NL2031473B1 - Fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids - Google Patents
Fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids Download PDFInfo
- Publication number
- NL2031473B1 NL2031473B1 NL2031473A NL2031473A NL2031473B1 NL 2031473 B1 NL2031473 B1 NL 2031473B1 NL 2031473 A NL2031473 A NL 2031473A NL 2031473 A NL2031473 A NL 2031473A NL 2031473 B1 NL2031473 B1 NL 2031473B1
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- Netherlands
- Prior art keywords
- fluid
- annular
- flange
- inner body
- fluid conduit
- Prior art date
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 275
- 230000008878 coupling Effects 0.000 title claims abstract description 86
- 238000010168 coupling process Methods 0.000 title claims abstract description 86
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 86
- 239000000463 material Substances 0.000 claims abstract description 18
- 239000001257 hydrogen Substances 0.000 claims description 68
- 229910052739 hydrogen Inorganic materials 0.000 claims description 68
- 238000001514 detection method Methods 0.000 claims description 20
- 238000007789 sealing Methods 0.000 claims description 13
- 238000002955 isolation Methods 0.000 claims description 11
- 239000007788 liquid Substances 0.000 claims description 10
- 238000000034 method Methods 0.000 claims description 8
- 241001416181 Axis axis Species 0.000 claims 1
- 125000004435 hydrogen atom Chemical class [H]* 0.000 claims 1
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 56
- 230000014759 maintenance of location Effects 0.000 description 14
- 150000002431 hydrogen Chemical class 0.000 description 11
- 230000000903 blocking effect Effects 0.000 description 6
- 239000012212 insulator Substances 0.000 description 6
- 238000010926 purge Methods 0.000 description 5
- 125000004429 atom Chemical group 0.000 description 4
- 230000007704 transition Effects 0.000 description 4
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 3
- 229910052799 carbon Inorganic materials 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- 239000001301 oxygen Substances 0.000 description 3
- 229910052760 oxygen Inorganic materials 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- MYMOFIZGZYHOMD-UHFFFAOYSA-N Dioxygen Chemical compound O=O MYMOFIZGZYHOMD-UHFFFAOYSA-N 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 239000003077 lignite Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000032258 transport Effects 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 239000008186 active pharmaceutical agent Substances 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005262 decarbonization Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 229910002804 graphite Inorganic materials 0.000 description 1
- 239000010439 graphite Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 229910000601 superalloy Inorganic materials 0.000 description 1
- 229920000785 ultra high molecular weight polyethylene Polymers 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L27/00—Adjustable joints; Joints allowing movement
- F16L27/08—Adjustable joints; Joints allowing movement allowing adjustment or movement only about the axis of one pipe
- F16L27/0804—Adjustable joints; Joints allowing movement allowing adjustment or movement only about the axis of one pipe the fluid passing axially from one joint element to another
- F16L27/0808—Adjustable joints; Joints allowing movement allowing adjustment or movement only about the axis of one pipe the fluid passing axially from one joint element to another the joint elements extending coaxially for some distance from their point of separation
- F16L27/0824—Adjustable joints; Joints allowing movement allowing adjustment or movement only about the axis of one pipe the fluid passing axially from one joint element to another the joint elements extending coaxially for some distance from their point of separation with ball or roller bearings
- F16L27/0828—Adjustable joints; Joints allowing movement allowing adjustment or movement only about the axis of one pipe the fluid passing axially from one joint element to another the joint elements extending coaxially for some distance from their point of separation with ball or roller bearings having radial bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L39/00—Joints or fittings for double-walled or multi-channel pipes or pipe assemblies
- F16L39/04—Joints or fittings for double-walled or multi-channel pipes or pipe assemblies allowing adjustment or movement
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Quick-Acting Or Multi-Walled Pipe Joints (AREA)
- Joints Allowing Movement (AREA)
Abstract
The invention relates to a fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids, comprising: an annular outer body and an annular inner body, which are rotatable with respect to each other 5 around a rotation axis; a bearing ring provided between the annular outer body and the annular inner body; and a first flange connected to the annular inner body and configured for being connected to a first fluid conduit, and a second flange connected to the annular outer body and configured 10 for being connected to a second fluid conduit, wherein the first flange is provided with a first fluid conduit section extending into the annular inner body parallel to the rotation axis and towards the second flange, and the second flange is provided with a second fluid conduit section 15 extending into the annular inner body parallel to the rotation. axis and. towards the first flange, wherein the first fluid conduit section and the second fluid conduit section define a fluid channel extending through the annular inner body, and wherein an annular seal is provided 20 around the facing ends of the first fluid conduit section and the second fluid conduit section, and wherein the annular seal is manufactured. of a material that has a shrinkage rate that is higher than the shrinkage rate of the material of at least the first and second fluid conduit 25 sections.
