CN112703316B - Compression cylinder - Google Patents
Compression cylinder Download PDFInfo
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- CN112703316B CN112703316B CN201980058200.3A CN201980058200A CN112703316B CN 112703316 B CN112703316 B CN 112703316B CN 201980058200 A CN201980058200 A CN 201980058200A CN 112703316 B CN112703316 B CN 112703316B
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- cylinder
- piston
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- gas
- compression cylinder
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- 230000006835 compression Effects 0.000 title claims abstract description 207
- 238000007906 compression Methods 0.000 title claims abstract description 207
- 239000010687 lubricating oil Substances 0.000 claims abstract description 33
- 230000002093 peripheral effect Effects 0.000 claims description 45
- 230000008878 coupling Effects 0.000 claims description 29
- 238000010168 coupling process Methods 0.000 claims description 29
- 238000005859 coupling reaction Methods 0.000 claims description 29
- 238000004891 communication Methods 0.000 claims description 19
- 238000007789 sealing Methods 0.000 claims description 11
- 239000002826 coolant Substances 0.000 abstract description 95
- 239000003921 oil Substances 0.000 abstract description 52
- 239000007789 gas Substances 0.000 description 117
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 72
- 239000003949 liquefied natural gas Substances 0.000 description 41
- 238000001816 cooling Methods 0.000 description 35
- 239000003345 natural gas Substances 0.000 description 35
- 239000003507 refrigerant Substances 0.000 description 21
- 239000000446 fuel Substances 0.000 description 14
- 238000002485 combustion reaction Methods 0.000 description 12
- 239000000110 cooling liquid Substances 0.000 description 9
- 239000011347 resin Substances 0.000 description 8
- 229920005989 resin Polymers 0.000 description 8
- 238000003860 storage Methods 0.000 description 7
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 6
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 6
- 230000007423 decrease Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 125000006850 spacer group Chemical group 0.000 description 4
- 238000012546 transfer Methods 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 239000003054 catalyst Substances 0.000 description 3
- 238000006477 desulfuration reaction Methods 0.000 description 3
- 230000023556 desulfurization Effects 0.000 description 3
- 238000003780 insertion Methods 0.000 description 3
- 230000037431 insertion Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 239000007864 aqueous solution Substances 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 239000012809 cooling fluid Substances 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 239000012535 impurity Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 230000007257 malfunction Effects 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000002737 fuel gas Substances 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000001141 propulsive effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- UONOETXJSWQNOL-UHFFFAOYSA-N tungsten carbide Chemical compound [W+]#[C-] UONOETXJSWQNOL-UHFFFAOYSA-N 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
-
- 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
- F04B25/00—Multi-stage pumps
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
-
- 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
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63B—SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING
- B63B25/00—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby
- B63B25/02—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby for bulk goods
- B63B25/08—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby for bulk goods fluid
- B63B25/12—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby for bulk goods fluid closed
- B63B25/16—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby for bulk goods fluid closed heat-insulated
-
- 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
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/30—Use of alternative fuels, e.g. biofuels
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Combustion & Propulsion (AREA)
- Compressor (AREA)
Abstract
The invention provides a compressor which does not need oil supply in each compression stage and does not mix lubricating oil in gas after passing through a final compression stage, and an LNG ship carrying the compressor. In a compressor 1 in which gas supplied from an intake port 3 is compressed in one or more compression stages 9, 10, 13, 14, 15 and is discharged from a discharge port 7, cylinders 11, 12, 16, 17, 18 of the one or more compression stages 9, 10, 13, 14, 15 do not require oil supply in all the compression stages, and at least the cylinders 11, 12, 16, 17, 18 of a final compression stage 9, 10, 13, 14, 15 are cooled by the backflow of a coolant in a flow path provided in a cylinder liner 35.
Description
Technical Field
The present invention relates to a compressor for compressing gas, an LNG ship, and a compression cylinder, and more particularly, to a compressor in which oil supply is not required in each compression stage and lubricating oil is not mixed into gas after passing through a final compression stage, an LNG ship equipped with the compressor, a compression cylinder in which lubricating oil is not mixed into gas compressed without oil supply, and a compression cylinder in which a load applied to a rod seal for sealing an outer periphery of a rod is small.
Background
Conventionally, compressors have been used to compress various gases. For example, natural gas is cooled to a temperature of-162 ℃ or lower to be delivered as Liquefied Natural Gas (LNG), but a compressor is used to compress boil-off gas generated from the liquefied natural gas and to use the boil-off gas as a fuel source for driving an internal combustion engine for LNG ship propulsion. Patent document 1 describes a compressor that compresses an evaporation gas.
Patent document 1 describes a cylinder that compresses gas supplied to a cylindrical cylinder tube. A cylindrical cylinder liner is disposed in the cylinder tube, and a cylindrical piston having a piston ring and a guide ring is slidably disposed in the cylinder liner. The supplied gas is compressed by the reciprocating movement of the piston. The compressed gas is sent out from the discharge port.
The gas compression is performed on, for example, natural gas (300 bar) for internal combustion engine fuel, which is boil-off gas evaporated from liquefied natural gas, hydrogen (200 bar) for diesel fuel desulfurization equipment, CNG fuel (240 bar), and methane gas (240 bar) for automobiles.
Patent document 2 describes a reciprocating compressor. In such a reciprocating compressor, a supplied gas is compressed by a compression cylinder in which a cylindrical piston is slidably disposed in a cylindrical cylinder tube.
Documents of the prior art
Patent document
Patent document 1: japanese Kokai publication 2008-528882
Patent document 2: japanese laid-open patent publication No. 2017-026044
Disclosure of Invention
The compressor comprises one or more compression stages each having a cylinder, and the gas is compressed in steps at each compression stage to be gradually pressurized. If the number of compression stages is increased, the gas can be further pressurized.
When the number of compression stages increases, it is necessary to supply lubricating oil to the piston in the subsequent compression stage in order to further compress the gas that has already become high pressure. Therefore, the lubricating oil is mixed into the gas after passing through the final compression stage. The cylinder of the latter compression stage cannot be of the oil-less type because the resin seal ring is shortened in life due to high heat.
Accordingly, an object of the present invention is to provide a compressor in which oil supply is not required in each compression stage and lubricating oil is not mixed into gas after passing through a final compression stage, and an LNG carrier equipped with the compressor.
Further, the cylinder may be used to further increase the pressure of the gas to be pressurized. At present, it is necessary to supply lubricating oil to the compression cylinder for high pressure above a certain limit. The reason why the lubricating oil must be supplied is that the resin piston ring and guide ring constituting the piston are exposed to high heat, and the life of the piston is shortened.
The lubricating oil supplied to the compression cylinder is mixed into the gas having a high pressure. If lubricating oil is mixed into the high-pressure gas, the LNG reliquefier which operates at a very low temperature may malfunction in the case of the LNG compressor, the life of an expensive catalyst may be shortened by the amount of oil in the diesel desulfurization facility, and peripheral components of the engine may malfunction in the CNG vehicle.
Accordingly, an object of the present invention is to provide a compression cylinder in which oil supply is not required and lubricating oil is not mixed into compressed gas.
Further, in the cylinder tube, the internal pressure largely pulsates between the suction pressure and the compression pressure due to the movement of the piston. The pressure pulsation is also applied to a rod packing that seals the outer periphery of the rod, and a large load due to vibration, impact, and sliding friction heat is applied to the rod packing, thereby shortening the life thereof.
Accordingly, an object of the present invention is to provide a compression cylinder in which a small load is applied to a rod seal for sealing an outer periphery of a rod.
Other problems of the present invention will be apparent from the following description.
The above problems are solved by the following inventions.
1.
A compressor that compresses a gas supplied from a suction port in one or more compression stages and then discharges the compressed gas from a discharge port, the compressor characterized by:
the cylinders of the one or more compression stages do not require oil supply in all compression stages,
at least the cylinders of the final compression stage are cooled by the return flow of the coolant in the flow path provided in the cylinder liner.
2.
