insulation elements 6 are retained on the second thermal insulation wall 1.

According to one embodiment, the insulating element 6 has a thickness of 100 mm, a width of 1000 mm to 1200 mm and a length of 2000 mm to 3000 mm. More specifically, each of the upper panel 20 and the lower panel 18 has a thickness of 12 mm, and the layer of the insulation foam 19 has a thickness of 76 mm.

When the tank is filled with liquefied natural gas, the first fluid tight wall 4 has a temperature of -163 ° C. The temperature outside the tank is higher than the temperature of the first fluid tight membrane 4. In conclusion, the first thermal insulation element 6 is in a thermal gradient state. In particular, the temperature varies from -163 ° C of the top panel 20 to a higher temperature in the bottom panel 17, such as -117 ° C.

If the thermal insulation element 6 is in this temperature gradient, the thermal insulation layer 19 and the panels are subject to heat shrinkage. However, the coefficients of thermal expansion of the plywood constituting the panels 18 and 20 and the coefficients of thermal expansion of the insulating foam 19 are 5.5 * 10 -6 m / m / K and 18 * 10 -6 m / m / K, respectively, and the panel 18 , 20) and the temperature of the layer of foam 19 depend on the height of the thermal insulation element 6. In addition, the shrinking of the panels 18, 20 and the shrinking of the foam 19 layer are different. More specifically, the heat shrinkage of the layer of foam 19 is greater than the heat shrinkage of the panels 18, 20. The heat shrink of the top panel 20 is greater than the heat shrink of the bottom panel 18. As a result, the panels 18, 20 exert a bending stress on the layer of foam 19.

The bending stress is especially explained in that the bending stiffness of the foam layer 19 is greater than the bending stiffness of the plywood panels 18, 20 because it has a thicker thickness than the plywood panels 18, 20.

Specifically, the Young's modulus and the Young's modulus of the plywood are approximately E plywood = 10000 MPa and E foam = 100 MPa, respectively. Furthermore, the section modulus proportional to the third square of the thickness is

I form = (100-12-12) 3 = 438,976mm 3

For plywood I plywood = (12) 3 = 1,727 mm 3

The bending stiffnesses of the plywood and foam are approximately as follows respectively.

Figure 112014089214474-pct00001

Figure 112014089214474-pct00002

The insulating layer 19 also tends to bend itself according to the differential of heat shrink. In particular, the heat shrink depends on the height in the thickness direction of the heat insulation layer because of the temperature gradient in the thickness direction of the tank wall.

However, the first fastening members 13 are connected to the central region of the thermal insulation element and not to the thermal insulation element 6 with respect to the second thermal insulation wall 1. The perimeter of the insulating element 6 is independent of the second insulating wall. In addition, the bending deformation of the thermal insulation element 6 is not prevented by the first fixing members 13.

In this embodiment, in order to balance the bending stress in the thermal insulation element 6 and thus avoid deformation of the thermal insulation element 6, thirteen transverse slots 24 are parallel to the short side 25. Extends across the entire width of the second thermal insulation element in the direction. The transverse slots 24 are arranged at regular intervals along the longitudinal direction of the first thermal insulation element 6.

The function of the transverse slots 24 is to reduce the longitudinal stiffness of the lower panel 18.

3 shows in detail a side view of one of the transverse slots 24. This transverse slot 24 does not penetrate the entire thickness of the panel 18. In addition, the reduced portion 26 of the lower panel 18 is retained and creates residual longitudinal stresses between the two portions of the lower panel located on either side of the slots.

The transverse slots 24 have a depth of 10 mm inside the lower panel 18 and a width of 4 mm.

In contrast to the transverse slots 24, the groove 11 penetrates in the thickness direction of the lower panel 18 and divides the lower panel 18 into two side panels 22 and an intermediate panel 21. As a result, the side stiffness of the lower panel 18 is weakened. Shims 28 are used in this embodiment to reset the lateral stiffness to a sufficient level between the side panels 22 and the intermediate panel 21. These shims are shown in FIG. 4. Each shim 27 consists of a bar having portions of an isosceles trapezoid shape.