Description
P140800NLOO
FLUID LOADING COUPLING FOR ROTATABLE COUPLING OF FLUID
CONDUITS FOR CRYOGENIC FLUIDS
The invention relates to a fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids.
As known, an energy transition is currently going on, wherein the energy transition is considered a process of the global energy sector to shift from fossil-based energy production and consumption to zero-carbon energy production and consumption. In order to limit climate change, the main aspect of the energy transition is reducing CO: emissions related to energy generation, also known as decarbonization of the energy sector. Energy transition, thus, refers to the shift of the global energy section to renewable energy sources like wind and solar, as well as hydrogen (Hs).
It is known in the energy sector that a pilot project is going on in which hydrogen is used. The pilot project involves starting up a complete supply chain for hydrogen. The supply chain includes inter alia a process of generating hydrogen from brown coal, also known as lignite, while carbon dioxide generated during the process is hopefully captured and stored. The generated hydrogen is transported in gaseous form to a harbor by means of trucks.
At the harbor, the hydrogen is liquified and stored in a shore storage tank, from which the ligquified hydrogen is loaded into a transporting vessel by means of so-called loading arms, in particular marine loading arms. The transporting vessel transports the liquified hydrogen to another country, where the transporting vessel is discharged via so-called loading arms. Thereafter, the liguified hydrogen may be used for generating energy.
Each of the loading arms is provided with at least one fluid loading conduit to be coupled to a fluid loading conduit of the transporting vessel. A fluid loading coupling is used to achieve coupling of the at least one fluid loading conduit of the loading arms to a fluid loading conduit of the transporting vessel.
Such a fluid loading coupling, also known as a fluid loading joint, for example, is known from US patent application US 2021/0071795. US 2021/0061640 describes a fluid loading joint including: a first half provided at an end of a first vacuum double pipe, the first half including a first inner pipe, a first outer pipe, and a first blocking member blocking between the first inner pipe and the first outer pipe; a second half provided at an end of a second vacuum double pipe, the second half including a second inner pipe, a second outer pipe, and a second blocking member blocking between the second inner pipe and the second outer pipes; an annular inner insulator interposed between the first inner pipe and the second inner pipe; and an annular outer insulator interposed between the first outer pipe and the second outer pipe, the outer insulator surrounding the inner insulator, with a gas space positioned between the outer insulator and the inner insulator, the gas space being formed between the first blocking member and the second blocking member.
As mentioned above, the fluid loading coupling may be used by loading liquified hydrogen from a shore storage tank to a transporting vessel, or vice versa. In order to be liquified, hydrogen needs to be cooled below its critical point of -240 °C (33 K) to exist as a liquid.
The critical point is considered to be the liquid-vapor critical point, which corresponds to the end point of a pressure-temperature curve designating conditions under which a liquid form and gaseous form of hydrogen may coexist. If for example the temperature rises above the critical point of -240 °C, while the pressure remains constant, hydrogen will only exist in gaseous form. In order to be fully liquid at atmospheric pressure, hydrogen needs to be cooled to 252.87 °C (20.28 K), which is close to the absolute zero.
While loading liguified hydrogen by means of the fluid loading coupling, at least a part of the fluid loading coupling is in contact with the liquified hydrogen and, therefore, is cooled to a temperature corresponding to or very close to the temperature of the liquified hydrogen.
The very low temperature of -252.87 °C causes the atoms of the material of the fluid loading coupling to come almost to a standstill, as the kinetic energy and thus movement of the atoms is dramatically decreased. As the movement of the atoms is dramatically decreased, the atoms need less space in comparison to a situation in which the material has a higher temperature. As a result, the material of the cooled part of the fluid loading coupling shrinks. Additionally, the material stiffness of material increases when the temperature decreases.
The fluid loading coupling of US 2021/0061640 applies annular sealing members to preventing leakage of liquified hydrogen through a gap between the first half and the second half. The applied sealing members are substantially U-shaped in cross-section, wherein the open top of the U-shape is directed towards the rotation axis of the fluid loading coupling such that liquified hydrogen may enter the sealing members. Due the very low temperature of the liquified hydrogen, the sealing members will acquire substantially the temperature of the ligquified hydrogen.
