WO2009112478A1 - Dispositif et procédé de préparation de carburant de gaz naturel - Google Patents

Dispositif et procédé de préparation de carburant de gaz naturel Download PDF

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Publication number
WO2009112478A1
WO2009112478A1 PCT/EP2009/052763 EP2009052763W WO2009112478A1 WO 2009112478 A1 WO2009112478 A1 WO 2009112478A1 EP 2009052763 W EP2009052763 W EP 2009052763W WO 2009112478 A1 WO2009112478 A1 WO 2009112478A1
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WO
WIPO (PCT)
Prior art keywords
natural gas
compression stage
compressor
piston
compression
Prior art date
Application number
PCT/EP2009/052763
Other languages
German (de)
English (en)
Inventor
Besim Fejzuli
Omri Senn
Original Assignee
Burckhardt Compression Ag
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Burckhardt Compression Ag filed Critical Burckhardt Compression Ag
Publication of WO2009112478A1 publication Critical patent/WO2009112478A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J99/00—Subject matter not provided for in other groups of this subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J99/00—Subject matter not provided for in other groups of this subclass
    • B63J2099/001—Burning of transported goods, e.g. fuel, boil-off or refuse
    • B63J2099/003—Burning of transported goods, e.g. fuel, boil-off or refuse of cargo oil or fuel, or of boil-off gases, e.g. for propulsive purposes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T70/00—Maritime or waterways transport
    • Y02T70/50—Measures to reduce greenhouse gas emissions related to the propulsion system
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T70/00—Maritime or waterways transport
    • Y02T70/50—Measures to reduce greenhouse gas emissions related to the propulsion system
    • Y02T70/5218—Less carbon-intensive fuels, e.g. natural gas, biofuels

Definitions

  • the invention relates to an apparatus and a method for providing natural gas fuel.
  • Liquid natural gas also referred to as "Liquefied natural gas” or “LNG” for short, is natural gas that has been cooled to a temperature of -162 ° C and has therefore assumed a liquid state.
  • LNG Low-density natural gas
  • a convenient way to transport natural gas over long distances is to liquefy natural gas and transport it in tankers, also known as LNG tankers. At the destination, the liquid natural gas is transformed back into gaseous natural gas.
  • G1414WO Power engines of the LNG tanker with this fuel As described in detail in the document, a boil-off gas is formed in the upper region of a storage container containing liquefied natural gas, this boil-off gas being taken from the storage container, then compressed, and subsequently as gaseous natural gas of a machine
  • a disadvantage of this device and this method is the fact that it is not able to reliably supply an internal combustion engine with natural gas when the internal combustion engine is driven with different loads and / or that natural gas must be flared.
  • the object of the present invention is to propose a more advantageous device and a more advantageous method, which allow to recover from the exhaust gas of liquefied natural gas a fuel which is suitable for use in internal combustion engines of LNG tankers.
  • the object is achieved with a device having the features of claim 1.
  • the dependent claims 2 to 8 relate to further advantageous embodiments of the inventive device.
  • the object is further achieved by a method comprising the features of claim 9.
  • the dependent claims 10 to 15 relate to further advantageous embodiments of the inventive method.
  • a device for providing natural gas fuel comprising a compressor with an inlet for a natural gas flow, wherein the inlet fluid is conductively connectable to an LNG storage tank to supply Abdampfgas from the LNG storage tank, and an outlet of the fluid conducting can be connected to a natural gas supply line, wherein the compressor comprises a first and then a second compression stage, wherein the first and the second compression stage as a labyrinth-sealed piston compressor or piston rings sealed piston compressors are designed, and wherein the compressor subsequently comprises at least a third compression stage, which Piston ring sealed piston compressor or labyrinth-sealed piston compressor is configured, and wherein after the first or second compression stage, a return line is arranged, for the recovery of natural gas in the LNG storage tank.
  • the third compression stage is followed by a fourth compression stage downstream.
  • the fourth compression stage is followed by a fifth compression stage.
  • the third, and if present, the fourth and fifth compression stage designed as a piston ring compression stage configured.
  • the third, and if present, the fourth and fifth compression stage designed as a piston ring compression stage configured.
  • Compression stage designed as a labyrinth-sealed compression stage.
  • all the compression stages are designed either as a compression-type labyrinth-sealed compression stage or as a compression stage sealed with piston rings.
  • the first and second compression stage designed as a labyrinth-sealed piston compressor and the subsequent compression stages designed as piston rings with sealed piston compressor.
  • the inventive device has the advantage that from the exhaust gas of an LNG storage tank, a natural gas flow can be generated, which has a pressure between 100 bar and 500 bar, in particular between 150 bar and 300 bar, wherein the natural gas stream is used to supply fuel to an internal combustion engine, preferably a turbine or a piston engine such as a diesel engine.
