Sealed heat insulation tank
阅读说明:本技术 密封隔热罐 (Sealed heat insulation tank ) 是由 安托万·菲利普 塞德里克·莫雷尔 塞巴斯蒂安·德拉诺 安托万·布戈 于 2019-01-22 设计创作,主要内容包括:本发明涉及一种用于储存液化气的密封隔热罐,包括:一隔热屏障(5),其包括至少两个隔热板(14),每个隔热板(14)包括一顶板(14),顶板限定一支撑表面(36),密封膜(6)抵靠在该支撑表面(36)上,所述两个隔热板(14)的顶板(19)均具有其中安装有焊接支架的凹槽(21),所述两个隔热板(14)的所述凹槽(21)对齐且在纵向方向上延伸;-至少所述两个隔热板(14)中的一个隔热板中的凹槽(21)具有面向另一隔热板(14)的一端,该端通过该凹口(33)延伸,所述凹口(33)设计为使得所述焊接支架(23)不被保持在所述凹口(33)的区域内的所述隔热板(14)上。(The invention relates to a sealed and thermally insulated tank for storing liquefied gas, comprising: -a thermal insulation barrier (5) comprising at least two thermal insulation panels (14), each thermal insulation panel (14) comprising a top panel (14) defining a support surface (36) against which support surface (36) a sealing film (6) rests, the top panels (19) of the two thermal insulation panels (14) each having a groove (21) in which a welding bracket is mounted, the grooves (21) of the two thermal insulation panels (14) being aligned and extending in a longitudinal direction; -the groove (21) in at least one of the two heat insulation panels (14) has an end facing the other heat insulation panel (14) which end extends through the recess (33), the recess (33) being designed such that the welding bracket (23) is not held on the heat insulation panel (14) in the region of the recess (33).)
1. A sealed and insulated tank for storing liquefied gas, comprising a wall (1), the tank comprising, in order from the outside to the inside of the tank in the thickness direction of the wall (1): -a heat-insulating barrier (5) and a sealing film (6) resting on said heat-insulating barrier (5);
-the thermal insulation barrier (5) comprises at least two thermal insulation panels (14), each having an upper panel (19) defining a support surface (36) against which the sealing film (6) rests, the upper panels (19) of the thermal insulation panels (14) each having a groove (21) in which a welding bracket (23) is mounted, the grooves (21) in the two thermal insulation panels (14) being aligned and extending in a longitudinal direction; the welding bracket (23) extends in a longitudinal direction and comprises a welding flange (24) and an anchoring flange (25) inclined with respect to the welding flange (24); each recess (21) opens out into the support surface (36) and has a return (27), in which return (27) the anchoring flange (25) of the welding bracket (23) is accommodated, the return (27) forming a retaining portion (28) in the respective heat shield (14) between the return (27) and the support surface (26), against which retaining portion (28) the anchoring flange abuts in order to retain the welding bracket (23) on the heat shield (14);
-the sealing membrane (6) comprises, on either side of the welding support (23), at least two metal strips (22) extending parallel to the longitudinal direction, the strips (22) having a middle portion (29) abutting against the support surface (36) and two folded-over edges (30), the two folded-over edges (30) extending parallel to the longitudinal direction and projecting from the middle portion (29) towards the inside of the tank, one of the folded-over edges (30) of each of the two strips (22) being welded to a welding flange (24) of the welding support (23);
-the sealed insulating tank is characterized in that at least one groove (21) of one of the two insulating panels (14) has an end facing the other insulating panel (14) which extends through a recess (33), the recess (33) opening into the support surface (36) and being formed in the longitudinal direction at least in the continuation of the groove (21) and the retaining portion (28) such that the welding bracket (23) is not fixed in the insulating panel (14) in the region (33) of the recess.
2. The sealed, thermally insulated tank according to claim 1, characterized in that the two insulating panels (14) each have two transverse edges (32) perpendicular to the longitudinal direction, the adjacent transverse edges (32) of the two insulating panels (14) being spaced apart from each other by a gap (31) having a width in the longitudinal direction of less than 20 mm.
3. The sealed, thermally insulated tank according to claim 1 or 2, characterized in that the grooves (21) of the insulating panels (14) are spaced apart by a spacing i, the longitudinal dimension of which is between 20mm and 70 mm.