 According to one embodiment, each shim 27 has a base having a width of 38 mm and a thickness of 24.5 mm. Both sides of the trapezoidal part have an inclination of 20 ° with respect to the thickness direction perpendicular to the lower panel 20.

The base 28 of the shim 27 is connected in a state spanning both the edges adjacent to the upper surface of the intermediate panel 21 and any one side panel 22. Shims 27 are connected to lower panel 18 by adhesive bonding, staples or screwing. Moreover, the groove 11 extends partially inside the shim 27 to have a thickness of 12 mm.

Shims 27 generate lateral stiffness of lower panel 18 by joining portions 21, 22 of lower panel 18 while the raised edges 12 enter inside grooves 11. . When the thermal insulation element is in a thermal gradient, the lower panel to which the shims are connected compensates for the bending occurring by the upper panel. In addition, shims 27 relieve stress concentration in the bottom of groove 11 and in the foam of insulating layer 19.

  In order to receive the shims 27, the layer of insulation foam 19 has housings 30 having a shape similar to the shape of the shims 27. Portions of these housings may be provided with the same size as the shims 27 or may be provided with a substantially larger size to allow gaps between the shims 27 and the foams of the thermal insulation layer 19.

In order to firmly attach the lower panel 18, it is also possible to proceed in the manner described below: the housings are machined in a layer of insulation foam 19 and the shims 27 are connected to the lower panel 18. The bottom panel 18 is then firmly attached to the layer of insulating foam 19.

Preferably, the plurality of shims 27 are arranged side by side on both sides of the groove 11 and are connected along the length of the thermal insulation element 6. Moreover, the shims 27 are preferably arranged side by side in a spaced apart state. In this way, the shims 27 do not reinforce the lower panel 18 along its length.

An inverted-T shaped groove 9 extends along each of the grooves 11, on top of each of the grooves 11.

Correction of the bending stress prevents the bending of the thermal insulation element 6 such that the thermal insulation element 6 is supported by the second thermal insulation wall 1 all over its bottom face. It is possible to provide a maximum bending strain of 1 mm within the effect of the gradient, furthermore, this correction limits the forces in the anchoring means 6 and concentrates the stresses in the material which constitutes the various elements of the insulating element 6. In addition, the first fluid tight membrane 4 is not bent by the first heat insulating element 6 supporting the first fluid tight membrane 4.

An alternative to the shims disclosed in connection with FIGS. 2 to 4 is to use shims in the form of metal forming elements 29 made of stainless steel. This forming element 29 is disclosed in connection with FIGS. 5 and 6. The forming element 29 is connected below the lower panel 18 and receives the raised edges 12 of the metal strikes 10. At its end, the forming element 29 is formed in the groove 11 in the thickness direction. It has a U shape 43 extending up to 25 mm in height to 28. The plate 91 is connected to each of the U-shaped branches 43 of the forming element and in a direction parallel to the bottom of the lower panel 18. These two plates 91 are connected to the side panels 22 on the surface 30 provided rearward with respect to the bottom of the middle panel 21 and the lower panel 18, respectively. In this way, the forming elements 29 do not protrude out of the lower panel 29. The shims can be connected by riveting, screwing, adhesive bonding or any other fastening method.

Compared to the method for firm bonding of the lower panel 18 shown in connection with FIG. 2, the forming elements 29 can be connected after the lower panel is firmly attached.

Each forming element 29 has a base 38 mm wide and 24.5 mm thick. The two sides of the trapezoidal part have an inclination of 20 ° with respect to the thickness direction perpendicular to the lower panel 20.

Each forming element 29 is formed by a metal plate 3 mm thick. The forming element 29 extends 25 mm in the height direction 28. The width of the forming element 29 and the width between the two U-shaped branches 43 are 50 mm and 6 mm, respectively.

In a similar manner to the shim 27, a plurality of forming elements 29 are arranged and connected side by side to each groove 11 of the lower panel 18. This arrangement is shown in FIG. 6, which is similar to that shown in relation to FIG. 2. Each of the two grooves 11 has six forming elements 29. The forming elements 29 extend between two transverse slots 24 or between one transverse slot 24 and one edge of the lower panel 18.