A compressor that compresses a gas supplied from a suction port in one or more compression stages and then discharges the compressed gas from a discharge port, the compressor characterized by:
the cylinders of the one or more compression stages do not require oil supply in all compression stages,
cooling at least the cylinder of the final compression stage by a return flow of the cooling liquid in a flow path provided in the piston rod.
3.
A compressor that compresses a gas supplied from a suction port in one or more compression stages and then discharges the compressed gas from a discharge port, the compressor characterized by:
the cylinders of the one or more compression stages do not require oil supply in all compression stages,
the cylinders of at least the final compression stage are cooled by the return flow of the cooling liquid in the flow path provided between the cylinder bore and the cylinder liner.
4.
The compressor according to 1, 2 or 3, wherein the coolant is clean water, oil or a low-temperature coolant of 0 ℃ or lower.
5.
The compressor according to any one of 1 to 4, wherein the compression stage is 3 stages or more.
6.
In the compressor according to any one of claims 1 to 5, the gas after passing through the final compression stage is pressurized to 200 bar or more.
7.
In the compressor of said 6, the gas after passing through a compression stage preceding the final compression stage is pressurized to 100 to 120 bar.
8.
In the compressor according to any one of claims 1 to 7, the one or more compression stages are driven by a horizontally opposed crank drive mechanism.
9.
An LNG ship, comprising:
the compressor according to any one of 1 to 8; and
a reliquefaction device disposed between the suction port and the discharge port to convert the gas into a liquid,
the boil-off gas of the liquefied natural gas stored in the LNG tank is compressed by the compressor to obtain fuel for the propulsion combustion engine, and the unused fuel is re-liquefied by the re-liquefying device and returned to the LNG tank.
10.
A compression cylinder which includes a cylinder tube, a cylinder liner disposed in the cylinder tube, and a piston slidably disposed in the cylinder liner, and which compresses a gas supplied from an intake port and discharges the compressed gas from a discharge port, the compression cylinder being characterized in that:
a flow path is provided in the cylinder liner, and the cylinder tube, the cylinder liner, and the piston are cooled by causing a coolant to flow back in the flow path.
11.
A compression cylinder which includes a cylinder tube and a piston slidably disposed in the cylinder tube, and which compresses a gas supplied from a suction port and discharges the compressed gas from a discharge port, the compression cylinder being characterized in that:
a flow path is provided in the piston, and the cylinder tube and the piston are cooled by causing a coolant to flow back through the flow path.
12.
A compression cylinder which includes a cylinder tube, a cylinder liner disposed in the cylinder tube, and a piston slidably disposed in the cylinder liner, and which compresses a gas supplied from an intake port and discharges the compressed gas from a discharge port, the compression cylinder being characterized in that:
a flow path is provided between the cylinder tube and the cylinder liner, and the cylinder tube and the piston are cooled by causing a coolant to flow back in the flow path.
13.
In the compression cylinder according to claim 10, 11 or 12, the coolant is clean water, oil or a low-temperature coolant of 0 ℃.
14.
In the compression cylinder according to any one of claims 10 to 13, a pressure of the gas supplied from the suction port or the gas discharged from the discharge port is 200 bar or more.
15.
A compression cylinder, comprising:
a cylinder barrel which is communicated with the suction inlet and the discharge outlet;
a piston disposed in the cylinder tube so as to be capable of sliding in close contact therewith;
a coupling shaft which is integrally connected to the piston coaxially, has a smaller diameter than the piston, and can slide closely in a coupling cylinder formed coaxially with the cylinder;
a rod connected to the connecting shaft and configured to transmit a driving force to the piston through the connecting shaft;
a stem seal sealing an outer periphery of the stem; and
a communication hole that communicates a space inside the coupling cylinder between a rear end portion of the coupling shaft and the rod seal with the outside,
the compression cylinder compresses the gas supplied from the suction port in the cylinder tube by the piston and then sends the compressed gas out from the discharge port.
16.
In the compression cylinder according to claim 15, a space in the coupling cylinder between the rear end portion of the coupling shaft and the rod seal communicates with the outside via the communication hole, and thus the pressure is lower than the pressure of the gas discharged from the discharge port and higher than the atmospheric pressure.
17.
In the compression cylinder of the 15 or 16, the rod seal does not need to be supplied with lubricating oil.
18.
In the compression cylinder according to claim 15, 16 or 17, a piston ring is attached to an outer peripheral surface of the connecting shaft, and an outer peripheral portion of the piston ring slides in close contact with an inner peripheral surface of the connecting cylinder.
19.
In the compression cylinder according to any one of claims 15 to 18, a cylindrical cylinder liner is attached to the cylinder tube,
a piston ring and a guide ring are attached to an outer peripheral surface of the piston, and outer peripheral portions of the piston ring and the guide ring slide in close contact with an inner peripheral surface of the cylinder liner.
20.
The compression cylinder according to any one of claims 15 to 19, wherein the compression cylinder is used so that the gas is 200 bar or more.
21.
A compression cylinder, comprising:
a cylinder barrel which is communicated with the suction inlet and the discharge outlet;
a piston which is disposed in the cylinder tube so as to be capable of sliding in close contact therewith, compresses gas sucked from the suction port, and discharges the compressed gas from the discharge port;
a rod that transmits a driving force to the piston; and
a stem seal sealing an outer periphery of the stem,
the rod seal includes a plurality of rod seal rings arranged around the rod in an axial direction of the rod, and a pressure at a middle portion in the axial direction is lower than a pressure of gas discharged from the discharge port and higher than atmospheric pressure.
22.
In the compression cylinder described in the above 21, the rod seal connects the gap between the rod seal rings to a space that is lower in pressure than the gas discharged from the discharge port and higher than atmospheric pressure via the communication hole at least 1 part in the axial direction.
23.
In the compression cylinder of the above 21 or 22, the rod seal does not need to be supplied with lubricating oil.
24.
In the compression cylinder according to 21, 22 or 23, a cylindrical cylinder liner is attached to the cylinder tube,
a piston ring and a guide ring are attached to an outer peripheral surface of the piston, and outer peripheral portions of the piston ring and the guide ring slide in close contact with an inner peripheral surface of the cylinder liner.
25.
The compression cylinder according to any one of claims 21 to 24, wherein the compression cylinder is used so that the gas is 200 bar or more.
Effects of the invention
According to the present invention, it is possible to provide a compressor in which oil supply is not required in each compression stage and lubricating oil is not mixed into gas after passing through the final compression stage, and an LNG carrier equipped with the compressor.
Further, according to the present invention, it is possible to provide a compression cylinder in which lubricating oil is not mixed into a gas to be compressed without requiring oil supply.
Further, according to the present invention, it is possible to provide a compression cylinder in which a load applied to a rod seal for sealing an outer periphery of a rod is small.
Drawings
Fig. 1 is a block diagram schematically showing an embodiment of a compressor according to the present invention.
Fig. 2 is a sectional view showing the structure of a compression cylinder (embodiment 1) of the present invention.
Fig. 3 is a longitudinal sectional view (a-a section in fig. 2) showing the shape of a gasket of the compression cylinder shown in fig. 2.
Fig. 4 is a longitudinal sectional view (section B-B in fig. 2) showing the shape of the cylinder liner of the compression cylinder shown in fig. 2.
Fig. 5 is a longitudinal sectional view (section C-C in fig. 2) showing the shape of the cylinder liner of the compression cylinder shown in fig. 2.
Fig. 6 is a vertical cross-sectional view showing the structure of the piston and the piston rod of the compression cylinder (embodiment 2).
Fig. 7 is a view showing the shape of the support ring of the cylinder shown in fig. 6, i.e., the compression cylinder of the present invention, wherein (a) is a vertical sectional view and (b) is a plan view.
Fig. 8 is a sectional view showing the structure of a compression cylinder (embodiment 3) of the present invention.
Fig. 9 is a cross-sectional view showing the shape of a flow path of the coolant in the compression cylinder shown in fig. 8.
Fig. 10 is a perspective view showing the shape of a flow path of the coolant in the compression cylinder shown in fig. 8.
Fig. 11 is a vertical sectional view showing the structure of a rod seal of a compression cylinder of the present invention, which is the cylinder shown in fig. 2, 6, and 8.