Due to the very low temperature of the sealing members, the sealing members will shrink, while the stiffness thereof increases, as a result of which the sealing members are not capable of sealing the gap between the first half and the second half of the fluid loading coupling. An disadvantage of the known fluid loading coupling, thereof, is that leakage of hydrogen may occur during use.
It is an object of the present invention to ameliorate or to eliminate one or more disadvantages of the known fluid loading coupling, to provide an improved fluid loading coupling or to at least provide an alternative fluid loading coupling.
According to a first aspect, the invention provides a fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids, comprising: an annular outer body and an annular inner body, which are rotatable with respect to each other around a rotation axis, a bearing ring provided between the annular outer body and the annular inner body, and a first flange connected to the annular inner body and configured for being connected to a first fluid conduit, and a second flange connected to the annular outer body and configured for being connected to a second fluid conduit, wherein the first flange is provided with a first fluid conduit section extending into the annular inner body parallel to the rotation axis and towards the second flange, and the second flange is provided with a second fluid conduit section extending into the annular inner body parallel to the rotation axis and towards the first flange, wherein the first fluid conduit section and the second fluid conduit section define a fluid channel extending through the annular inner body, and wherein an annular seal is provided around the facing ends of the first fluid conduit section and the second fluid conduit section, and wherein the annular seal is manufactured of a material that has a shrinkage rate that is higher than the shrinkage rate of the material of at least the first and second fluid conduit sections.
During use of the fluid loading coupling 5 according to the invention, the fluid loading coupling may be arranged at a loading arm located within a harbor for transporting liquified hydrogen from a source of liquified hydrogen to a transporting vessel, i.e. to load liquified hydrogen into the transporting vessel. The fluid loading coupling, at least the outer surface thereof, is exposed to the environment, such that the outer surface has the same or approximately the same temperature as the environment. Liquified hydrogen has a temperature of, approximately, -252.87 °C, such that ligquified hydrogen flowing through the fluid channel defined by the first and second fluid conduit sections, cools at least the inside of the fluid loading coupling, in particular the first and second fluid conduit sections. Due to thermal conductivity within the fluid loading coupling, further components of the fluid loading coupling will be cooled too. One of the further components is the annular seal arranged around the facing ends of the first and second fluid conduit sections. Because of the cooling, the material of the annular seal and the first and second fluid conduit sections will shrink. As the material of the annular seal has a higher shrinkage rate than the material of at least the first and second fluid conduit sections, the annular seal will shrink more than the first and second fluid conduit sections. This is advantageous, as the annular seal tightens around the facing ends of the first and second fluid conduit sections, thereby sealing the fluid channel through the fluid loading coupling in a reliable manner.
The annular seal being arranged around the facing ends of the first and second fluid conduit sections, in the context of the present patent application, has to be understood as the annular seal being arranged at the outer circumference of the first and fluid conduit sections and circumventing the facing ends of the first and second fluid conduits sections in the circumferential direction thereof.
In the context of the present patent application, shrinkage rate of material may be understood as the volume contraction of the respective material during the cooling thereof.
In an embodiment, a gap is provided between the facing ends of the first and second conduit sections. The gap allows liguified hydrogen, at the start of loading liquified hydrogen, to flow towards the annular seal and to contact the annular seal, such that the annular seal is cooled off rapidly by the liquified hydrogen. As a result, a small leakage of liquified hydrogen towards the annular seal is allowed for a limited amount of time. This advantageously results in the annular seal sealing the fluid channel in a reliable manner shortly after the start of loading liquified hydrogen.
In an embodiment, the annular inner body has an inner circumference facing towards the rotation axis, and the first and second fluid conduit sections each have an outer circumference facing away from the rotation axis and towards the inner circumference of the annular inner body.
In an embodiment thereof, a chamber is provided between the inner circumference of the annular inner body and the outer circumference of the first and second fluid conduits.
Preferably, a gap is present between the facing ends of the first and second conduit sections. At the start of loading liquified hydrogen by means of the fluid loading coupling, a small leakage of liquified hydrogen through the gap is allowed, which leaked liduified hydrogen flows into the chamber. Within the chamber, the leaked liquified hydrogen warms up and, therefore, evaporates at least partially or even completely. Due to the leaked liquified hydrogen evaporating within the chamber, the pressure within the chamber increases. The increased pressure applies a force
: on the annular seal, thereby advantageously forcing the annular seal against the outer circumference of the first and second fluid conduit sections, such that the annular seal seals the fluid channel in a reliable manner.