More specifically, each end of the groove 11 has a forming element 29, wherein the forming elements 29 are then spaced apart by three transverse slots 24, where the transverse slots 24 Excluding the two central forming elements 29 juxtaposed on each side of the).

7 to 9 show another insulating element suitable for the first insulating wall. This thermal insulation element 6 has a similar size to the thermal insulation element shown in FIG. 2 and is also similar to the top panel 20. The upper thermal insulation layer 32 is firmly attached to the lower side of the upper panel 20. The middle panel 31 having a thickness of 4 mm is firmly attached to the lower side of the upper insulating layer 32. The lower layer of insulation foam 33 having the same thickness as the upper insulation layer 32 is firmly attached and extends under the middle panel 31. The bottom panel 18 is firmly attached to the bottom layer 33 and supports the second fluid tight membrane. The lower panel 18 and the upper panel 20 each have the same thickness, for example 12 mm thick.

The transverse grooves 34 and the longitudinal grooves 11 divide the lower panel into rectangular portions 35 and extend in the thickness direction of the lower insulating layer 33. The transverse grooves 34 and the longitudinal grooves 11 extend in the thermal insulation element and below the intermediate panel 31. More specifically, the grooves are machined to a depth of 35 mm and the thickness of each is 4 mm and 8 mm. These grooves separate the areas in the lower thermal insulation layer 33 and the lower panel 18. The longitudinal groove 11 receives the raised edge 12 of the strokes 11.

 However, the sizes of the grooves 11 and 34 may be different from each other. In addition, in one variant, these grooves 11, 34 can penetrate the ends in the lower insulation layer 33 and the intermediate panel 31 as a whole.

 The transverse grooves 34 and the longitudinal grooves 11 divide the lower panel 18 and the lower insulating layer 33. In this way, the lateral grooves 34 and the longitudinal grooves 11 make it possible to eliminate the longitudinal bending stiffness and the lateral bending stiffness of each of the lower layer and the lower panel 18 of the insulating foam 33. In addition, the bending stress caused by the change of the thermal gradient along the height in the thickness direction is prevented in the lower heat insulating layer 33 and the lower panel 18.

In a general manner, dividing the bottom panel 18 and the bottom insulation layer 33 is a differential heat between the bottom panel 18 and the layers of the insulation foam 33, 32 compared to not dividing the bottom panel and the insulation layer. Reduces the impact of the gradient

The function of the intermediate panel 31 is to generate bending stress as opposed to the bending stress generated by the top panel 20 in the thermal insulation element. In the thermal insulation element shown in FIGS. 7-9, the intermediate panel 31 is less thick than the top panel 20, which makes it possible to compensate for the bending exerted by the top panel 20. Moreover, the presence of the intermediate panel 31 makes it possible to prevent concentration of stress at the bottom of the grooves 11, 34.

Moreover, the intermediate panel 31 enables the insulating element to be reinforced or stabilized.

In a similar manner, the lower panel 18 of the thermal insulation element can be provided thinner than the upper panel 20. In addition, the insulating element suitably provided for the insulating wall from FIG. 1 may consist of an insulating element similar to the insulating element 6 shown in FIG. 2, and the lower panel 18 may not have transverse slots but may have a similar thickness. It may be provided in 4mm instead of 12mm.

In another variant of the thermal insulation element, the lower panel 18 and the upper panel 20 have the same thickness. However, the lower panel 18 has a different coefficient of expansion than the upper panel 20. More specifically, the upper panel has an expansion coefficient of 5.5 * 10 −6 m / m / K, and the lower panel 18 is made of a material having an expansion coefficient calculated as follows.

Figure 112014089214474-pct00003

Here, ΔTtoppanel and ΔTbottompanel are the temperature difference at the ambient temperature and the temperature of each panel 18, 20 when the tank is full. In this way, the thermal shrinkage of the panels 18, 20 is the same while the temperature gradient is formed.

The above insulation elements can also be used to implement the second insulation wall.

The tanks described above can be used in a variety of installations, such as ground facilities or methane tankers or similar floating structures.