4. The sealed, thermally insulated tank according to any of claims 1 to 3, characterized in that the groove (21) of each of the two insulating panels (14) has one end facing the other insulating panel (14), which end extends through a recess (33), which recess (33) opens into the support surface (36), each recess (33) being formed in the longitudinal direction at least in the continuation of the groove (21) and the retaining portion (28) such that the welding bracket (23) is not retained at the recess (33).
5. A sealed and thermally insulated tank according to any of claims 1 to 4, characterized in that the or each recess (33) has a dimension n in the longitudinal direction of between 5mm and 30 mm.
6. The sealed, thermally insulated tank according to any of claims 1 to 5, characterized in that the depth p of the or each recess (33) is greater than or equal to the depth of the groove (21).
7. The sealed, thermally insulated tank according to any of claims 1 to 6, characterized in that the recess (33) has a bottom (34) and a plurality of side walls (35) connecting the bottom (34) to the support surface (36).
8. The sealed, insulated tank according to claim 7, characterized in that the bottom (34) of the recess (33) has a sloping slope such that the depth p of the recess (33) decreases in the direction of the groove (21).
9. The sealed, insulated tank of claim 7 or 8, characterized in that the side wall (35) of the recess (33) intersects the groove by means of a chamfer or fillet (37).
10. The sealed, thermally insulated tank according to any of claims 1 to 9, characterized in that the two insulating panels (14) each have two lateral edges (32) perpendicular to the longitudinal direction, the upper plate (19) of each of the two insulating panels (14) comprising a recess (38) along the lateral edge of the insulating panel (14) facing the other insulating panel (14), the recess (38) extending perpendicular to the longitudinal direction from one end of the insulating panel (14) to the other end, so that the slats (22) are not supported by the supporting surface (36) along the lateral edges of the insulating panel (14).
11. A sealed and insulated tank according to claim 10, characterized in that the or each recess (33) opens into one of the recesses (38).
12. Sealed and insulated tank according to claim 10 or 11, characterized in that the adjacent transverse edges (32) of the two insulating panels (14) are spaced apart from each other by a gap (31) having a width in the longitudinal direction of less than 5 mm.
13. The sealed, thermally insulated tank according to claim 12, characterized in that the sum of the longitudinal dimension of the recess (38) of each of the two insulating panels (14) and the width of the gap (31) formed between the insulating panels (14) is between 7mm and 25 mm.
14. Vessel (70) for transporting fluids, characterized in that it comprises a double shell (72) and a tank (71) according to any of claims 1 to 13 arranged inside the double shell (72).
15. A fluid delivery system, comprising: a vessel (70) according to claim 14, arranged to connect the tank (71) mounted in the hull to insulated piping (73, 79, 76, 81) of an offshore or onshore storage facility (77), and pumps for flowing fluids between the offshore or onshore storage facility and the vessel's tank through the insulated piping.
16. A method for loading or unloading a vessel (70) according to claim 14, wherein the fluid is transferred from an offshore or onshore storage facility (77) to the tanks of the vessel (71) or from the tanks of the vessel (71) to the offshore or onshore storage facility (77) by insulated pipes (73, 79, 76, 81).
Technical Field
The present invention relates to the field of sealed insulated tanks with membranes for storing and/or transporting fluids, such as liquefied gases.
The sealed insulated tank with membrane is particularly useful for storing liquefied natural Gas (GNL) stored at about-163 ℃ at atmospheric pressure. These tanks may be mounted on land or on a floating structure. Where these tanks are installed on a floating structure, the tanks may be used to transport liquefied natural gas or to contain liquefied natural gas for use as fuel to propel the floating structure.
Background
Document WO2014096600 discloses a sealed and thermally insulated tank for storing liquefied natural gas, which is arranged in a load-bearing structure, the tank wall having a multilayer structure, i.e. comprising, from the outside to the inside of the tank: a primary insulating barrier anchored to the load bearing structure; a primary sealing membrane supported by the secondary thermal barrier; a primary insulating barrier supported by the secondary sealing membrane; and a primary sealing membrane supported by the primary insulating barrier and adapted to be in contact with the liquefied natural gas stored in the tank.