Fig. 12 is a sectional view showing the structure of a compression cylinder (embodiment 4) of the present invention.
Fig. 13 is a side view showing the structure of a piston of a compression cylinder (embodiment 4) of the present invention.
Fig. 14 is a sectional view showing the structure of a compression cylinder (embodiment 5) of the present invention.
Fig. 15 is a vertical sectional view showing the structure of a rod seal of a compression cylinder (embodiment 5) of the present invention.
Fig. 16 is a block diagram schematically showing a compressor configured by using the compression cylinder of the present invention.
Fig. 17 is an external perspective view of the compressor.
Fig. 18 is a sectional view of the compressor.
Description of the reference numerals
1 compressor
3 suction inlet
4 natural gas
7 discharge port
9 1 st compression stage
10 nd 2 compression stage
11. 12, 16, 17, 18 cylinders (compression cylinder)
13 3 rd compression stage
14 th 4 compression stage
15 th 5 compression stage
28 horizontal opposite crank driving mechanism
31 reliquefaction device
33 piston
34 cylinder barrel
35 cylinder jacket
36 piston ring
37 piston rod (rod)
38 annular groove
39 communication path
40 peripheral flow path
42a, 42b outer coolant passages
43 flow path
46 cooling liquid inlet
47 liquid coolant inlet
48 cooling liquid flow path
50 outlet for cooling liquid
51 coolant flow outlet
52 cooling fluid flow path
65 piston cover
70 rod seal
71 annular spacer
72 connecting shaft
73 piston ring
75 connecting tube
76 communication hole
Detailed Description
The compressor of the invention gradually compresses gas to high pressure in each of a plurality of compression stages, and oil supply to the piston is not needed in all the compression stages. The LNG ship of the present invention includes the compressor of the present invention, and sails by the propulsive force of the combustion engine using the natural gas compressed by the compressor as fuel.
In embodiments 1 to 3, the compression cylinder of the present invention is a cylinder constituting each compression stage of the compressor of the present invention, and oil supply to the piston is not required.
In embodiments 4 and 5, the compression cylinder according to the present invention reduces the load applied to the rod seal that seals the outer periphery of the piston rod, and does not require oil to be supplied to the rod seal. In the compression cylinders according to embodiments 4 and 5, the piston ring and the guide ring are formed of a material having high heat resistance, or the structure according to any one of embodiments 1 to 3 is combined, so that oil supply to the piston is not required.
The present inventors have made intensive studies on a compressor, an LNG ship, and a compression cylinder in order to eliminate the need to supply a lubricating oil to a piston or the like, and have completed the above inventions. If lubricating oil is supplied to the piston or the like, oil is mixed into the natural gas, and the natural gas cannot be liquefied again and returned to the storage tank. This is due to the contamination of the natural gas in the storage tank with oil.
The above embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
(compressor embodiment)
In this embodiment, the compressor of the present invention includes one or more (e.g., 5) compression stages each having a cylinder (compression cylinder), and the gas is gradually compressed to be gradually increased in pressure in each compression stage. In the subsequent compression stage (e.g. 4 th stage) of the plurality of compression stages, the gas is already at a high pressure above 100 bar (10 MPa).
In a cylinder that further compresses a high-pressure gas of 100 bar (10MPa) or more, resin seal rings (piston rings and rod seal rings) may have a shortened life due to high heat. The resin seal ring can maintain its useful life even in a non-oil supply type device under low pressure. However, under the conditions that the suction pressure is 100 to 120 bar and the discharge pressure is 200 bar or more as in the following (for example, 5 th stage) compression stage, the practical life of the resin seal ring may not be maintained in the oil-less type apparatus.
In the compressor of the present invention, a flow path is provided at least in the cylinder of the final compression stage, and cooling is performed by causing the cooling liquid to flow back in the flow path, so that oil supply to the piston is not required in all the compression stages.
Therefore, in this compressor, there is no possibility that the compressed gas is contaminated with the lubricating oil. Therefore, not only the gas after passing through the subsequent compression stage but also the gas after any compression stage can be re-liquefied and reused at extremely low temperature and high pressure. The compressor can be applied to all uses, for example, in the case of using the compressor in a ship, compressed natural gas can be returned to a storage tank as cargo.
Fig. 1 is a block diagram schematically showing an embodiment of a compressor according to the present invention.
As shown in fig. 1, the compressor 1 of the present embodiment compresses a boil-off gas 6 (natural gas 4) generated from a liquefied natural gas Ef. The compressor 1 pressurizes the natural gas 4 taken in to 100 bar (10MPa) to 500 bar (50MPa), in most cases 150 bar (15MPa) to 300 bar (30 MPa). The natural gas 4 is used as a fuel for a combustion engine such as a diesel engine.
In the compressor 1 of the present embodiment, fuel for a propulsion combustion engine disposed on a ship, particularly on an LNG ship, can be obtained based on the boil-off gas 6 of the liquefied natural gas Ef stored in the LNG tank 5, for example. The boil-off gas 6 is at a pressure of 1 bar (100kPa) and about-162 c. The compressor 1 brings the boil-off gas 6 preferably into a natural gas 4 compressed to a feed pressure variable in the range of 100 bar (10MPa) to 500 bar (50MPa), in particular into a natural gas 4 compressed to a feed pressure in the range of 150 bar (15MPa) to 300 bar (30 MPa). When the amount of the boil-off gas 6 is insufficient as the fuel source, a part of the liquefied natural gas Ef in the LNG tank 5 is heated and vaporized.
Further, in this embodiment, the gas after passing through the final compression stage is pressurized to 200 bar or more, but may be 150 bar (15MPa) to 300 bar (30MPa) depending on the load of the supplied side. Depending on the rated pressure, it may be 150 bar (15MPa) to 400 bar (40MPa) or more.
The compressor 1 includes a suction inlet 3 for natural gas 4. Further, the compressor 1 includes an outlet 7 communicating with a natural gas supply pipe 8 for a combustion engine disposed downstream.
The suction port 3 communicates with the LNG tank 5. The liquefied natural gas Ef is stored in the LNG storage tank 5 at a pressure of 1 bar (100kPa) and a temperature of-162 ℃. The boil-off gas 6 is generated from the surface portion of the liquefied natural gas Ef. The boil-off gas 6 is sucked in by the compressor 1 and compressed, preferably at a pressure of 150 bar (15MPa) to 300 bar (30MPa), and is delivered as natural gas 4 from the discharge opening 7.
The compressor 1 comprises 1 st to 5 th compression stages 9, 10, 13, 14, 15. Although the compression stage is 5 stages in this embodiment, the compression stage is not limited to 5 stages in the present invention. If a centrifugal compressor or a screw compressor is applied at the low-pressure stage, the number of stages can also be reduced from 5 stages to 2 or 3 stages, for example.
The 1 st to 5 th compression stages 9, 10, 13, 14, 15 have piston ring seal-type cylinders (hereinafter also simply referred to as cylinders) 11, 12, 16, 17, 18 connected in series. The piston ring seal type cylinder 11 can reliably suck and compress the natural gas 4 in a wide temperature range where the suction gas temperature is-162 ℃ to +45 ℃.
The cylinders 11, 12, 16, 17 of the 1 st to 4 th stages have double-acting cylinders in which both sides of a piston are compression chambers for natural gas compression, and the 5 th-stage cylinder 18 has a single-acting cylinder in which only one side of a piston is a compression chamber. The natural gas 4 passes through these compression stages 9, 10, 13, 14, 15 and is then discharged from the discharge opening 7.