  • the device according to the invention has the advantage that the amount of fuel supplied to the internal combustion engine can be varied within a large range, although exhaust gas has to be withdrawn from the LNG storage vessel. The removal of the exhaust gas from the LNG storage tank is required to avoid too high a pressure increase in the LNG storage tank.
  • the device according to the invention makes it possible, in addition to the supply of natural gas to the internal combustion engine, to partially re-liquefy the exhaust gas withdrawn from the LNG storage tank and to return it to the LNG storage tank. to
  • Partial reliquefaction requires oil-free compaction, using advantageously labyrinth-sealed reciprocating compressors.
  • the device according to the invention thus has the advantage that a sufficient amount of natural gas with a correspondingly required pressure can be provided to the internal combustion engine and that, in addition, an excessive increase in pressure in the LNG storage container is avoided.
  • the device according to the invention is preferably arranged on a ship, in particular on an LNG tanker, and makes it possible to obtain the fuel for supplying the internal combustion engines from the liquid natural gas stored in the LNG storage tanks.
  • the Abdampfgas of the liquid natural gas usually has a temperature of about minus 162 ° C and a pressure of typically 1 bar.
  • the erf ⁇ ndungshacke device allows this Abdampfgas to a preferably variable final pressure in the range between 100 bar and 500 bar, in particular 150 bar and 300 Bar, and also allows, if necessary, that the amount of natural gas supplied to the engine is variable, and also makes it possible to ensure that the pressure in the LNG storage tank does not rise to an impermissibly high value.
  • the labyrinth sealed piston compressor has the advantage that this natural gas in a wide temperature range of preferably between - 160 0 C to + 100 0 C can suck and compact, and that the compression takes place oil-free. Since the compression takes place oil-free, the compressed natural gas, if necessary, can also be returned to the LNG storage tank via a return feed line.
  • the piston ring sealed piston compressor has the advantage that this natural gas can compress to a high pressure, which is preferably oil lubricated.
  • the erf ⁇ ndungsconcee combination of labyrinth-sealed piston compressor and piston ring sealed piston compressor has the advantage that a very reliable and cost-effective compression of natural gas, starting from a Abdampfgas is possible, which in particular allows the engine of an LNG tanker
  • a check valve is arranged between the second and third compression stage, wherein in the first and second compression stage is compressed oil-free.
  • Compressor stage or from two compressor stages connected in series, or from a reciprocating compressor or from two piston compressors connected in series.
  • all compression stages are arranged on a common housing and driven by a common crank mechanism.
  • the crank mechanism on compensation weights to achieve a particularly high smoothness of the compressor, which is particularly advantageous when operating on a ship.
  • At least one of the compression stages to a bypass with controllable valve to control the reflux, and thus to control the flow rate and / or the delivery pressure of the compression stage.
  • Fig. 1 shows schematically an embodiment of a compressor
  • Fig. 2 shows schematically a further embodiment of a compressor
  • FIG. 3 schematically shows a development of the compressor shown in FIG. 2;
  • Fig. 5 is a detail view of the compressor shown in Fig. 4;
  • FIG. 6 shows a further detail view of the compressor shown in FIG. 4;
  • FIG. 7 shows schematically two compressors arranged in parallel for the supply of two diesel engines
  • FIG. 10 shows a longitudinal section through a crosshead with balancing mass.
  • G1414WO Fig. 1 1 a side view of a crosshead with
  • FIG. 12 schematically shows a development of the compressor shown in FIG. 2;
  • FIG 13 shows an LNG storage tank with heat exchanger and supply and discharge lines.
  • Figure 1 shows schematically a device 1 for providing natural gas fuel
  • a compressor 2 with an inlet 3 for a natural gas stream 4 and comprising an outlet 7, the fluid is conductively connected to a natural gas supply line 8 for a downstream internal combustion engine.
  • the inlet 3 is fluidly connectable to an LNG storage tank 5 in which liquid natural gas Ef is stored, usually at a pressure of 1 bar and a temperature of minus 162 ° C.
  • liquid natural gas Ef gaseous natural gas Eg forms, also referred to as Abdampfgas 6.
  • This Abdampfgas 6 is sucked by the compressor 2, compressed, and leaves the compressor 2 at the outlet 7 as natural gas under a pressure of preferably between 150 bar and 300 bar.
  • the compressor 2 is preferably arranged on an LNG tanker, the compressed natural gas preferably serves as fuel for the drive motor.
  • the compressor 2 comprises a first and subsequently a second compression stage 9, 10, wherein the first and the second compression stage 9, 10 designed as a labyrinth piston compressor 11, 12 are configured, and wherein the first compression stage 9 has a larger piston diameter than the second compression stage 10th
  • the compressor 2 includes one below
  • G1414WO third and fourth compression stage 13, 14, which are designed as a piston ring sealed piston compressor 15. Thereafter, the compressed natural gas is supplied to the outlet 7.