Each of the primary and secondary thermal barriers comprises a set of primary and secondary heat-insulating panels, generally parallelepiped in shape, arranged side by side so as to form a support surface for the respective sealing membrane. The primary and secondary sealing membranes each comprise a continuous layer of sheet metal strip, the edges of which are turned up and welded to parallel welding brackets. The L-shaped welding bracket is fixed in a groove which is formed in a heat insulation plate of the main heat insulation clapboard or the secondary heat insulation clapboard. The primary and secondary heat insulating panels are easily deformed, which may cause a difference in height between the adjacent heat insulating panels in the thickness direction of the tank wall. Such deformation is more likely to occur due to the effects of liquid movement within the tank (known as "sloshing") and due to thermal gradients which tend to shrink the insulation panels.
The applicant company has observed that in tanks of the above type, it is necessary to take into account the minimum gap distance between adjacent insulating panels, and in particular between the lateral edges of the panels perpendicular to the direction of welding of the brackets. Reducing the distance between the lateral edges of two adjacent insulation panels results in an increase in the angular deformation of the welding brackets and the membrane fixed to the insulation panels, which increases the fatigue stress of the membrane, due to the tendency to produce a levelling effect between adjacent insulation panels. Thus, the film is susceptible to degradation unless a minimum gap distance is considered.
In particular, the fatigue properties of the sealing membrane of a tank of the type described above have been tested when the dimension at the gap formed between the adjacent lateral edges of the two insulating panels is less than a minimum value.
Each fatigue test included approximately 2000 cycles. In each cycle, a height difference of about a few millimetres is produced between the adjacent lateral edges of the two insulating panels in the thickness direction of the wall of the tank. Such tests represent the life of the ship.
In these tests, it is worth noting that in the gap region between adjacent lateral edges of the insulating panel:
the flat median portion of the web of the sealing film is liable to bend and possibly break, thus resulting in a lack of sealing;
the areas where the folded over edges of the slats and the flap edges meet the planar middle portion of the slats are prone to deformation, produce corrugations and may break, resulting in a lack of sealing.
However, making the minimum gap distance between the lateral edges of the insulation panels uniform can compromise the thermal performance of the insulation barrier.
Furthermore, the larger the value of the gap, the longer the distance over which the sealing membrane is not supported by the insulating plate, and the more easily the sealing membrane deforms under the pressure of the liquid stored in the tank.
Disclosure of Invention
One idea of the invention is to allow the width of the gap between adjacent primary and/or secondary heat shields in the longitudinal direction of the weld carrier to be reduced without significantly impairing the fatigue properties of the membrane.
One idea of the present invention is to propose a sealed and thermally insulated tank for storing liquefied gas, comprising, in order from the outside to the inside of the tank in the direction of the thickness of the wall: a heat insulating barrier and a sealing film abutting against the heat insulating barrier;
-the heat insulating barrier comprises at least two heat insulating panels, each having an upper panel defining a support surface against which the sealing film rests, the upper panels of the heat insulating panels each having a groove in which a welding carriage is mounted, the grooves of the two heat insulating panels being aligned and extending in a longitudinal direction; the welding bracket extends in a longitudinal direction and comprises a welding flange and an anchoring flange inclined relative to the welding flange; each recess opening onto the support surface and having a return portion in which the anchoring flange of the welding carriage is accommodated, the return portion forming a retaining portion in the respective heat shield between the return portion and the support surface against which the anchoring flange abuts in order to retain the welding carriage on said heat shield;
-the sealing membrane comprises, on either side of the welding support, at least two metal strips extending parallel to the longitudinal direction, the strips having a middle portion abutting against the support surface and two folded-over edges extending parallel to the longitudinal direction and projecting from the middle portion towards the interior of the tank, one of the folded-over edges of each of the two strips being welded to the welding flange of the welding support;
at least one groove of one of the two heat shields has an end facing the other heat shield, which end extends through a recess which opens into the supporting surface and is formed in the longitudinal direction at least in the continuation of the holder and the groove, so that the welding bracket is not fixed in the heat shield in the region of the recess.
Therefore, the welding brackets are not held on the heat insulating barrier at the notches, and the welding brackets and the sealing film exhibit greater flexibility according to the gap formed between the heat insulating boards, so that it is possible to limit the stress applied to the welding brackets and the sealing film when a height variation is formed between the adjacent main heat insulating boards.
According to other advantageous embodiments, such a tank may exhibit one or more of the following characteristics.
According to one embodiment, both insulation panels have two transverse edges perpendicular to the longitudinal direction, adjacent transverse edges of both insulation panels being spaced apart from each other by a gap having a width in the longitudinal direction of less than 20mm, preferably less than 10 mm.