Conventionally, since the high-pressure compression stage as the subsequent stage is of the oil supply type, there is a possibility that the natural gas is contaminated with the lubricating oil. When natural gas is re-liquefied at extremely low temperature and high pressure, lubricating oil is mixed into the natural gas, which may cause a failure of the re-liquefaction apparatus. The lubricating oil mixed into the natural gas is removed by the oil separator and the oil filter. However, since complete removal is impossible, failure of the reliquefaction device cannot be avoided. Therefore, in order to prevent the lubricating oil in the gas after the 5 th stage from being further sent to the preceding stage through the bypasses 20e, 20d, 20c, 20b, and 20a provided in the respective stages in consideration of liquefying the high-pressure gas after the 4 th stage, in the conventional compressor, a check valve must be provided in front of the compression stage of the subsequent stage (between the 4 th stage 14 and the 5 th stage 15). Since the 5 th stage 15, which is the final stage, is of the oil supply type and is bypassed and returned from the 5 th stage to the previous stage, which is necessary for operation such as capacity adjustment, the low-pressure stage gas before the 5 th stage may be contaminated with a very small amount of lubricating oil. If the rear stage compression stage is of the oil-free type and all the stages are of the oil-free type, it is extremely advantageous that the reliquefaction device is prevented from malfunctioning when reliquefying the gas in all the compressors not limited to the ship compressor. In addition, a check valve preceding the compression stage of the subsequent stage (between the 4 th stage 14 and the 5 th stage 15) is not required.
A reliquefaction device 31 for liquefying the compressed residual natural gas 4 unnecessary for the engine is usually provided after the 4 th compression stage 14 or the 5 th compression stage 15.
Preferably, any or all of the compression stages 9, 10, 13, 14, 15 have a bypass 20a, 20b, 20c, 20d, 20e for returning the natural gas 4 after passing through the respective compression stage 9, 10, 13, 14, 15 to the front (upstream) of the compression stage 9, 10, 13, 14, 15. Preferably, each bypass 20a, 20b, 20c, 20d, 20e has a control valve 24a, 24b, 24c, 24d, 24e controlled by the compressor control system 23. By controlling the valves 24a, 24b, 24c, 24d, and 24e, at least one of the pressure and the feed amount of the natural gas 4 at the discharge port 7 can be adjusted.
The natural gas 4 returns via the bypasses 20a, 20b, 20c, 20d, 20e, and the natural gas 4 at the discharge port 7 becomes the desired target pressure Pset. The reverse flow through the bypasses 20a, 20b, 20c, 20d, 20e is controlled by the control valves 24a, 24b, 24c, 24d, 24 e. The feed pressure at the discharge opening 7 is variable in the range of 100 bar (10MPa) to 500 bar (50MPa), typically in the range of 150 bar (15MPa) to 300 bar (30MPa) depending on the operating conditions. In addition, the desired flow rate of the natural gas 4 is variable in the range of 0% to 100%. The compressor 1 makes the pressure at the discharge side at the discharge port 7a variable feed pressure specified by a control input value.
In the present embodiment, since the cylinders 11, 12, 16, 17, 18 of all the compression stages 9, 10, 13, 14, 15 do not need to be supplied with oil to the pistons, the natural gas 4 compressed in these compression stages 9, 10, 13, 14, 15 is not contaminated with impurities. Since the natural gas 4 compressed in each compression stage 9, 10, 13, 14, 15 is not contaminated, unused natural gas 4 can be returned to the LNG storage tank 5 as cargo if necessary.
(embodiment of LNG ship)
The LNG ship according to the present invention includes the compressor 1 described above, and is an LNG ship equipped with a combustion engine (for example, a diesel engine) using the natural gas 4 compressed by the compressor 1 as fuel. In the LNG ship, the combustion engine is mainly used for propulsion, and the power generated by the combustion engine is used as propulsion power to sail the ship.
In this LNG ship, the boil-off gas 6 of the liquefied natural gas Ef stored in the LNG tank 5 is compressed by the compressor 1, whereby fuel for the propulsion combustion engine can be obtained, and the unused fuel can be re-liquefied by the reliquefier 31 and returned to the LNG tank 5 as cargo. Therefore, the LNG ship can minimize the amount of decrease in the liquefied natural gas Ef in the LNG tank 5 while effectively utilizing the boil-off gas 6, and is extremely useful in a sailing environment where the combustion engine fuel and the liquefied natural gas Ef cannot be supplied from the outside.
(embodiment 1 of the Cylinder)
Fig. 2 is a sectional view showing a structure of a compression cylinder (embodiment 1) of the present invention, which is a cylinder of the compressor.
As shown in fig. 2, the cylinders (compression cylinders) 11, 12, 16, 17, and 18 of the present embodiment include a cylinder tube 34, a cylinder liner 35 disposed in the cylinder tube 34, and a piston 33 slidably disposed in the cylinder liner 35, and compress gas supplied from an intake port 63 through an intake valve 63a and send the compressed gas out of a discharge port 64 through a discharge valve 64a (fig. 2 shows the 5 th-stage cylinder 18).
The cylinder tube 34 is formed in a tubular shape, and a cylindrical cylinder liner 35 is fitted therein. The piston 33 is formed in a cylindrical shape capable of being fitted in the cylinder liner 35. A ring-shaped piston ring 36 and a guide ring 36a are fitted to the outside of the piston 33. The piston rod 37 is coaxially coupled to the piston 33, and the piston 33 is reciprocated in the axial direction by reciprocating the piston rod 37 by a motor. The piston 33 slides in the cylinder liner 35 in the axial direction of the cylinder tube 34, whereby the gas in the cylinder tube 34 (in the cylinder liner 35) is compressed. The high-pressure cylinder tube is usually small in diameter, and therefore the piston 33 and the piston rod 37 are formed as an integral structure, but they may be formed as separate structures depending on the case. A rod seal 70 is provided on the outer periphery of the piston rod 37.
In the cylinder tube 34, gas compression heat and sliding friction heat between a piston ring 36 and a guide ring 36a fitted to the piston 33 and the cylinder liner 35 are generated. The heat of gas compression is substantially constant regardless of the pressure level. However, the sliding frictional heat of the piston ring 36 and the cylinder liner 35 increases as the pressure increases. This is because the surface pressure between the piston ring 36 and the cylinder liner 35 is the same as in the oil-fed type, but the friction coefficient between the piston ring 36 and the cylinder liner 35 increases in the absence of the lubricating oil. The sliding friction heat generated by the guide ring 36a is independent of the pressure, but if the oil-less type is adopted, the friction coefficient between the guide ring 36a and the cylinder liner 35 increases and increases similarly to the piston ring. If the piston ring 36 and the guide ring 36a are in a melt-worn state due to an increase in temperature caused by sliding frictional heat, the life of the piston ring 36 and the guide ring 36a is shortened. If the sliding frictional heat of the piston ring 36 is removed, the life of the piston ring 36 and the guide ring 36a can be extended without supplying oil to the piston.
In the compression cylinder (high-pressure non-fueled cylinder) 18, a structure is formed to actively remove the sliding frictional heat of the piston ring 36 and the guide ring 36a in a high-pressure non-fueled state, and the life of the piston ring 36 and the guide ring 36a is extended. By providing the cooling mechanism, sliding friction heat is positively removed, and temperature rise of the piston ring 36 and the guide ring 36a is suppressed.
Since the compression cylinder (high-pressure non-fueled cylinder) 18 is provided with a cooling mechanism for removing frictional heat, the cooling mechanism for supplying oil to the piston is not required, and the inside of the cylinder liner 35 is cooled by forming a coolant passage 55 in the cylinder liner 35 inserted into the cylinder tube 34 with a slight fitting margin. The cylinder liner 35 is made of stainless steel or steel, has a thickness of about 15mm, and is provided with a coolant passage 55 by machining. The rear end portion (left end in fig. 2) of the coolant passage 55 is closed by welding the rear end portion 56 of the cylinder liner 35.
The front end (right end in fig. 2) of the cylinder tube 34 is closed by a cylinder head 57.
Fig. 3 is a longitudinal sectional view (a-a section in fig. 2) showing the shape of a gasket of the compression cylinder shown in fig. 2.
In order to prevent leakage of the high-pressure gas and the coolant, the contact surface between the cylinder head 57 and the cylinder liner 35 is sealed by a gasket 58 made of pure iron. As shown in fig. 3 (a-a cross-sectional view in fig. 2), an upper coolant passage 60 and a lower coolant passage 61 having a semicircular arc shape are formed in the contact surface portion of the gasket 58 with the cylinder head 57.