  • a check valve 16 is arranged between the second compression stage 10 and the third compression stage 13, so that the natural gas can flow only in one direction.
  • the compressor 2 shown in FIG. 1 thus comprises four piston compressors 11, 12, 15 connected in series.
  • At least one of the compression stages 9, 10, 13, 14 has a bypass 20, 21, 22 with a e.g. via an electrical line 23a, 24a, 25a controllable valve 23,24,25.
  • An advantage of this arrangement is the fact that so that the pressure and / or the flow rate of the outlet 7 pending or can be regulated by eating natural gas.
  • a return line 50 is provided, via which a partial flow of the LNG storage tank removed natural gas can be reliquefied and the LNG storage tank can be fed again.
  • the return feed line 50 is shown only schematically in FIG. FIG. 13 shows an exemplary embodiment in detail.
  • FIG. 1 has two compression stages 9, 10 and 13, 14 connected in series, respectively.
  • the device 1 could also be designed in such a way
  • the two compression stages 9, 10 and / or 13, 14 are each formed by a single compression stage, or three compression stages connected in series are used instead of the two illustrated in each case.
  • the embodiment shown in Figure 1 could also have only a single piston compressor 15, or three series-connected reciprocating compressor 15th
  • the compressor 2 in comparison to the embodiment shown in Figure 1, additional piston compressors 11, 12, 15 include, which form additional, connected in series compressor stages to achieve a higher final pressure , or which form parallel compressor stages to achieve a larger flow rate, or which have both in series and parallel compressor stages.
  • the first compression stage 9 could consist of two piston compressors 1 1 connected in parallel in order to increase the flow rate.
  • the second compression stage 10 consists in a preferred embodiment, as shown in Figure 2 of two compressor stages by two piston compressor 12 may be arranged in series connection successively to increase the compression pressure.
  • the need for an additional compressor stage in the first or second compression stage 9, 10 is given in particular when the suction pressure is relatively low.
  • the third and fourth compression stage 13, 14 could, for example, at least one additional series-connected piston compressor 15 to increase the final pressure of the natural gas.
  • the inventive compressor 2 can thus be configured in different ways, depending on the given or
  • the compressor 2 shown in Figure 2 shows a preferred embodiment with five connected in series reciprocating compressors 1 1, 12, 15th
  • the compressor 2 shown in Figure 2 comprises a plurality of pressure sensors 42a, 42b, 42c, 42d for measuring the natural gas pressure at the respective location.
  • the compressor 2 also comprises three control devices 40a, 40b, 40c.
  • a pressure setpoint value 41 is specified for the control device 40a, the actual pressure being the end pressure 42d of the natural gas in the region of the outlet 7.
  • the control device 40a influences the position of the valve 23, thereby influencing the return flow in the bypass 20.
  • the regulator 40b compares the pressures 42a, 42b before and after the second compression stage 10
  • the regulator 40c compares the pressures 42c, 42d before and after the third and fourth compression stages 13, 14 with the position of the valve 24 based on these measured values or 25 to influence and thereby the reflux flow in the
  • Bypass 21 and 22 influence.
  • the control devices 40a, 40b, 40c could also be connected to a higher-level control. It may prove advantageous, as shown in FIG. 2, to arrange coolers 31 after the compression stages 10, 13, 14 in order to cool the compressed natural gas.
  • the cooler 31 is cooled, for example, with a water-glycol mixture.
  • FIG. 3 shows the part of the compressor 2 already shown in FIG. 2 arranged to the left of the check valve 16 in a further
  • the compressor 2 also has a recirculation line 50, whose flow is controlled by a closing valve 51, wherein the return feed line 50 as shown, preferably arranged upstream of the check valve 16 left or in the direction of flow of natural gas. As shown in detail in FIG.
  • the recirculation line 50 is fed to a reliquefaction device so that the superfluous natural gas is returned to the LNG storage container 5.
  • the recycle line 50 could also open into a gas combustion device where the natural gas is flared, for example. However, this would have the disadvantage that the flared natural gas can not be used profitably.
  • Figure 12 shows a very similar arrangement as the arrangement shown in Figure 3, wherein the return feed line 50 branches off after the second compression stage 10.
  • the pressure in the return line 50 may be through the first and second
  • Compression stage 9, 10 and / or also by the bypass valves 23, 24 are influenced.
  • the pressure in the return line 50 is in an advantageous embodiment in the range between 35 and 52 bar.
  • the pressure and / or the amount of natural gas supplied to the internal combustion engine at the outlet 7 can in particular by the
  • G1414WO third and fourth compression stage 13, 14 and / or controllable valves 25 are determined.