According to one embodiment, the grooves of the heat-insulating panel are spaced apart by a spacing i, the longitudinal dimension of which is between 20mm and 70mm, advantageously between 25mm and 45mm, more particularly between 30mm and 40 mm. In other words, the size of the welding brackets not held on the heat shield in the region of the gap between the lateral edges of the heat shield is between 20mm and 70mm, advantageously between 25mm and 45mm, and more particularly between 30mm and 40 mm. This makes it possible, on the one hand, to limit the stresses which can be easily applied to the soldering mount and the sealing film to an acceptable range and, on the other hand, to hold the sealing film sufficiently firmly on the insulating plate without being pulled apart.
According to one embodiment, the groove of each of the two heat insulation panels has an end facing the other heat insulation panel, which end extends through a recess, which recess opens into the support surface, each recess being formed in the longitudinal direction at least in the continuation of the groove and the holder, so that the welding bracket is not held at the recess. Thus, the added flexibility of the weld support and the sealing membrane is distributed at the gap.
According to one embodiment, the or each notch has a dimension n in the longitudinal direction of between 5mm and 30 mm.
According to one embodiment, the depth p of the or each recess is equal to and preferably greater than the depth of the groove. Thereby, when the lateral edge of the heat insulating board having the notch is raised with respect to the adjacent lateral edge of another heat insulating board, it is possible to limit the stress applied to the soldering bracket and the sealing film.
According to one embodiment, the recess has a bottom and a side wall connecting the bottom to the support surface.
According to one embodiment, the bottom of the recess has a slope that is inclined such that the depth p of the recess decreases in the direction of the groove.
According to one embodiment, the side walls of the recess intersect the groove by a chamfer or fillet. Such a chamfer or fillet allows guiding the weld holder towards the groove, thereby facilitating the fitting of the weld holder in the groove.
According to one embodiment, the side wall of the recess is constituted by a planar portion and intersects the groove by a cylindrical portion.
According to one embodiment, the recess has the overall shape of a triangle or trapezoid narrowing in the direction of the groove.
According to one embodiment, at least the upper plate of one of the two heat insulating plates comprises a recess along a lateral edge of said heat insulating plate facing the other heat insulating plate, which recess extends in a direction perpendicular to the longitudinal direction from one end to the other end of the upper wall of said heat insulating plate, so that the sheet metal strip is not supported by the support surface along said lateral edge of the heat insulating plate. Thus, when the width of the gap between the heat insulating panels is small, the deformation of the slats during the cutting process can be prevented or limited according to the gap between the lateral edges of the main heat insulating panels.
According to one embodiment, both insulation panels have two lateral edges perpendicular to the longitudinal direction, the upper plate of each of the two insulation panels comprises a recess along the lateral edge of the insulation panel facing the other insulation panel, the recess extending from one end of the insulation panel to the other end perpendicular to the longitudinal direction, such that the slats are not supported by the support surface along the lateral edges of the insulation panels.
According to one embodiment, the recess is arranged in such a way that the upper plate is recessed at least in a defined area above a plane inclined at an angle of 55 ° with respect to the supporting surface and intersecting a lateral edge of the heat insulating plate, wherein the lateral edge of the heat insulating plate is 6mm from the supporting surface in the thickness direction of the wall.
According to one embodiment, the or each recess is formed by a cut, chamfer or radius formed in the upper plate along a lateral edge of the insulating plate.
According to one embodiment, the or each recess opens into one of these recesses.
According to another embodiment, the or each cut-out extends all the way to the lateral edge of the respective insulating panel.
According to one embodiment, the adjacent lateral edges of two insulating panels are spaced apart from each other by a gap having a width in the longitudinal direction of less than 5mm, for example about 1 mm.
According to an advantageous embodiment, the sum of the longitudinal dimension of the recess of each of the two heat insulation panels and the width of the gap formed between said heat insulation panels is between 7mm and 25 mm.
According to one embodiment, the groove has an inverted T-shaped cross-sectional shape.
According to one embodiment, the welding stent is L-shaped.
According to one embodiment, the upper plate is made of plywood.
According to one embodiment, the thickness of the upper plate is between 9mm and 15 mm.
According to one embodiment, the thermal insulation barrier is a primary thermal insulation barrier and the sealing membrane is a primary sealing membrane, the wall comprising, in order from the outside to the inside of the tank, a secondary thermal insulation barrier anchored to the carrying structure, a secondary sealing membrane resting on the secondary thermal insulation barrier, the primary thermal insulation barrier and the primary sealing membrane.