Fig. 4 is a longitudinal sectional view (section B-B in fig. 2) showing the shape of the cylinder liner of the compression cylinder shown in fig. 2.
As shown in fig. 4 (a cross-sectional view B-B in fig. 2), in the cylinder liner 35, a coolant passage 55 including 24 circular holes based on the cylinder bore diameter is formed along the axial direction of the cylinder liner 35. The circular holes may be long holes, and the number of the circular holes may not be 24.
As also shown in fig. 4, the cylinder tube 34 is provided with an outer peripheral flow path 40. The outer peripheral flow path 40 communicates from one end side surface 41 to the other end side surface 42 of the cylinder tube 34. The outer circumferential flow path 40 is provided on the outer circumferential side of the cylinder liner 35, has a plurality of straight pipe shapes, and is a normal cylinder coolant path provided in the high-pressure cylinder. The coolant flows through the outer peripheral flow path 40. The coolant flows through the outer circumferential flow path 40 from the side surface 41 and then flows out from the side surface 42.
The cylinder liner 35 is cooled by the coolant flowing through the outer circumferential flow path 40, and absorbs heat of the piston rings 36 and the guide rings 36a, and radiates heat to the outside of the cylinder tube 34, thereby lowering the temperature of the rings.
Fig. 5 is a longitudinal sectional view (section C-C in fig. 2) showing the shape of the cylinder liner of the compression cylinder shown in fig. 2.
In order to prevent wear of the piston ring 36, the guide ring 36a, and the cylinder liner 35, the sliding surfaces of the cylinder liner 35 and the piston ring 36 and the guide ring 36a are nitrided or sprayed with tungsten carbide. The cylinder head 57 is equipped with an O-ring 59 for gas sealing at its insertion into the cylinder barrel 34. On the base end side (left side in fig. 2) of the cylinder liner 35, a coolant communication passage 62 is formed substantially all around the inside of the cylinder liner 35 as shown in fig. 5 (cross-sectional view C-C in fig. 2).
The coolant is supplied from a lower coolant passage 61a of the cylinder head 57 on the lower side in fig. 2. The coolant enters the lower half of the cylinder liner 35 from the lower side coolant passage 61 through the through-holes formed in the gasket 58. The coolant that has entered the cylinder liner 35 flows toward the base end side (left side in fig. 2) within the cylinder liner 35. The coolant passing through the lower half of the cylinder liner 35 is diverted at the base end side of the cylinder liner 35, and moves toward the upper half of the cylinder liner 35 through the coolant communication passage 62. The coolant that has moved to the upper half of the cylinder liner 35 flows toward the top end side (right side in fig. 2), and finally returns to the coolant supply device through the upper coolant passage 60a located at the upper portion of the cylinder head 57.
As the coolant, clean water at a cooling temperature corresponding to the compression pressure is generally used, but if a low-temperature coolant of 0 ℃ or lower, for example, an ethylene glycol aqueous solution, is used as necessary, the cooling effect can be increased. Although the cooling effect is slightly poor, oil cooling can be used.
The coolant flowing back through the coolant passage 55 absorbs heat of the piston 33, the piston rings 36, the guide ring 36a, the cylinder tube 34, and the cylinder liner 35, and dissipates heat to the outside of the cylinder tube 34, thereby cooling the inside of the cylinder tube 34. By providing such a cooling mechanism, the compression cylinder (high-pressure non-fuel-supply cylinder) 18 does not need to be supplied with fuel. In the compression cylinder (high-pressure non-fueled cylinder) 18, the temperature conditions of the piston ring 36 and the guide ring 36a are the same as those of the low-pressure non-fueled cylinder, and therefore, the life of the piston ring 36 and the guide ring 36a is extended.
A heat transfer area of such a degree that the temperature of the piston ring 36 and the guide ring 36a can be substantially removed by the cooling mechanism can be ensured. Therefore, since only the gas compression heat which is almost the same as that in the case of the oil supply type remains, the gas can be pressurized to a high pressure in the oil-non-supply state.
In the compressor using the compression cylinder (high-pressure non-oil-supply cylinder) 18, since oil supply to the piston is not required in all compression stages, the gas is not contaminated with impurities, and the unused gas can be returned to the reservoir. In addition, the gas circulated in each compression stage can be finally returned to the storage tank.
This cooling mechanism can achieve reliable fitting of the cylinder tube 34 and the cylinder liner 35, as compared with the later-described embodiment (fig. 8 to 10) in which the outer peripheral side of the cylinder liner 35 is cooled.
(embodiment 2 of the cylinder)
Fig. 6 is a vertical sectional view showing the structure of a piston and a piston rod of a compression cylinder (embodiment 2) of the present invention, which is a cylinder of the compressor.
In the cylinder (compression cylinder 18) of the present embodiment, instead of or in addition to the cooling mechanism shown in fig. 2 to 5, a flow path 43 is provided in the piston rod 37 as shown in fig. 6, and the cooling liquid is cooled by being returned in the flow path 43. The flow path 43 is formed along the axial direction of the piston rod 37 from the distal end side to the proximal end side of the piston 33 and the piston rod 37. The inside of the flow path 43 is divided into a center portion 43a and an outer peripheral portion 43b by a cylindrical body 44 disposed in the flow path 43. A support ring 45 is fitted between the distal end side portion of the cylinder 44 and the inner wall portion of the flow path 43. Further, the cylinder tube for high pressure is generally small in diameter, and therefore the piston 33 and the piston rod 37 are formed in an integral structure, but they may be formed in a separate structure depending on the case.
Fig. 7 is a view showing the shape of the support ring of the cylinder shown in fig. 6, i.e., the compression cylinder of the present invention, wherein (a) is a vertical sectional view and (b) is a plan view.
As shown in fig. 6 and 7, a plurality of insertion holes 49 through which the cooling liquid flows are formed in the support ring 45 in the axial direction.
The coolant after passing through the coolant flow path 48 from the coolant flow inlet 47 provided in the cylinder tube 34 flows into the flow path 43 in the piston rod 37. The coolant having passed through the coolant flow path (flexible tube) 48 flows into the center portion 43a in the cylinder 44 through the coolant inlet 46 provided on the proximal end side of the piston rod 37. The coolant in the central portion 43a flows toward the distal end side of the piston rod 37, and reaches the outer peripheral portion 43b through a plurality of through holes 44a provided on the distal end side of the cylinder 44. The coolant in the outer peripheral portion 43b flows toward the base end side of the piston rod 37 through the insertion hole 49 of the support ring 45. The coolant on the base end side of the piston rod 37 flows out of the piston rod 37 through a coolant outlet 50 provided on the base end side of the piston rod 37. The coolant flowing out from the piston rod 37 flows out from the coolant outlet 51 through a coolant flow path (flexible tube) 52 provided in the cylinder tube 34.
One end of the cylinder 44 is fixed in a guide hole provided in the piston rod 37, and the other end of the cylinder 44 is fixed in a guide hole provided in the piston cover 65, and vibration is not generated during the reciprocation of the piston 33. If the inner diameter of the support ring 45 is adjusted relative to the outer diameter of the cylinder 44, the cylinder 44 is prevented from vibrating.
The coolant that flows back through the piston rod 37 absorbs heat of the piston 33, the piston rings 36, the guide rings 36a, the cylinder tube 34, and the cylinder liner 35, and dissipates heat to the outside of the cylinder tube 34, thereby cooling the piston rings 36 and the guide rings 36 a. By providing such a cooling mechanism, oil supply is not required in the compression cylinder (high-pressure non-oil-supply cylinder) 18.
A heat transfer area of such a degree that the temperature of the piston ring 36 and the guide ring 36a can be substantially removed by the cooling mechanism can be ensured. Therefore, since only the gas compression heat which is almost the same as that in the case of the oil supply type remains, the gas can be pressurized to a high pressure in the oil-non-supply state.
As shown in fig. 6, a rod seal 70 is provided on the outer periphery of the piston rod 37.
(embodiment 3 of the Cylinder)
Fig. 8 is a sectional view showing the structure of a compression cylinder (embodiment 3) of the present invention, which is a cylinder of the compressor.