  • the device according to the invention thus makes it possible to regulate both the natural gas supplied to the internal combustion engine with regard to pressure and / or quantity and to regulate the pressure in the LNG storage container.
  • the check valve 16 shown in FIGS. 1, 3 and 12 could also be dispensed with if the third and fourth compression stages 13, 14 comprise only oil-free or lubricant-free compressors.
  • FIG. 4 shows in a section an embodiment of a compressor 2 according to the invention in detail.
  • the compressor 2 comprises a common housing 18 with a crank mechanism 17 and a spacer 18 a.
  • the crank mechanism 17 includes a crankshaft 17a mounted therein, and six crossheads 17c spaced apart along the crankshaft 17a with the crankshaft 17a via push rods 17b, the crank mechanism 17 having crosshead bores 17d into which the crossheads 17c are guided, each crosshead 17c is connected to a piston rod 17e, and each piston rod 17e is connected to a piston 9a, 10a, 13a, 14a.
  • the crankshaft 17a is connected via a flywheel 26 with a drive shaft 27.
  • the spacer 18a has at the top a support surface on which in the illustrated embodiment, six reciprocating compressors 11, 12, 15 are arranged, the pistons 9a, 10a, 13a, 14a are driven by piston rods 17e of the common crankshaft 17a.
  • Figures 5 and 6 show the reciprocating compressor 11, 12, 15 in detail.
  • the compressor 2 comprises a first compression stage 9 with two piston compressors 11, which are designed as a labyrinth sealed piston compressor 11, wherein the piston compressor 11 of the compression stage 9, as shown in Figure 5 in
  • G1414WO Detail comprising a piston 9a with piston diameter 9b, wherein the piston 9a on the outer cylindrical surface labyrinth seals 9c, and a surface structure, which causes a non-contact labyrinth seal 9c in connection with the cylinder wall 9d.
  • Piston compressor 11 also includes a piston rod guide 9e to guide the piston rod 17e and piston 9a.
  • the two left and right piston compressor 11 may be arranged mutually parallel or in series with respect to the natural gas to be compressed.
  • the first compression stage 9 has a double-acting cylinder in that both sides of the piston 9a delimit a compression space for compressing the natural gas.
  • the first compression stage 9 is preferably designed in a cryogenic construction, and made of a material suitable for low temperatures.
  • the compressor 2 comprises a second compression stage 10 consisting of two series-connected reciprocating compressors 12, which are also designed as a labyrinth sealed piston compressor 12, each piston compressor 12 of the second compression stage 10, as shown in detail in Figure 5, a piston 10a with piston diameter 10b in which the piston 10a has labyrinth seals 10c on the outer cylindrical surface, or a surface structure which, in conjunction with the cylinder wall 10d, effects a non-contact labyrinth seal 10c.
  • the labyrinth seals could also be arranged on the cylinder wall 10d, and the piston 10a have a relatively smooth surface.
  • the second compression stage 10 also includes a piston rod guide 10e around the piston rod
  • the two juxtaposed piston compressors 12 are preferably arranged in series with respect to the natural gas to be compressed.
  • the first compression stage 9 has a larger piston diameter 9b than the second compression stage 10 with piston diameter 10b.
  • the compressor 2 comprises two piston ring sealed piston compressors 15, wherein each piston compressor 15 is designed as a double-acting cylinder and has two compression stages, a third compression stage 13 and a fourth compression stage 14, wherein as shown in detail in Figure 6, the third compression stage 13 a piston 13 a comprising a plurality of piston rings 13b and a cylinder 13c, and wherein the fourth compression stage 14 comprises a piston 14a with a plurality of piston rings 14b and a cylinder 14c.
  • the third compression stage 13 is disposed on the piston top, whereas the fourth compression stage 14 is disposed on the piston bottom.
  • the third compression stage 13 could also on the
  • Plunger bottom and the fourth compression stage 14 may be arranged on the piston top.
  • the two piston compressors 15 are preferably mutually connected in series, but may also be connected in parallel.
  • the crosshead is oil lubricated.
  • the spacer 18a ⁇ labstreifer 17f are arranged, which surround the piston rod 17e.
  • the common housing 18 is supplied via an oil supply 28 with lubricating oil, and has at the bottom of the bottom outlets, via which the
  • G1414WO Oil is removed via the oil drains 29 again.
  • This embodiment has the advantage that bottom of the housing 18 no permanently existing oil sump is formed, since the oil is removed.
  • the housing 18 in its most preferred embodiment has six crossheads 17c and correspondingly six piston rods 17e.
  • a compensation weight 19 is connected to the crosshead 17c and / or to the piston rod 17e.