In an embodiment, the first fluid conduit section comprises a first retention part near or at a distance from the end facing towards the second flange, and the second fluid conduit section comprises a second retention part near or at a distance from the end facing towards the first flange, wherein the first and second retention parts together define a retention space for retaining the annular seal in position. Preferably, each of the first and second retention parts is substantially elbow-shaped or is a raised edge extending radially outwards. According to this embodiment, the annular seal is retained within the retention space by the first and second retention parts.
This is advantageous, as the annular seal is therewith prevented from moving away from one or both of the facing ends.
In an embodiment, the annular inner body comprises a first inner body portion having a first inner body portion having a first outer diameter and an first inner diameter, and a second inner body portion extending from a side of the first inner body portion substantially parallel to the rotation axis and having a second outer diameter that is smaller than the first outer diameter, and the first inner diameter, wherein the second inner body portion is located within the annular outer body. In an embodiment thereof, the first flange 1s arranged at the first inner body portion at the side facing away from the second inner body portion, and the second inner body portion extends to the second flange. Preferably, the annular outer body comprises a first outer body portion located adjacent to the first inner body portion and having a third outer diameter, which is larger than the second outer diameter and smaller than the first outer diameter, and a second inner diameter that is slightly larger than the second outer diameter, wherein, at the side facing away from the first inner body portion, the first outer body portion passes into a second outer body portion that has an outer diameter corresponding to the first outer diameter, and an inner diameter corresponding to the second inner diameter. In an even further embodiment, the first inner body portion has a first seal recess at the side facing the first flange, which first seal recess extends radially outwards from the inner circumference of the first inner body portion, wherein the second inner body portion comprises a second seal recess at the side facing the second flange, which second seal recess extends radially outwards from the inner circumference of the second inner body portion, and wherein a first seal is arranged within the first seal recess and a second seal is arranged within the second seal recess. As described above, a small leakage of liquified hydrogen between the facing ends of the first and second fluid conduit sections is allowed. The leaked liquified hydrogen, in this case, enters the space between the outer circumference of the first and second fluid conduit sections and the inner circumference of the annular inner body, also known as a chamber. By providing the first seal between the first inner body portion and the first flange, and the second seal between the second inner body portion and the second flange, any possible gap that is present there, is sealed. As a result, the leaked hydrogen within the space between the outer circumference of the first and second fluid conduit sections and the inner circumference of the annular inner body is advantageously prevented from leaking into the environment.
In an embodiment, the second inner body portion has a third seal recess at the side facing the second flange, which third seal recess extends radially inwards from the outer circumference of the second inner body portion, wherein a third seal is arranged within the third seal recess, and/or an additional seal is provided within the first flange at the side thereof facing towards the annular inner body in order to provide an additional seal between the first flange and the annular inner body, and/or within the second flange at the side thereof facing towards the annular outer body in order to provide an additional seal between the second flange and the annular outer body.
In an embodiment thereof, the second flange comprises a leakage detection channel extending therethrough, wherein the leakage detection channel debouches, at one end thereof, into a space present between the second and third seal recesses, and, at the opposite end, into the environment, at which end the leakage detection channel preferably is closed off by a leakage detection seal, preferably wherein the leakage detection seal is configured for allowing a leakage detection device to be connected to the leakage detection channel. This embodiment advantageously allows a user to connect a leakage detection device to the fluid loading coupling in order to detect whether any hydrogen leaks beyond the first or second seal.
In an embodiment, the first fluid conduit section comprises an annular first outer fluid wall, and an annular first inner fluid wall located within and at a distance from the annular first outer fluid wall, thereby defining a first isolation space within the first fluid conduit section, and wherein the second fluid conduit section comprises an annular second outer fluid wall, and an annular second inner fluid wall located within and at a distance from the annular second outer fluid wall, thereby defining a second isolation space within the second fluid conduit section, such that each of the first and second fluid conduit sections is a double-walled fluid conduit section. In an embodiment, the annular first outer fluid wall and the annular first inner fluid wall are connected to each other at the end facing towards the second flange, and wherein the annular second outer fluid wall and the annular second inner fluid wall are connected to each other at the end facing towards the first flange. As mentioned above, hydrogen is fully liquid by a temperature of -252.87
°C. Transporting liquid hydrogen through the fluid conduit sections may result in the outer circumference of the fluid conduit sections being cooled to the same temperature of -252.87 °C. As the outer circumference of the fluid conduit sections 1s in contact with the surrounding air, and thus with the surrounding oxygen within the air, the oxygen within the surrounding air may become liquid since oxygen is liquid by a temperature below -182.96 °C. As a result, liquid oxygen may be present at the outer circumference of the fluid conduit sections, which may result in dangerous situations due to the nature of liquid oxygen. By providing double-walled fluid conduit sections, the inside of the fluid conduit sections may be isolated, for example vacuum isolated, from the environment. This is advantageous, as it may prevent dangerous situations due to liguifying gasses at the outer circumference of the fluid conduit sections from occurring.