The cylinder (compression cylinder 18) of the present embodiment may be configured such that the piston rings 36 and the guide rings 36a are cooled by circulating the coolant between the cylinder tube 34 and the cylinder liner 35 as shown in fig. 8, instead of or in addition to the cooling mechanism shown in fig. 2 to 5. In order to circulate the coolant around the outer periphery of the cylinder liner 35 to achieve uniform cooling and increase the cooling area to improve the cooling effect, a plurality of annular grooves 38 having semicircular cross sections are provided on the outer periphery of the cylinder liner 35. O- rings 41a and 41b for preventing leakage of the coolant are inserted in front and rear of the annular groove 38, and leakage of the high-pressure gas to the coolant side is prevented by both the fitting margin and the O- rings 41a and 41 b.
Fig. 9 is a cross-sectional view showing the shape of a flow path of the coolant in the compression cylinder shown in fig. 8.
Fig. 10 is a perspective view showing the shape of a flow path of the coolant in the compression cylinder shown in fig. 8.
As shown in fig. 9, the coolant is supplied from the outer coolant passage 42a of the side surface 41 of the cylinder tube 34, flows through the annular groove 38 located on the back surface of the cylinder liner 35 as shown in fig. 10, is discharged from the outer coolant passage 42b of the other side surface 42 of the cylinder tube 34 as shown in fig. 9, and returns to the cooling circuit of the coolant recovery line, and the sliding friction heat between the piston ring 36 and the cylinder liner 35 and the sliding friction heat between the guide ring 36a and the cylinder liner 35 and the gas compression heat in the cylinder are effectively removed in the vicinity of the heat generation source. As shown in fig. 10, the annular groove 38 communicates from one end side to the other end side of the cylinder tube 34 via a communication passage 39.
As also shown in fig. 9, an outer peripheral flow path 40 is provided in the cylinder tube 34. The outer peripheral flow path 40 communicates from one end side surface 41 to the other end side surface 42 of the cylinder tube 34. The outer circumferential flow path 40 is provided on the outer circumferential side of the cylinder liner 35, is in the shape of a plurality of straight pipes located outside the annular groove 38, and is a normal cylinder coolant path provided in the high-pressure cylinder. The outer peripheral flow path 40 increases the cooling effect of the cylinder tube 34 together with the annular groove 38.
The coolant flows back through the annular groove 38 and the outer peripheral flow path 40. As shown in fig. 9, the outer coolant passage 42a of the side surface 41 communicates with the annular groove 38. The outer coolant passage 42b of the side surface 42 communicates with the annular groove 38. The coolant flows into the annular groove 38 from the side surface 41, flows back into the annular groove 38 and the outer circumferential flow path 40, and then flows out from the side surface 42.
The coolant flowing back through the annular groove 38 and the outer circumferential flow path 40 cools the cylinder liner 35, absorbs heat from the piston rings 36 and the guide rings 36a, and dissipates the heat to the outer surface of the cylinder tube 34, thereby reducing the temperature of the rings and extending the life of the rings. By providing such a cooling mechanism, oil supply is not required in the cylinder (compression cylinder 18).
The heat transfer area of the inner wall of the annular groove 38 differs depending on the cylinder diameter and the cylinder length, and also depends on the coolant used, but a heat transfer area of such a degree that the temperature of the piston ring 36 and the guide ring 36a can be substantially removed by the cooling mechanism to remove the frictional heat can be secured. Therefore, since only the gas compression heat which is almost the same as that in the case of the oil supply type remains, the gas can be pressurized to a high pressure in the oil-non-supply state.
(construction of shaft seal)
Fig. 11 is a vertical sectional view showing the structure of a rod seal of a compression cylinder of the present invention, which is the cylinder shown in fig. 2, 6, and 8.
As shown in fig. 11, the rod seal 70 includes a plurality of rod seal rings 53 that support the outer periphery of the piston rod 37, and a plurality of ring cups 54 that house the rod seal rings 53. Sliding friction heat is also generated by the sliding of the rod seal ring 53 and the piston rod 37. The sliding frictional heat is transmitted to the ring cup 54 that houses the rod seal ring 53.
The rod seal 70 may be configured to have a cooling mechanism of a direct cooling method: the coolant (clean water or oil) is distributed and supplied from the coolant supply passage 66 communicating with the outside at the coolant supply port 68 to the flow passages in the respective ring cups 54, and the coolant is collected and discharged from these flow passages to the coolant discharge passage 67 communicating with the outside at the coolant discharge port 69. Further, by increasing the cooling effect by using a low-temperature cooling liquid (for example, a low-temperature ethylene glycol aqueous solution), by making the coolant flow path as close to the ring as possible, or by increasing the coolant flow path area, a large amount of sliding friction heat can be removed.
(Cylinder 4 th embodiment)
Fig. 12 is a sectional view showing the structure of a compression cylinder (embodiment 4) of the present invention.
As shown in fig. 12, the compression cylinder of the present embodiment includes: the cylinder 34, the cylinder liner 35 disposed in the cylinder 34, and the piston 33 slidably disposed in the cylinder liner 35 are configured such that gas supplied from the intake port 63 through the intake valve 63a is compressed by the piston 33 in the cylinder 34, and then is discharged from the discharge port 64 through the discharge valve 64 a.
The cylinder tube 34 is formed in a tubular shape, and a cylindrical cylinder liner 35 is fitted therein. Further, if the inner surface portion of the cylinder tube 34 has sufficient strength and durability, the cylinder liner 35 may not be provided. The cylinder tube 34 communicates with the suction port 63 and the discharge port 64 on the rear end side (left end side in fig. 12). Further, a front end portion (right end portion in fig. 12) of the cylinder tube 34 is closed by a cylinder head 57. The space in the cylinder tube 34 between the front end portion (right end portion in fig. 12) 33a of the piston 33 and the cylinder head 57 communicates with the outside (gas suction side) via the communication hole 34 a.
Fig. 13 is a side view showing the structure of a piston of a compression cylinder (embodiment 4) of the present invention.
As shown in fig. 13, the piston 33 is formed in a cylindrical shape capable of being fitted in the cylinder liner 35. A plurality of ring-shaped piston rings 36 are fitted around the piston 33. Further, a guide ring 36a is fitted to the outside of the front end side (right end side in fig. 12 and 13) and the base end side (left end side in fig. 12 and 13) of the piston 33. The outer peripheral portions of the piston ring 36 and the guide ring 36a closely slide on the inner peripheral surface of the cylinder liner 35. Further, if sufficient strength and durability are secured for the piston ring 36 and the guide ring 36a, various types of seal members may be used instead, and these seal members may not be provided, for example, as in a labyrinth seal.
The gas in the cylinder bore 34 (in the cylinder liner 35) is compressed by the piston 33 sliding in the cylinder liner 35 in the axial direction (arrow a in fig. 12) of the cylinder bore 34. The internal pressure greatly varies in the cylinder tube 34 (in the cylinder liner 35) depending on the direction of movement of the piston 33. When the moving direction of the piston 33 is a direction (right direction in fig. 12) in which the volume in the cylinder 34 increases, the pressure in the cylinder 34 decreases, and when the moving direction of the piston 33 is a direction (left direction in fig. 12) in which the volume in the cylinder 34 decreases, the pressure in the cylinder 34 increases. At this time, the gas in the cylinder tube 34 is compressed.
A coupling shaft 72 is coaxially and integrally connected to a base end portion (left end portion in fig. 12 and 13) 33b of the piston 33. The coupling shaft 72 is formed in a cylindrical shape having a smaller diameter than the piston 33. A ring-shaped piston ring 73 is fitted around the coupling shaft 72. The outer peripheral portion of the piston ring 73 closely slides on the inner peripheral surface of a connecting cylinder 75 coaxially formed in the cylinder tube 34. That is, the coupling shaft 72 can slide closely in the coupling cylinder 75.