  • the compensation weight 19 is selected such that the respective crosshead 17c, the associated piston rod 17e, the associated piston 9a, 10a and the associated compensation weight 19 have substantially the same mass. This embodiment with compensating weight 19 causes the compressor 2 has a great smoothness during operation.
  • the compressor 2 according to the invention is therefore preferably configured such that it has low forces and torques, and the compressor 2 is therefore particularly well suited for operation on a ship.
  • the compressor 2 shown in Figure 4 has the advantage that it is very compact and therefore requires little space, and that the compressor 2 is driven by a single, compactly constructed electric motor.
  • the compensation weights 19 are preferably chosen such that each of the six movable assemblies has the same mass, which ensures a great smoothness with low vibration.
  • the embodiment shown in Figure 4 with a crankshaft 17a with six cranks causes the attacking forces are relatively optimally balanced, so that low vibration forces occur.
  • FIG. 10 shows a longitudinal section through a crosshead 17c with piston rod 17e, crosshead pins 17g, connecting means 17h and guide surface 17i.
  • the balancing mass 19 can also be located somewhere above the crosshead 17c, wherein the balancing mass 19 is preferably connected to the piston rod 17e.
  • Figure 11 shows the arrangement shown in Figure 10 in a side view, wherein the push rod 17b via the crosshead pin 17g with the
  • the balancing mass 19 could consist of a single part. However, the balancing mass 19 preferably consists of a plurality of part weights 19a, preferably of geometrically identically designed part weights 19a. In a preferred embodiment, the part weights 19a, as shown in Figures 10 and 11, designed plate-shaped.
  • FIG. 13 shows an LNG storage tank 5 in detail.
  • the exhaust gas 6 is withdrawn via a line 70 and fed to a heat exchanger 60 with cooling coils 61, 62. Thereafter, the exhaust gas 6 is supplied via lines 73 and 74 as natural gas stream 4 to the compressor 2.
  • the return feed line 50 is fed to the heat exchanger 60 after a closing valve 51.
  • a separation device 67 is arranged, with line 64, controllable control valve 65 and sensor 66.
  • the separation device 67 comprises a line 72 whose flow rate can be controlled via the control valve 68 and the sensor 69.
  • a line 71 conveys natural gas from the separator 67 to the heat exchanger 60, wherein the line 71 is connected via the cooling coil 60 to the line 74, which opens into the natural gas stream 4.
  • the arrangement shown in FIG. 13 makes it possible to back-liquefy a partial stream of the natural gas stream and to feed it back to the LNG storage container, the quantity of the partial stream being controllable.
  • G1414WO shown is a pressure sensor that allows to detect the applied pressure in the LNG storage tank 5.
  • the device according to the invention and the method according to the invention make it possible to take such a large amount of exhaust gas from the LNG storage tank 5 that the pressure moves in a predeterminable range, wherein the amount of natural gas supplied to the internal combustion engine can also be controlled by a partial flow via the recirculation line 50 is reliquefied, and the LNG storage tank 5 is fed.
  • crankshaft 17a In the case of the compressor 2 illustrated in FIG. 4, all compression stages 9, 10, 13, 14 or all reciprocating compressors 11, 12, 15 are driven by the same crankshaft 17a.
  • the housing 18 it is also possible to divide the housing 18 into two separate housings by, for example, the first and second compression stages 9, 10 are arranged on the first housing and the third and fourth compression stage 13, 14 are arranged on the second housing. All compression stages 9, 10, 13, 14 could be driven by the same crankshaft 17a. In a further embodiment, however, two or even more separate crankshaft 17a could be used, which could also be driven by separate drives such as motors.
  • FIG. 7 schematically shows an arrangement with two compressors 2 arranged in parallel, to which a natural gas flow 4, which consists of exhaust gas 6, is fed via an inlet 3.
  • a natural gas flow 4 which consists of exhaust gas 6
  • the compressed natural gas in two natural gas supply lines 8 via a closing valve 52, 53 is supplied to the respective internal combustion engine 32, wherein the
  • G1414WO Engine 32 for example, a piston engine such as a marine diesel engine, which is also suitable for operation with natural gas.
  • the control device of the internal combustion engine 32 presets a pressure setpoint 41 for the supplied natural gas, this pressure setpoint 41 being supplied to the two compressors 2 as the setpoint.
  • the internal combustion engine 32 is operated such that it requests a specific gas pressure via the pressure setpoint 41 at a certain power.
  • the desired pressure value 41 is the only desired value signal for the compressor 2 shown in FIGS. 1 and 2.
  • the gas quantity required by the internal combustion engine 32 is not known.
  • the device according to the invention and the method according to the invention make it possible to provide natural gas with a certain pressure and variable amount from exhaust gas 6.
  • the labyrinth-sealed reciprocating compressor 11, 12 has the advantage that it can be operated reliably over a wide temperature range, in particular even at very low temperatures and also in the case of larger, occurring temperature changes.