According to one embodiment, the sealing membrane is made of a material selected from the group consisting of stainless steel, an alloy of iron and nickel, and having a coefficient of expansion of 1.2 × 10-6And 2 × 10-6K-1And alloys of iron and manganese with an expansion coefficient of 15 × 10-6K-1The following is a description.
According to one embodiment, the welding stent is made of a material selected from the group consisting of stainless steel, an alloy of iron and nickel, and has a coefficient of expansion of 1.2 × 10-6And 2 × 10-6K-1And alloys of iron and manganese having an expansion coefficient of less than 15 × 10- 6K-1。
According to one embodiment, at least one of the insulating panels comprises a bottom panel, an intermediate panel positioned between the bottom panel and the top panel, a first insulating polymer foam layer sandwiched between the bottom panel and the intermediate panel, and a second insulating polymer foam layer sandwiched between the intermediate panel and the top panel. Such a structure has an advantage in that bending load generated by different shrinkage of the material of the heat insulating board can be restricted.
According to another embodiment, at least one of the insulation panels further comprises a bottom plate and a load-bearing flange extending between the bottom plate and the top plate in the thickness direction of the wall of the tank and delimiting a plurality of cells filled with an insulation material, such as perlite.
According to one embodiment, the heat insulation barrier comprises a plurality of heat insulation panels, each heat insulation panel having a top panel which defines a support surface against which a sealing film rests, each top panel having one or more grooves in which a welding bracket is mounted, each end of each groove having a notch which is open to the support surface and which is formed in the longitudinal direction at least in the continuation of the groove and the holder, so that the welding bracket is not held on the panel in the region of the notch.
Such tanks may form part of a land based storage facility, for example for storing liquefied natural gas, or may be installed in a floating, offshore or offshore structure, in particular a methane tanker, a Floating Storage and Regasification Unit (FSRU), a floating production storage and offloading unit (FPSO) or the like.
According to one embodiment, a vessel for transporting cryogenic fluids comprises a double hull and the aforementioned tank disposed within the double hull.
According to one embodiment, the double housing comprises an inner housing forming a load bearing structure for the tank.
According to one embodiment, the invention also provides a method for loading or unloading such a vessel, in which method a fluid is transferred from an offshore or onshore storage facility to the tanks of the vessel or from the tanks of the vessel to the offshore or onshore storage facility through insulated conduits.
According to one embodiment, the invention also provides a fluid transfer system comprising a vessel as described above, an insulated pipeline arranged to connect a tank mounted in the hull to an offshore or onshore storage facility, and a pump for flowing fluid between the offshore or onshore storage facility and the vessel's tank through the insulated pipeline.
Drawings
The invention will be better understood and other objects, details, characteristics and advantages thereof will become more clearly apparent in the course of the description of several particular embodiments thereof, given by way of non-limiting example only, with reference to the accompanying drawings, in which
Figure 1 is a cut-away perspective view of a tank wall.
Fig. 2 is a cross-sectional view showing a recess formed in the main plate, a welding bracket received in the recess and a strip welded to the welding bracket.
Fig. 3 is a perspective view of the main plate according to the first embodiment.
Figure 4 is a detailed perspective view showing the primary thermal insulation barrier at the junction between two adjacent primary insulation panels according to the first embodiment.
Figure 5 is a detailed view of the notch at the lateral edge of the primary insulation panel according to the first embodiment.
Figure 6 is a schematic cross-sectional view of a groove and a notch.
Figure 7 is a perspective view of a primary heat shield according to a second embodiment.
Figure 8 is a schematic cross-sectional view showing a primary thermal insulation barrier at a junction between two adjacent primary insulation panels according to a second embodiment.
Figure 9 is a schematic cross-sectional view showing a primary thermal insulation barrier at the junction between two adjacent primary insulation panels according to a variant of the second embodiment.
Figure 10 is a schematic cross-sectional view showing a primary thermal insulation barrier at the junction between two adjacent primary insulation panels according to another variant of the second embodiment.
Figure 11 is a perspective view of a primary heat shield according to a third embodiment.
Figure 12 is a schematic cross-sectional view showing a primary thermal insulation barrier at a junction between two adjacent primary insulation panels according to a third embodiment.