A space (a space around the rod (piston rod) 37) in the coupling cylinder 75 between the rear end portion 74 of the coupling shaft 72 and the rod seal 70 communicates with the outside via a communication hole 76. Preferably, the space between the rear end portion 74 of the connecting shaft 72 and the rod seal 70 is communicated with the outside, so that the pressure is lower than the pressure of the gas discharged from the discharge port 64 and higher than the atmospheric pressure. In this case, the pressure can be set to such a pressure by communicating the communication hole 76 with the gas suction side. However, the refrigerant may be communicated with a discharge port of another compressor.
When the space between the rear end portion 74 of the coupling shaft 72 and the rod seal 70 is communicated with the outside (gas suction side) through the communication hole 76, the internal pressure of the space between the rear end portion 74 of the coupling shaft 72 and the rod seal 70 can be made equal to the suction pressure, fluctuations can be suppressed, the load applied to the rod seal 70 can be further reduced, and it is not necessary to supply lubricating oil between the rod (piston rod) 37 and the rod seal ring of the rod seal 70.
The close contact between the outer peripheral surface of the connecting shaft 72 and the inner peripheral surface of the connecting cylinder 75 is not limited to the structure of the piston ring 73, and if sufficient strength, durability, and sealing properties are ensured, the structure may be replaced with a structure of a sealing member of various forms, or a structure in which the outer peripheral surface of the connecting shaft 72 directly slides in close contact with the inner peripheral surface of the connecting cylinder 75 without providing a sealing member may be adopted. Further, the seal member may be provided on the inner peripheral surface of the coupling cylinder 75 instead of the outer peripheral surface of the coupling shaft 72.
As shown in fig. 13, a rod (piston rod) 37 for transmitting a driving force to the piston 33 via the coupling shaft 72 is connected to a rear end portion 74 (left end portion in fig. 12 and 13) of the coupling shaft 72. As shown in fig. 12, the outer periphery of the rod (piston rod) 37 is sealed by a rod seal 70.
As shown in fig. 11, the rod seal 70 includes a plurality of rod seal rings 53 that seal the outer periphery of the rod (piston rod) 37, and a plurality of ring cups 54 that house the rod seal rings 53. Sliding friction heat is generated by sliding of the rod seal ring 53 and the rod (piston rod) 37. The sliding frictional heat is transferred to the ring cup 54.
In this compression cylinder, since the coupling cylinder 75 sealed by the coupling shaft 72 exists between the cylinder tube 34 and the rod seal 70, a high pressure in the cylinder tube 34 is not applied to the rod seal 70. Therefore, even if the pressure in the cylinder tube 34 pulsates between the suction pressure and the discharge pressure, the load applied to the rod seal 70 does not increase, and the vibration, the impact, and the sliding frictional heat generated in the rod seal 70 are small. Therefore, the load applied to the rod seal 70 that seals the outer periphery of the rod (piston rod) 37 is small, and the life can be extended.
Further, since the rod seal 70 generates less vibration, less impact, and less sliding frictional heat, it is not necessary to supply lubricant oil between the rod (piston rod) 37 and the rod seal ring 53. In this case, the lubricating oil can be prevented from being mixed into the compressed gas.
Further, in the compression cylinder, by forming the piston ring 36 and the guide ring 36a by using a material having high heat resistance, it is not necessary to supply oil to the piston 33. Alternatively, in the compression cylinder, as shown in embodiments 1 to 3, by providing a cooling mechanism for circulating the coolant, the heat of the piston 33, the piston ring 36, the guide ring 36a, the cylinder tube 34, and the cylinder liner 35 is absorbed and radiated to the outside of the cylinder tube 34, thereby cooling the inside of the cylinder tube 34, and oil supply to the piston 33 is not necessary.
As shown in fig. 11, the rod seal 70 may be configured such that the refrigerant is distributed and supplied from the refrigerant (coolant) supply passage 66 to the flow passages in the respective cups 54, and the refrigerant is collected and discharged from these flow passages to the refrigerant (coolant) discharge passage 67. The refrigerant (coolant) supply passage 66 communicates with the outside at a refrigerant (coolant) supply port 68, penetrates the inside of each ring cup 54, and branches off in each ring cup 54 to communicate with the flow path inside each ring cup 54. The refrigerant (coolant) discharge passage 67 communicates with the flow path in each of the annular cups 54, is collected in each of the annular cups 54, penetrates the inside of each of the annular cups 54, and communicates with the outside at a refrigerant (coolant) discharge port 69. By supplying the refrigerant to the flow path in each ring cup 54, a large amount of sliding friction heat can be removed, and the durability of the rod seal 70 can be improved.
(5 th embodiment of Cylinder)
Fig. 14 is a sectional view showing the structure of a compression cylinder (embodiment 5) of the present invention.
As shown in fig. 14, the compression cylinder of the present embodiment includes a cylinder tube 34, a cylinder liner 35 disposed in the cylinder tube 34, and a piston 33 slidably disposed in the cylinder liner 35, and the gas supplied from an intake port 63 through an intake valve 63a is compressed by the piston 33 in the cylinder tube 34 and then sent out from an exhaust port 64 through an exhaust valve 64 a.
The cylinder tube 34 is formed in a tubular shape, and a cylindrical cylinder liner 35 is fitted therein. Further, if the inner surface portion of the cylinder tube 34 has sufficient strength and durability, the cylinder liner 35 may not be provided. The cylinder tube 34 communicates with the suction port 63 and the discharge port 64 on the rear end side (left end side in fig. 14). Further, a front end portion (right end portion in fig. 14) of the cylinder tube 34 is closed by a cylinder head 57. The space in the cylinder tube 34 between the front end portion (right end portion in fig. 14) 33a of the piston 33 and the cylinder head 57 communicates with the outside (gas suction side) via the communication hole 34 a.
The piston 33 is formed in a cylindrical shape capable of being fitted in the cylinder liner 35. A plurality of ring-shaped piston rings 36 are fitted around the piston 33. Further, a guide ring 36a is fitted to the outside of the front end side (right end side in fig. 14) and the base end side (left end side in fig. 14) of the piston 33. The outer peripheral portions of the piston ring 36 and the guide ring 36a closely slide on the inner peripheral surface of the cylinder liner 35. Further, if the piston ring 36 and the guide ring 36a ensure sufficient strength and durability, they may be replaced with various types of seal members, or they may not be provided, for example, as in a labyrinth seal.
The gas in the cylinder bore 34 (in the cylinder liner 35) is compressed by the piston 33 sliding in the cylinder liner 35 in the axial direction (arrow a in fig. 14) of the cylinder bore 34. In the cylinder tube 34 (in the cylinder liner 35), the internal pressure greatly varies depending on the moving direction of the piston 33. When the moving direction of the piston 33 is a direction (right direction in fig. 14) in which the volume in the cylinder 34 increases, the pressure in the cylinder 34 decreases, and when the moving direction of the piston 33 is a direction (left direction in fig. 14) in which the volume in the cylinder 34 decreases, the pressure in the cylinder 34 increases. At this time, the gas in the cylinder tube 34 is compressed.
A rod (piston rod) 37 for transmitting a driving force to the piston 33 is coaxially and integrally connected to a base end portion 33b (left end portion in fig. 14) of the piston 33. The rod (piston rod) 37 is formed in a cylindrical shape having a smaller diameter than the piston 33. The rod (piston rod) 37 extends to the atmosphere side (outside) after passing through a coupling tube 75 coaxially formed in the cylinder tube 34. The outer periphery of the rod (piston rod) 37 is sealed by a rod seal 70.
Fig. 15 is a vertical sectional view showing the structure of a rod seal of a compression cylinder (embodiment 5) of the present invention.
As shown in fig. 15, the stem seal 70 is constituted to include: a plurality of rod seal rings 53 arranged around the rod (piston rod) 37, arranged in the axial direction of the rod (piston rod) 37, and sealing the outer periphery of the rod (piston rod) 37; and a plurality of ring cups 54 that receive the rod seal rings 53. Sliding friction heat is generated by sliding of the rod seal ring 53 and the rod (piston rod) 37. The sliding frictional heat is transferred to the ring cup 54.