According to a second aspect, the invention provides a loading arm, such as a marine loading arm, for loading cryogenic fluids, wherein the loading arm comprises: a fluid loading coupling according to the first aspect of the invention.
The loading arm has at least the same advantages as described in relation to the fluid loading coupling according to the first aspect of the invention.
It is noted that a loading arm according to the second aspect of the invention, for example, may comprise up to 6 fluid loading couplings according to the first aspect of the invention, thereby granting a high degree of freedom of movement to the loading arm.
According to a third aspect, the invention provides a method for loading a cryogenic fluid, such as liquified hydrogen, by means of a fluid loading coupling according to the first aspect of the invention, or by means of the loading arm according to the second aspect of the invention, wherein the method comprises the steps of:
- at one side, connecting the fluid loading coupling to a fluid conduit of a source of cryogenic fluid, - at another side, connecting the fluid loading coupling to a fluid conduit of a destination for the cryogenic fluid, - starting loading cryogenic fluid from the source of cryogenic fluid inte the destination for the cryogenic fluid via the fluid loading coupling, and - within the fluid loading coupling, allowing an amount of cryogenic fluid to flow towards the annular seal of the fluid loading coupling.
The method has at least the same advantages as described in relation to the fluid loading coupling according to the first aspect of the invention.
The various aspects and features described and shown in the specification can be applied, individually, wherever possible. These individual aspects, in particular the aspects and {features described in the attached dependent claims, can be made subject of divisional patent applications.
The invention will be elucidated on the basis of an exemplary embodiment shown in the attached drawings, in which:
Figure 1 shows an isometric view of a fluid loading coupling according to a first embodiment of the invention; and
Figure 2 shows a cross-sectional view of the fluid loading coupling of figure 1.
An isometric view of a fluid loading coupling 1, also known as a swivel joint or a fluid loading joint, according to an embodiment of the invention is shown in figure 1, and a cross-sectional view of the same fluid loading coupling 1 is shown in figure 2. The shown fluid loading coupling 1 may be provided at or incorporated within a loading arm, for example, located at a harbor, and, for example, may be used for establishing a fluid connection between on the one hand a transporting vessel for transporting liquified hydrogen, and on the other hand a truck for transporting liquified hydrogen, a liquefier for liquifying gaseous hydrogen or a shore storage tank for storing liquified hydrogen. Such a fluid loading coupling 1 may be used because of the high bending and axial load combination, during use, due to the reach of the loading arm and wind forces, and is intended for withstanding these loads.
The shown fluid loading coupling 1 is provided with an annular inner body 2 and an annular outer body 3, which are arranged rotatable with respect to each other around a rotation axis C. As best shown in figure 2, the annular inner body 2 has a first inner body portion 10 having a first outer diameter D1 and an first inner diameter D2, and a second inner body portion 11 extending from a side of the first inner body portion 10 substantially parallel to the rotation axis C and having a second outer diameter D3 smaller than the first outer diameter Dl and also having the first inner diameter D2.
The second inner body portion 11 is located within the annular outer body 3, while the first inner body portion 10 is located adjacent to the annular outer body 3.
The annular outer body 3 extends around the second inner body portion 11 and includes a first outer body portion 12 located adjacent to the first inner body portion 10 and having a third outer diameter D4, which is larger than the second outer diameter D3 and smaller than the first outer diameter Dl, and a second inner diameter DS that is slightly larger than the second outer diameter D3.
At the side facing away from the first inner body portion 10, the first outer body portion 12 passes into a second outer body portion 13 that has an outer diameter corresponding to the first outer diameter Dl, and an inner diameter corresponding to the second inner diameter D5.
As shown in figure 2, a first bearing ring 14 and a second bearing ring 15, each comprising a plurality of bearing balls 16 arranged within an annular bearing ball cage 17, are provided between the outer diameter of the second inner body portion 11 and the first outer body portion 12. The first and second bearing rings 15, 16 allow the annular inner body 2 and the annular outer body 3 to rotate with respect to each other.
As shown in figures 1 and 2, a first flange 5 is arranged at the annular inner body 2, in particular at the side of the first inner body portion 10 facing away from the second inner body portion 11, by means of bolts 18.