  • Figure 8 shows after the start of the compressor 2, the time course TA of the temperature of the sucked natural gas at the suction side of the first compression stage 9.
  • the time course TB shows the temperature of the natural gas at the pressure side of the first compression stage 9.
  • the time course TC shows the temperature of natural gas at the pressure side of the second compression stage 10. in the embodiment shown it can be seen that the labyrinth sealed piston compressors 11, 12 in a temperature range between - 150 0 C and let +100 0 C operate reliably.
  • the inventive compressor 2 also has
  • G1414WO has the advantage that it can be started substantially at each temperature applied to the suction side.
  • exhaust gas 6 is taken from an LNG storage tank 5 containing liquid natural gas. Subsequently, the exhaust gas 6 is compressed in a compression stage 9, 10, wherein the compression stage 9, 10 comprises a labyrinth-sealed piston compressor 11, 12. Thereafter, the natural gas is compressed in a compression stage 13, 14, which comprise a reciprocating compressor 15 sealed with piston rings. The natural gas is compressed to a pressure between 100 bar and 500 bar, preferably between 150 bar and 300 bar, and then provided at an outlet 7.
  • all the compression stages 9, 10, 13, 14 can also be configured as piston-type compressors 11, 12 sealed with labyrinth or as piston compressors 15 sealed with piston rings.
  • the labyrinth-sealed piston compressor 11, 12 advantageously forms a first and a second compression stage 9, 10, and the piston ring sealed piston compressor 15 preferably forms a third and a fourth compression stage 13, 14, so that the natural gas of preferably at least four compression stages 9, 10, 13 , 14 is compressed, wherein the second compression stage 10 in a particularly advantageous embodiment, two compressor stages connected in series or piston compressor 12 has.
  • the natural gas is supplied to the second compression stage 10 via a check valve 16 of the third compression stage 13.
  • At least one of the reciprocating compressors 11, 12, 15 comprises a bypass 20, 21, 22, the natural gas being fed back via the at least one bypass 20, 21, 22 in such a way that the natural gas at the outlet 7 has a predetermined desired pressure value Psoll.
  • the reflux in the bypasses 20, 21, 22 are controlled such that the final pressure at the outlet 7 in a wide range, for example, 150 bar to 300 bar is variable, and that the funded amount of natural gas in a wide range between 0% and 100% is variable, so that the compressor 2 on the pressure side at the outlet 7 has a variable, over the setpoint 41 predeterminable final pressure.
  • the compressor 2 according to the invention is able to maintain the final pressure given by the desired value 41 when the internal combustion engine 32 receives varying amounts of natural gas.
  • a flow rate in the range between 0% and 100% can be recirculated via the respective bypass 20, 21, 22.
  • the ability to reduce the flow rate up to 0%, or the possibility of a recirculation rate of 100% in a bypass 20,21, 22 has the advantage that the compressor 2 can also be driven when no natural gas is taken from the outlet 7.
  • the electric motor, which drives the crankshaft 17a of the compressor 2 is, depending on the configuration, for example, only for a certain number of starts per unit time available. For example, the occurring during startup
  • FIG. 9 shows a control concept for regulating the pressure and mass flow of the compressed natural gas at the outlet 7.
  • FIG. 9 shows the percentage mass flow in kg / h as a function of the power applied to the drive shaft 27 at a pressure P1 of 150 bar and at Pressure P2 of 265 bar.
  • the control concept is explained in detail with reference to FIG. 2 and the curve P2 according to FIG.
  • the course of the curve P2 marked Rl is achieved by changing the position of the valve 23, thereby changing the recovery rate in the bypass 20.
  • the course of the curve P2 marked R3 is also achieved by changing the position of the valve 25, thereby changing the rate of return in the bypass 22.
  • the course of the curve P2 labeled R4 is also achieved by changing the position of the valve 24, thereby changing the recovery rate in the bypass 21.
  • the mass flow or the delivery rate of natural gas can be changed at a constant pressure at the outlet 7 between 0% and 100%.
  • the same control method applies to other pressures, for example, for the curve Pl with a pressure of 150 bar.
  • the arrangement according to Figure 2 can also regulate pressure changes.
  • the control devices 40a, 40b, 40c are advantageously configured as P-I controllers. Assuming there is a pressure setpoint 41 at the control device 40a and the pressure actual value 42d drops below the predetermined pressure setpoint 41,
  • control device 40a would partially or completely close the valve 23, so that in the bypass 20 less natural gas flows back, with the result that at the outlet 7 a larger amount of natural gas is available and the pressure of the natural gas at the outlet 7 increases.
  • the control device 40b detects two actual values 42a, 42b, an input actual value 42a and an output actual value 42b.