The tanks can be manufactured from other well-known geometries such as, for example, prismatic structures on the double hull of a ship or cylinder structures on the ground. Referring to FIG. 10, a cutaway view of a methane tanker 70 shows a hermetic sealed tank 71 in the form of an overall prism installed within a double hull 72 of a vessel. The tank wall 71 is a first fluid hermetic wall intended for contact with the LNG contained in the tank, a second fluid hermetic wall and a first fluid hermetic wall and a second fluid disposed between the first fluid hermetic wall and the ship's double hull. Two insulating walls respectively disposed between the hermetic wall and between the second fluid tight wall and the double hull 72.

By a method well known per se, the loading / unloading pipes arranged on the upper deck of the ship can be connected by a suitable connector to load / unload LNG cargo between the tank 71.

10 shows an example of a marine terminal that includes a loading / unloading station 75, a subsea pipe 76, and a ground facility 77. The loading / unloading station 75 is a stationary marine facility that includes a movable arm 74 and a tower 78 that supports the movable arm 74. The movable arm 74 carries a number of insulated flexible pipes 79 that can be connected to the loading / unloading pipe 73. The pivotable movable arm 74 is adapted for methane tankers of all sizes. The connecting pipe (not shown) extends into the tower 78. The loading / unloading station 75 enables loading and unloading between the methane tanker 70 and the ground insulation structure 77. The ground insulation structure 77 includes connecting pipes 81 connected to the loading / unloading station 75 by the liquefied gas storage tank 80 and the subsea pipe 76. The subsea pipe 76 allows liquefied gas to be transferred between the loading / unloading station 75 and the ground insulation structure 77 over long distances, such as 5 km away, thereby allowing the methane tanker 70 to ship. Can be located far from the beach during unloading.

 In order to generate the pressure required for the delivery of liquefied gas, it is possible to use pumps which are shipped and carried on the vessel 70 and / or pumps which are mounted on the ground insulation structure 77 and / or pumps mounted on the loading / unloading station. .

Although the present invention has been described with respect to specific embodiments, it is not limited to these embodiments, and the technical equivalents of the above described means and combinations thereof within the scope of the present invention include all such equivalents if they fall within the scope of the present invention. It is self-evident.

The use of "includes" and its use does not exclude the presence of other elements or steps than those specified in the claims. The use of an indefinite article on a component or step does not exclude the presence of multiple components or steps unless otherwise specified.

In the claims, any reference signs placed between parentheses shall not be construed as limiting the claim.

Claims (12)