Additionally, a second flange 6 is arranged at the annular outer body 3, in particular at the side of the second outer body portion 13 facing away from the first outer body portion 12, by means of bolts 18. Each of the first flange 5 and second flange 6 is connected to a double-walled first elbow-shaped fluid conduit 7 and a double-walled second elbow-shaped fluid conduit 8, respectively, which first and second elbow-shaped fluid conduits 7, 8 are each connected to a double-walled further fluid conduit 9.
The first flange 5 has an annular first outer portion 20 with receiving holes for receiving the bolts 18, and an annular first inner portion 21 arranged at the side of the annular first outer portion 20 facing towards the rotation axis C. In cross-section, the annular first outer portion 20 is substantially rectangular-shaped, and the annular first inner portion 21 has a substantially frusto- conical shape and tapers in a direction radially outwards from the rotation axis C.
As best shown in figure 2, a first fluid conduit section 25 is arranged at the first flange 5, in particular at the side of the annular first inner portion 21 facing towards the rotation axis C. Preferably, the annular first inner portion 21 and the first fluid conduit section 25 merge into each other, without any gap arising therebetween. The first fluid conduit section 25 extends substantially parallel to the rotation axis C and in a direction away from the second flange 6, such that the first elbow-shaped circuit 7 may be connected to the fluid loading coupling 1 at the first flange 5. Additionally, the first {fluid conduit section 25 extends substantially parallel to the rotation axis C towards the second flange 6, preferably to about the middle of the annular inner body 2 when seen along the rotation axis C.
The first fluid conduit section 25 comprises an annular first outer fluid wall 26 having a fluid conduit outer diameter D6 that is smaller than the first inner diameter D2, and an annular first inner fluid wall 27 located within and at a distance from the annular first outer fluid wall 26 such that a first isolation space 28 is defined within the first fluid conduit section 25. The first fluid conduit section 25, thus, is a double-walled first fluid conduit section 25. The annular first outer fluid wall 26 and the annular first inner fluid wall 27 are connected to each other at the end 29 facing towards the second flange 6.
Likewise, the second flange 6 has an annular second outer portion 22 with receiving holes for receiving the bolts 18, and an annular second inner portion 23 arranged at the side of the annular second outer portion 22 facing towards the rotation axis C. In cross-section, the annular second outer portion 22 is substantially rectangular-shaped, and the annular second inner portion 22 has a substantially frusto-conical shape and tapers in a direction radially outwards from the rotation axis C.
As best shown in figure 2, a second fluid conduit section 30 is arranged at the second flange 6, in particular at the side of the annular second inner portion 23 facing towards the rotation axis C. Preferably, the annular second inner portion 23 and the second fluid conduit section 30 merge into each other, without any gap arising therebetween. The second fluid conduit section 30 extends substantially parallel to the rotation axis C and in a direction away from the first flange 5, such that the second elbow-shaped circuit 8 may be connected to the fluid loading coupling 1 at the second flange 6. Additionally, the second fluid conduit section 30 extends substantially parallel to the rotation axis C towards the first flange 5, preferably to about the middle of the annular inner body 2 when seen along the rotation axis C. The second fluid conduit section 30 defines together with the first fluid conduit section 25 a fluid channel through the fluid loading coupling 1.
The second fluid conduit section 30 comprises an annular second outer fluid wall 31 having also the first fluid conduit outer diameter D6 that is smaller than the first inner diameter D2, and an annular second inner fluid wall 32 located within and at a distance from the annular second outer fluid wall 31 such that a second isolation space 33 is defined within the second fluid conduit section 30. The second fluid conduit section 30, thus, is a double- walled second fluid conduit section 30. The annular second outer fluid wall 31 and the annular second inner fluid wall 32 are connected to each other at the end 33 facing towards the first flange 5.
A small gap 34 is present between the facing ends 29, 33 of the first and second fluid conduit sections 25, 30, in order to allow a small amount of liquified hydrogen to pass through the small gap 34.
The first and second fluid conduit sections 25, 30 are provided with the first and second isolation spaces 28, 33, respectively, such that a vacuum isolation may be arranged to isolate the liquid hydrogen from the environment and vice versa. By arranging the isolation spaces 28, 33 within the first and second fluid conduit sections 25, 30, the vacuum isolation extends into the fluid loading coupling 1 as far as possible. As a result,
the fluid channel through the fluid loading coupling 1 may be vacuum isolated almost completely. Additionally, since the first and second fluid conduit sections 25, 30 are arranged at the first and second flanges 5, 6, respectively, maintenance of the fluid loading coupling 1, in particular related to the annular inner body 2, the annular outer body 3, or components thereof, may be performed without breaking the vacuum isolation.