Fig. 13 is a sectional view of a tank of a methane oil ship and a terminal for loading/unloading from the tank.
Detailed Description
By convention, in the description, the elements of the
Fig. 1 shows a multilayer structure of a
The carrying structure 3 may in particular be formed by a hull or double hull of a ship. The load bearing structure 3 comprises a plurality of walls defining the overall shape of the walls, wherein the shape is generally polyhedral in shape.
The secondary
In the embodiment shown in fig. 1, each secondary heat-insulating
In another embodiment, the secondary
In another embodiment, the secondary
For example, the secondary
The
The
The structure of the
The
The structure of the
Returning to fig. 1, it can be seen that the
Anchoring of the
In the embodiment shown, the
The
The
The
The
The
As shown in fig. 4, the
Furthermore, in order to limit the mechanical stresses which tend to act on the
The
The
Furthermore, advantageously, the dimension m of the
More specifically, in the embodiment shown, the side wall has a planar portion and meets the
In other embodiments, not shown, the overall shape of the
The dimension n of the
Further, for example, the dimension n of the
Referring now to fig. 7 and 8, a
In order to avoid that the shearing deformation of the
Thus, when a height difference is generated between the adjacent
Advantageously, the length l, i.e. the sum of the longitudinal dimension of the
The
It should be noted that in this embodiment, as those described below in connection with fig. 9 and 10,
Fig. 9 and 10 show an embodiment variant of the second embodiment of fig. 7 and 8. These embodiment variants differ from the variant shown in fig. 8 in the shape of the
In the embodiment variant shown in fig. 9, the
In the embodiment variant shown in fig. 10, each
For both embodiment variants, the length l, i.e. the sum of the longitudinal dimension of the
Advantageously, whatever the shape of the
Fig. 11 and 12 depict a third embodiment. This embodiment differs from the embodiment described above in connection with fig. 7 to 10 in that the
Also, for example, in the embodiment shown in FIG. 12, the width of the
It should be noted that, in the above-described embodiment, only the primary
However, alternatively or additionally, the secondary
Referring to fig. 13, a cross-sectional view of a methane tanker 70 shows a sealed insulated tank 71 in the shape of a prismatic monolith mounted in a double hull 72 of a ship. The walls of the tank 71 comprise a primary hermetic barrier for contact with the GNLs contained in the tank, a secondary hermetic barrier arranged between the primary hermetic barrier and the double hull 72 of the ship, and two thermal insulation barriers arranged between the primary hermetic barrier and the secondary hermetic barrier and between the secondary hermetic barrier and the double hull 72, respectively.
In a manner known per se, a loading/unloading pipe system 73 arranged on the upper deck of the ship may be connected to the offshore or harbour terminal by means of suitable connectors for transporting LPG cargo to and from the tanks 71.
Figure 13 shows an example of an offshore terminal comprising a loading and unloading station 75, a subsea pipeline 76 and an onshore facility 77. The loading and unloading station 75 is a fixed offshore facility that includes a mobile arm 74 and a tower 78, the tower 78 supporting the mobile arm 74. The mobile arm 74 supports a bundle of insulated flexible tubes 79, the insulated flexible tubes 79 being connectable to the loading/unloading duct 73. The directable moving arm 74 can accommodate all sizes of methane tankers. Not shown, extending within tower 78. The loading and unloading station 75 allows the ship to be unloaded to or loaded from an onshore facility 77, the onshore facility 77 including a liquefied gas storage tank 80 and a connecting pipeline 81, the connecting pipeline 81 being connected to the loading or unloading station 75 by the underwater pipeline 76. The underwater pipeline 76 allows the liquefied gas to be transported over long distances, for example 5km, between the loading or unloading station 75 and the onshore facility 77, so that the vessel 70 remains far off shore during loading and unloading operations.
To generate the pressure required for the transportation of the liquefied gas, pumps onboard the ship 70 and/or pumps provided with onshore facilities 77 and/or pumps provided with loading and unloading stations 75 are used.
Although the invention has been described in connection with a number of specific embodiments, it is evident that the invention is not limited thereto in any way and that it comprises all technical equivalents of the described means and combinations thereof, provided that they fall within the scope of the invention.
Use of the verb "comprise", "have" or "comprise" and its conjugations does not exclude the presence of elements or steps other than those stated in a claim.
In the claims, any reference signs placed between parentheses shall not be construed as limiting the claim.
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