  • the control device 40b is given two setpoints, not shown, an input setpoint and an output setpoint. If the input actual value 42a is smaller than the input setpoint, then the valve 24 is opened. If the output setpoint is less than the output actual value 42, then the valve 24 is also opened.
  • the same control method also applies to the control device 40c and the associated sensors and the valve 25th
  • the compressor 2 and the engine 32 are preferably operated such that the engine 32 a
  • the natural gas is at least in the first and second piston compressors 11, 12 compressed oil-free.
  • G1414WO sealed piston compressor 15 is driven by a second common crankshaft.
  • An advantageous method is characterized in that the natural gas is cooled after a compression stage (9, 10, 13, 14).
  • a further advantageous method is characterized in that all reciprocating compressors (11, 12, 15) are driven by a common crankshaft (17a).
  • a further advantageous method is characterized in that the labyrinth-sealed piston compressor (11, 12) is driven by a first common crankshaft (17a) and the piston compressor sealed by piston rings (15) by a second common crankshaft.
  • Another advantageous method is characterized in that a part of the compressed natural gas is flared or re-liquefied.
  • Another advantageous method is characterized in that between the first and second compression stage (9, 10) an intercooler (31) is switched on or off.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

L'invention concerne un dispositif (1) de préparation de carburant de gaz naturel comportant un compresseur (2) comprenant une entrée (3) pour un flux de gaz naturel (4), l'entrée (3) pouvant être connectée en communication fluidique avec un réservoir de gaz naturel liquéfié (GNL) (5) afin d'extraire des gaz d'échappement (6) du réservoir de gaz naturel liquéfié (5), ainsi qu'une sortie (7) pouvant être connectée en communication fluidique avec une conduite d'alimentation en gaz naturel (8). Le compresseur (2) comporte un premier et un deuxième étage de compression successif (9, 10) conçus en tant que compresseurs à piston étanchés par labyrinthe (11, 12), ou en tant que compresseurs à piston étanchés par segment de piston (15). Le premier étage de compression (9) présente de préférence un diamètre de piston supérieur à celui du deuxième étage de compression (10), et le compresseur comporte ensuite au moins un troisième étage de compression (13, 14) conçu en tant que compresseur à piston étanché par labyrinthe (11, 12), ou en tant que compresseur à piston étanché par segment de piston (15). Une conduite de recyclage (50) est disposée en aval du premier et du deuxième étage de compression (9, 10) pour le recyclage de gaz naturel dans le réservoir de gaz naturel liquéfié (5).
PCT/EP2009/052763 2008-03-10 2009-03-10 Dispositif et procédé de préparation de carburant de gaz naturel WO2009112478A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
EP08102472.1 2008-03-10
EP08102472 2008-03-10
EP08102786.4 2008-03-19
EP08102786 2008-03-19
EP08104413 2008-06-13
EP08104413.3 2008-06-13

Publications (1)

Publication Number Publication Date
WO2009112478A1 true WO2009112478A1 (fr) 2009-09-17

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Cited By (13)

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KR20140075648A (ko) * 2012-12-11 2014-06-19 대우조선해양 주식회사 증발가스 처리 시스템
EP2714167A4 (fr) * 2011-05-24 2015-06-24 Invacare Corp Compresseur d'oxygène avec étage de surpression
KR20160080170A (ko) * 2014-12-29 2016-07-07 삼성중공업 주식회사 증발가스 처리장치