As best shown in {figure 2, a chamber 35 is present between the annular inner body 2 and the first and second fluid conduit sections 25, 30, wherein the chamber 35 is formed by the annular first inner portion 21 having a first inner diameter D2 that is larger than the fluid conduit outer diameter D6 of the annular first outer fluid wall 26 and the annular second outer fluid wall 30. The chamber 35 is in fluid communication with the fluid channel through the fluid loading coupling 1 via the small gap 34, such that liquified hydrogen passing through the small gap 34 is received within the chamber 35.
The first inner body portion 10 is provided with a first seal recess 36 at the side facing the first flange 5, which first seal recess 36 extends radially outwards from the inner circumference of the first inner body portion 10. A first seal 40 is received within the first seal recess 36. additionally, the second inner body portion 11 is provided with a second seal recess 37 at the side facing the second flange 6, which second seal recess 37 extends radially outwards from the inner circumference of the second inner body portion 11, and with a third seal recess 38 at the side facing the second flange 6, which third seal recess 38 extends radially inwards from the outer circumference of the second inner body portion 11. A second seal 41 and a third seal 42 are arranged within the second seal recess 37 and the third seal recess 38, respectively.
Furthermore, as shown in figure 2, a fourth seal 43 is provided between the first inner body portion 10 and the first outer body portion 12, in particular at the outer circumference of the first outer body portion 12.
For example, the first, second, third and/or fourth seals 40, 41, 42, 43 are an annular seal formed from a jacket of UHMW PE which is U-shaped in cross-section, a spring of an austenitic superalloy which is U-shaped in cross-section for exerting a force on the jacket in axial direction, and a spacer of a corrosion-resistant stainless steel (AISI) which is rectangular in cross-section for exerting a force on the jacket in radial direction.
Furthermore, an additional seal 44, such as a graphite seal, is provided within the first flange 5 at the side thereof facing towards the first inner body portion 10, in order to provide an additional seal between the first flange 5 and the first inner body portion 10, and/or within the second flange 6 at the side thereof facing towards the second outer body portion 13, in order to provide an additional seal between the second flange 6 and the second outer body portion 13.
As shown in figure 2, the second flange 6 is provided with a leakage detection channel 45 that extends through at least through the annular second outer portion 22 and debouches, at one end, into a space present between the second seal recess 37 and the third seal recess 38, and, at the opposite end, into the environment at which end the leakage detection channel 45 is closed off with a leakage detection seal 46. A non-shown leakage detection device may be connected to the leakage channel 45 via the leakage detection seal 46 in order to be able to detect whether or not any hydrogen is leaked from the chamber 35.
The annular outer body 3 is further provided with a purge channel 47 that extends through the second outer body portion 13 and, at one end, debouches into a space present between the annular inner body 2, in particular the second inner body portion 11 thereof, and the annular outer body 3, and, at the other end, debouches into the environment at which end the purge channel 47 is closed off by a purge seal 48. The purge channel 47 may be used for purging gas towards the first and second bearing rings 14, 15.
As shown in figure 2, a first annular retention part 50 is provided at the outer circumference of the first fluid conduit section 25 near the end 29 facing towards the second flange 6. A second annular retention part 51 is provided at the outer circumference of the second fluid section 30 near the end 33 facing towards the first flange 5. Each of the first and second annular retention part 50, 51 is shaped as a raised edge extending radially outwards from the respective fluid conduit section 25, 30, wherein the first and second annular retention parts 50, 51 together define a retention space 52.
Within the retention space 52, an annular seal 53 is provided that extends around the end 29 of the first fluid conduit section 25 facing towards the second flange 6, and around the end 33 of the second fluid conduit section 30 facing towards the first flange 5, thereby overlapping the gap 34 between the facing ends of the first and second fluid conduit sections 25, 30. The first and second annular retention parts 50, 51 limit or even prevent axial movement of the annular seal 53 in an axial direction parallel to the rotation axis C. The annular seal 53 is manufactured of a material that has a shrinkage rate that is higher than the shrinkage rate of the material of among others the first and second fluid conduit sections 25, 30 and, optionally, the remainder of the fluid loading coupling 1.