A hermetic insulated tank disposed in a load-supporting structure 8 for receiving low temperature fluid,
Tank wall,
A first sealing wall 4 provided with intent to contact a product received in the tank;
A first insulating wall (3) consisting of a plurality of insulating elements (5, 6) juxtaposed to form a uniform support surface for the first sealing wall;
It has a parallelepiped shape and is directly or indirectly connected to the rigid thermal insulation layers 19 and 33 and the rigid thermal insulation layer and supports the first sealing wall and has a thermal expansion smaller than the thermal expansion coefficient of the rigid thermal insulation layer. A thermal insulation element having an upper panel 20 having a coefficient and a rigid lower panel 18 connected below the rigid thermal insulation layer and having a thermal expansion coefficient smaller than that of the rigid thermal insulation layer;
A second sealing wall (2) and a second insulating wall (1);
The second sealing wall is supported on the second insulating wall and parallel strips of sheet metal 10 with the longitudinal edges 12 raised so as to project toward the interior of the tank and each time made of sheet metal 10. Parallel welding flanges protruding toward the inside of the tank to form a joint that is sealed and welded with the adjacent longitudinal edges raised between the two strips, the strips of sheet metal and the welding flanges Extend longitudinally of the insulating elements of the first insulating wall disposed on the second sealing wall,
The longitudinal edges and the weld flanges penetrate the lower panel 18 and extend in the thickness direction of the rigid thermal insulation layer of the thermal insulation elements, the first thermal insulation extending parallel to the longitudinal sides of the thermal insulation element. Protrudes into the longitudinal lower groove 11 of the wall 3,
The lower panel has transverse slots 24, 34 extending through a portion of the thickness of the lower panel 18, the slots extending in a direction perpendicular to the longitudinal lower grooves 11. Hermetic insulated tank. The method of claim 1,
The thermal insulation element has an upper thermal insulation layer 32 which firmly contacts the lower side of the upper panel and an intermediate panel 31 which firmly contacts the lower portion of the upper thermal insulation layer 32, the rigid thermal insulation layer 33. ) Forms a lower thermal insulation layer 33 connected to the lower portion of the intermediate panel 31, and the lower panel 18 is connected to the lower thermal insulation layer,
The thermal insulation element has the longitudinal lower grooves 11, the transverse slots 34 passing through the lower panel and extending in the thickness direction of the lower thermal insulation layer 33,
And the longitudinal lower grooves and the transverse slots each extend perpendicular and parallel to the longitudinal side of the thermal insulation element. The method of claim 2,
The longitudinal lower grooves (11) and the transverse slots (34) are completely insulated in the thickness direction of the lower thermal insulation layer (33). The method according to any one of claims 1 to 3,
The lower panel has longitudinal lower panel portions 21, 22 separated by the longitudinal lower grooves 11,
Extending shims 27 and 29 are connected across both sides between two adjacent longitudinal lower panel portions to reinforce the lower panel,
And the shims extend in the thickness direction of the rigid thermal insulation layer and separate a space in which the longitudinal edges and the welding flanges extend. The method of claim 4, wherein
The shims 27 are connected by the base 28 of the shims 27 on the longitudinal lower panel portions 21, 22, the base 28 of the shims 27 extending along the shims and Closed insulation tank having a channel for separating the space. The method of claim 4, wherein
The shims 29 have the form of elements shaped into a U shape 43, the shims having flanges at each end of the U shape,
And said longitudinal lower panel portions have an outer surface (30) below said longitudinal lower panel portions to which flanges of said shaped elements are connected. The method of claim 4, wherein
And a plurality of shims (27, 29) are connected in parallel and on both sides between the two adjacent longitudinal panel portions. The method of claim 1,
The lower panel (18) has a thermal expansion coefficient greater than the thermal expansion coefficient of the upper panel (20). The method according to any one of claims 1 to 3,
The upper panel is provided to be capable of generating bending stress upwards in the insulating element by differential expansion when the tank wall is in a state of temperature gradient between the inside and the outside of the tank, and the lower panel is configured to allow the tank wall to When there is a temperature gradient between the inside and the outside of the tank, it is possible to generate bending stress downward on the insulation element by differential expansion,
The upper panel, the lower panel and the rigid thermal insulation layer are caused by the differential expansion to prevent deformation by bending of the thermal insulation element when the tank wall is in a state of temperature gradient between the interior and exterior of the tank. An enclosed insulated tank in which bending stresses are arranged to be mutually compensated. In a vessel 70 for transporting a low temperature liquid product,
The vessel comprises a double hull (72) and a tank (71) of any one of claims 1 to 3 disposed in the double hull. In the method of using the vessel 70 according to claim 10 for loading and unloading low-temperature liquid products,
The low temperature liquid product is a method of using a ship that is transferred between the floating or above-ground storage facility (77) and the tank of the vessel (70) through a heat insulating pipe (73, 79, 76, 81). In a transport system for low temperature liquid products,
Insulation pipes (73,79,76,81) and the thermal insulation provided to connect the tank (71) installed on the hull of the vessel to the vessel 70, floating storage facility or ground storage facility (77) according to claim 10 A pump for flowing a low temperature liquid product between the floating storage facility or above ground storage facility and a tank of the vessel through a pipe.
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FR1251523 2012-02-20
FR1251523A FR2987100B1 (en) 2012-02-20 2012-02-20 CALORIFYING ELEMENTS FOR SEALED AND THERMALLY INSULATED TANKS
PCT/FR2013/050325 WO2013124573A1 (en) 2012-02-20 2013-02-18 Insulating elements for sealed and thermally insulated tank

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WO2013124573A1 (en) 2013-08-29
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FR2987100B1 (en) 2015-04-10
FR2987100A1 (en) 2013-08-23

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