KR20160096564A (ko) * 2016-03-10 2016-08-16 삼성중공업 주식회사 증발가스 처리장치
WO2016176006A1 (fr) 2015-04-30 2016-11-03 Atlas Copco Comptec, Llc Système et procédé de manipulation de gaz destinés à gérer efficacement les changements des conditions gazeuses
US9624918B2 (en) 2012-02-03 2017-04-18 Invacare Corporation Pumping device
KR20170104348A (ko) * 2016-03-07 2017-09-15 현대중공업 주식회사 증발가스 재액화 시스템 및 선박
KR20170126075A (ko) * 2016-05-04 2017-11-16 현대중공업 주식회사 가스 처리 시스템 및 이를 포함하는 선박
KR20180108283A (ko) * 2017-03-24 2018-10-04 대우조선해양 주식회사 선박용 증발가스 재액화 시스템 및 방법
KR20180135799A (ko) * 2017-06-13 2018-12-21 현대중공업 주식회사 증발가스 재액화 시스템 및 선박
US10220928B2 (en) 2012-03-30 2019-03-05 Mitsubishi Shipbuilding Co., Ltd. Ship, fuel gas supply apparatus, and fuel gas supply method
KR20190139724A (ko) * 2018-06-08 2019-12-18 대우조선해양 주식회사 선박용 증발가스 재액화 시스템 및 상기 시스템 내의 윤활유 배출 방법
EP3961034A1 (fr) * 2020-08-31 2022-03-02 Burckhardt Compression AG Bague d'étranglement

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AU2012258841B2 (en) * 2011-05-24 2016-09-29 Invacare Corp. Oxygen compressor with boost stage
EP2714167A4 (fr) * 2011-05-24 2015-06-24 Invacare Corp Compresseur d'oxygène avec étage de surpression
US9624918B2 (en) 2012-02-03 2017-04-18 Invacare Corporation Pumping device
US10220928B2 (en) 2012-03-30 2019-03-05 Mitsubishi Shipbuilding Co., Ltd. Ship, fuel gas supply apparatus, and fuel gas supply method
KR20140075648A (ko) * 2012-12-11 2014-06-19 대우조선해양 주식회사 증발가스 처리 시스템
KR102227891B1 (ko) * 2012-12-11 2021-03-16 대우조선해양 주식회사 증발가스 처리 시스템
KR102186045B1 (ko) 2014-12-29 2020-12-04 삼성중공업 주식회사 증발가스 처리장치
KR20160080170A (ko) * 2014-12-29 2016-07-07 삼성중공업 주식회사 증발가스 처리장치
KR20180004198A (ko) * 2015-04-30 2018-01-10 아틀라스 콥코 콤텍트, 엘엘씨 가스 상태의 변화를 효율적으로 관리하기 위한 가스 처리 시스템 및 방법
CN106089637A (zh) * 2015-04-30 2016-11-09 阿特拉斯科普柯康珀泰克有限责任公司 用于有效地管理气体条件中的改变的气体处理系统与方法
KR102562422B1 (ko) * 2015-04-30 2023-08-01 아틀라스 콥코 콤텍트, 엘엘씨 가스 상태의 변화를 효율적으로 관리하기 위한 가스 처리 시스템 및 방법
WO2016176006A1 (fr) 2015-04-30 2016-11-03 Atlas Copco Comptec, Llc Système et procédé de manipulation de gaz destinés à gérer efficacement les changements des conditions gazeuses
EP3289292A4 (fr) * 2015-04-30 2018-12-05 Atlas Copco Comptec, LLC Système et procédé de manipulation de gaz destinés à gérer efficacement les changements des conditions gazeuses
KR20170104348A (ko) * 2016-03-07 2017-09-15 현대중공업 주식회사 증발가스 재액화 시스템 및 선박
KR102255790B1 (ko) * 2016-03-07 2021-05-25 현대중공업 주식회사 증발가스 재액화 시스템 및 선박
KR20160096564A (ko) * 2016-03-10 2016-08-16 삼성중공업 주식회사 증발가스 처리장치
KR102189807B1 (ko) * 2016-03-10 2020-12-14 삼성중공업 주식회사 증발가스 처리장치
KR102175551B1 (ko) * 2016-05-04 2020-11-09 한국조선해양 주식회사 가스 처리 시스템 및 이를 포함하는 선박
KR20170126075A (ko) * 2016-05-04 2017-11-16 현대중공업 주식회사 가스 처리 시스템 및 이를 포함하는 선박
KR102066632B1 (ko) * 2017-03-24 2020-01-15 대우조선해양 주식회사 선박용 증발가스 재액화 시스템 및 방법
KR20180108283A (ko) * 2017-03-24 2018-10-04 대우조선해양 주식회사 선박용 증발가스 재액화 시스템 및 방법
KR102088565B1 (ko) * 2017-06-13 2020-03-12 현대중공업 주식회사 증발가스 재액화 시스템 및 선박
KR20180135799A (ko) * 2017-06-13 2018-12-21 현대중공업 주식회사 증발가스 재액화 시스템 및 선박
KR102087180B1 (ko) * 2018-06-08 2020-03-11 대우조선해양 주식회사 선박용 증발가스 재액화 시스템 및 상기 시스템 내의 윤활유 배출 방법
KR102066635B1 (ko) * 2018-06-08 2020-01-15 대우조선해양 주식회사 선박용 증발가스 재액화 시스템 및 상기 시스템 내의 윤활유 배출 방법
KR20190139723A (ko) * 2018-06-08 2019-12-18 대우조선해양 주식회사 선박용 증발가스 재액화 시스템 및 상기 시스템 내의 윤활유 배출 방법
KR20190139724A (ko) * 2018-06-08 2019-12-18 대우조선해양 주식회사 선박용 증발가스 재액화 시스템 및 상기 시스템 내의 윤활유 배출 방법
EP3961034A1 (fr) * 2020-08-31 2022-03-02 Burckhardt Compression AG Bague d'étranglement
WO2022043577A1 (fr) * 2020-08-31 2022-03-03 Burckhardt Compression Ag Bague d'étranglement

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