During use, the fluid loading coupling 1, for example, is fluidly connected to a source of liquified hydrogen and to a transporting vessel, such that liquified hydrogen, with a temperature of approximately -252.87 °C, may be transported from the source of liquified hydrogen to the transporting vessel. When transport of liquified hydrogen from the source of ligquified hydrogen to the transporting vessel is started, liquified hydrogen flows through a fluid conduit 9 towards the fluid loading coupling 1. Upon flowing through the fluid loading coupling 1, liquified hydrogen is allowed to flow through the gap 34 and to enter the chamber 35, thereby flowing along the annular seal 53. Due to the very low temperature of the liquified hydrogen all components of the fluid loading coupling 1, at least the components of the fluid loading coupling 1, in contact with the liquified hydrogen, will be cooled. As described above, the shrinkage rate of the annular seal 35 is higher than the shrinkage rate of, among others, the first and second fluid conduit sections 25, 30.
As a result, the shrinkage of the annular seal 35 will be larger than the shrinkage of, among others, the first and second fluid conduit sections 25, 30. Therefore, the annular seal 35 tightens around the first and second fluid conduit sections 25, 30, thereby closing off the gap 34 between the facing ends 29, 33 of the first and second fluid conduit sections 25, 30.
Furthermore, when the liquified hydrogen has flown into the chamber 35, the temperature of the liquified hydrogen within the chamber 35 increases. As the temperature at which hydrogen is completely liquid and the critical temperature are so close to each other, the hydrogen within the chamber 35 will at least partially evaporate, such that gaseous hydrogen will be present within the chamber 35. Because of the gaseous hydrogen within the chamber 35, the pressure within the chamber 35 also increases. The inventors have found that the increased pressure works on the annular seal 53, thereby pushing the annular seal 53 against the outer circumference of the first and second fluid conduit sections 25, 30. This contributes to closing off the gap 34 between the facing ends 29, 33 of the first and second fluid conduit sections 25, 30.
It is to be understood that the above description is included to illustrate the operation of the preferred embodiments and is not meant to limit the scope of the invention.
From the above discussion, many variations will be apparent to one skilled in the art that would yet be encompassed by the scope of the present invention.
Claims (16)
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NL2031473A NL2031473B1 (en) | 2022-04-01 | 2022-04-01 | Fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids |
| DE102023108303.1A DE102023108303A1 (en) | 2022-04-01 | 2023-03-31 | Liquid loading connector for a rotatable connection of liquid pipes for cryogenic liquids |
| JP2023060138A JP2023153101A (en) | 2022-04-01 | 2023-04-03 | Fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NL2031473A NL2031473B1 (en) | 2022-04-01 | 2022-04-01 | Fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| NL2031473B1 true NL2031473B1 (en) | 2023-10-24 |
Family
ID=82483008
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| NL2031473A NL2031473B1 (en) | 2022-04-01 | 2022-04-01 | Fluid loading coupling for rotatable coupling of fluid conduits for cryogenic fluids |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2023153101A (en) |
| DE (1) | DE102023108303A1 (en) |
| NL (1) | NL2031473B1 (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3371946A (en) * | 1965-10-02 | 1968-03-05 | Gustave A. Bleyle Jr. | Cryogenic coupling |
| DE2012882A1 (en) * | 1970-03-13 | 1971-09-30 | Mannesmann Ag | |
| WO2004033950A1 (en) * | 2002-10-11 | 2004-04-22 | Societe Europeenne D'ingenierie Mecanique-Eurodim | Swivel joint system |
| US20210061640A1 (en) | 2017-12-28 | 2021-03-04 | Kawasaki Jukogyo Kabushiki Kaisha | Fluid loading joint and fluid loading equipment |
| US20210071795A1 (en) | 2017-12-28 | 2021-03-11 | Kawasaki Jukogyo Kabushiki Kaisha | Fluid loading joint |
-
2022
- 2022-04-01 NL NL2031473A patent/NL2031473B1/en active
-
2023
- 2023-03-31 DE DE102023108303.1A patent/DE102023108303A1/en active Pending
- 2023-04-03 JP JP2023060138A patent/JP2023153101A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3371946A (en) * | 1965-10-02 | 1968-03-05 | Gustave A. Bleyle Jr. | Cryogenic coupling |
| DE2012882A1 (en) * | 1970-03-13 | 1971-09-30 | Mannesmann Ag | |
| WO2004033950A1 (en) * | 2002-10-11 | 2004-04-22 | Societe Europeenne D'ingenierie Mecanique-Eurodim | Swivel joint system |
| US20210061640A1 (en) | 2017-12-28 | 2021-03-04 | Kawasaki Jukogyo Kabushiki Kaisha | Fluid loading joint and fluid loading equipment |
| US20210071795A1 (en) | 2017-12-28 | 2021-03-11 | Kawasaki Jukogyo Kabushiki Kaisha | Fluid loading joint |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2023153101A (en) | 2023-10-17 |
| DE102023108303A1 (en) | 2023-10-12 |
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