The middle portion (for example, substantially the center portion) of the stem seal 70 in the axial direction is set to a pressure (for example, suction pressure) lower than the pressure of the gas discharged from the discharge port 64 and higher than the atmospheric pressure.
As shown in fig. 14 and 15, in order to set the middle portion in the axial direction of the rod seal 70 to the predetermined pressure, it is preferable that an annular spacer 71 is disposed in the middle portion in the axial direction in a gap between the rod seal rings 53 at the position, and an inner peripheral portion of the annular spacer 71 communicates with a space (for example, the suction port 63) lower in pressure than the gas discharged from the discharge port 64 via the communication hole 76.
The number of rod seal rings 53 on the front stage side (cylinder tube 34 side) and the number of rod seal rings 53 on the rear stage side (atmosphere side) of the portion (inner peripheral portion of the annular spacer 71) that is set as the space of the predetermined pressure can be appropriately set in accordance with the pressure of the gas discharged from the discharge port 64.
The axial middle portion of the stem seal 70, which is set to a pressure lower than the discharge pressure, may be at least 1 portion, or may be a plurality of portions. Therefore, the number of the communication holes 76 is not limited to 1, and a plurality of communication holes may be provided. When a plurality of portions in the axial direction of the rod seal 70 are set to a pressure lower than the discharge pressure, it is preferable to gradually decrease the pressure from a portion on the front stage side (cylinder tube 34 side) toward a portion on the rear stage side (atmosphere side).
A high pressure difference between the inside of the cylinder bore 34 and the atmospheric pressure is not applied to the portion on the front stage side of the rod seal 70. The only pressure difference applied to this portion is the pressure difference between the discharge pressure and, for example, the suction pressure, and not the pressure difference between the discharge pressure and the atmospheric pressure. In addition, only the pressure difference between, for example, the suction pressure and the atmospheric pressure, not the pressure difference between the discharge pressure and the atmospheric pressure, is applied to the portion on the rear stage side of the rod seal 70. Therefore, even if the pressure in the cylinder tube 34 pulsates between the suction pressure and the discharge pressure, the load applied to the rod seal 70 does not increase, and the vibration, the impact, and the sliding friction heat generated in the rod seal 70 are small. Therefore, the load applied to the rod seal 70 is small, and the life can be extended.
Further, since the rod seal 70 generates less vibration, shock, and sliding frictional heat in the rod seal 70, it is not necessary to supply lubricant oil between the rod (piston rod) 37 and the rod seal ring 53. In this case, the lubricating oil can be prevented from being mixed into the compressed gas.
Further, in the compression cylinder, by forming the piston ring 36 and the guide ring 36a by using a material having high heat resistance, it is not necessary to supply oil to the piston 33. Alternatively, in the compression cylinder, a cooling mechanism for circulating the coolant is provided, and the heat of the piston 33, the piston ring 36, the guide ring 36a, the cylinder tube 34, and the cylinder liner 35 is absorbed and radiated to the outside of the cylinder tube 34, thereby cooling the inside of the cylinder tube 34, and the oil supply to the piston 33 is not necessary.
As shown in fig. 15, the rod seal 70 may be configured to distribute and supply the refrigerant from the refrigerant (coolant) supply passage 66 to the passages in the respective cups 54, and to collect and discharge the refrigerant from these passages to the refrigerant (coolant) discharge passage 67. The refrigerant (coolant) supply passage 66 communicates with the outside at a refrigerant (coolant) supply port 68, penetrates the inside of each ring cup 54, and branches off in each ring cup 54 to communicate with the flow path inside each ring cup 54. The refrigerant (coolant) discharge passage 67 communicates with the flow path in each of the annular cups 54, is collected in each of the annular cups 54, penetrates the inside of each of the annular cups 54, and communicates with the outside at a refrigerant (coolant) discharge port 69. By supplying the refrigerant to the flow path in each ring cup 54, a large amount of sliding friction heat can be removed, and the durability of the rod seal 70 can be improved.
The communication hole 76 may be provided so as to penetrate into each of the annular cups 54, like the refrigerant (coolant) supply passage 66 or the refrigerant (coolant) discharge passage 67.
(other construction example of compressor)
Fig. 16 is a block diagram schematically showing a compressor configured by using the compression cylinder of the present invention (showing an example in which oil is not supplied (lubricating oil is not required) because of the reliquefaction).
The compressor 100 configured by using the compression cylinder of the present invention may have 1 stage, but as an example, as shown in fig. 16, includes a plurality of (for example, 5) compression stages 101, 102, 103, 104, 105 each having a compression cylinder, and the gas is gradually compressed and increased in pressure in each of the compression stages 101, 102, 103, 104, 105. At a later stage (e.g. stage 4) of the plurality of compression stages 101, 102, 103, 104, 105, the gas has become a high pressure above 100 bar (10 MPa).
Conventionally, in a cylinder in which high-pressure gas of 100 bar (10MPa) or more is further compressed to, for example, 200 bar or more, there is a possibility that the resin seal rings (piston ring and rod seal ring) of the piston 33 and the rod seal 70 may have a shortened life due to high heat. The resin seal ring can maintain its useful life even in a non-oil supply type (not requiring the supply of lubricating oil) under low pressure. However, for example, in the case of compressing LNG boil-off gas to be fuel gas for a marine engine, 5-stage compression is required, and in the 5 th stage, under high pressure conditions where the suction pressure is 100 to 120 bar and the discharge pressure is 200 bar or more, the practical life of the resin seal ring may not be maintained by the oil-less type.
In the case where the compression cylinder of the present invention has the cooling mechanism as described above (embodiments 1 to 3), the cooling fluid is circulated in the flow path to cool the compression cylinder, and therefore, oil supply to the piston is not required in any of the compression stages 101, 102, 103, 104, and 105. The compression cylinders according to embodiments 4 and 5 do not require oil supply to the rod seal, and oil supply to the piston can be eliminated by providing a cooling mechanism, regardless of which compression stage 101, 102, 103, 104, 105 is used. In this case, in the compressor 100, there is no possibility that the compressed gas is contaminated by the lubricating oil. Therefore, the gas after passing through the subsequent compression stage can be liquefied again at a very low temperature and a high pressure and reused. That is, the compression cylinder of the present invention is particularly useful when used under high pressure (for example, for use in which a gas already at high pressure (for example, 100 bar or more) is further at high pressure (for example, 200 bar or more)).
Therefore, in the compressor 100, there is no possibility that the compressed gas is contaminated by the lubricating oil. Therefore, the gas after passing through the subsequent compression stage can be liquefied again at a very low temperature and a high pressure and reused. The compressor 100 can be adapted for all purposes, for example in the case of compressing natural gas, the natural gas after the last compression stage 105 can be returned to the storage tank 106. In addition, the check valve in front of the later stage compression stage (between the 4 th and 5 th stages 104 and 105) necessary in the existing compressor is no longer required.
In addition, in the high-pressure hydrogen gas used for diesel desulfurization, it is impossible to use the fuel-cut system because of the high pressure, and therefore, the hydrogen gas is used in a state of containing oil. This shortens the life of the expensive catalyst in the reactor, but there is no way to use only high-pressure hydrogen gas containing oil at present. If the hydrogen gas is a high-pressure hydrogen gas containing no oil, the life of the catalyst can be prolonged, which is advantageous.
(housing and horizontal opposed crank drive mechanism)
Fig. 17 is an external perspective view of the compressor.
Fig. 18 is a sectional view of the compressor.
In the compressors 1 and 100, as shown in fig. 17 and 18, all of the compression stages 9, 10, 13, 14, 15, 101 to 105 are mounted in a common casing 29.
As shown in fig. 17 and 18, the horizontally opposed crank drive mechanism 28 includes a crankshaft 28a to which a bearing is attached. The pair of cylinders are connected to each other across the crankshaft 28a so as to face each other horizontally. In the horizontally opposed compressor, cylinders are disposed on the left and right sides with a housing 29 and a crank drive mechanism 28 interposed therebetween.
On both sides of the crank shaft 28a, a plurality of engagement bars 28b separated in the longitudinal direction along the crank shaft 28a are provided. Each of the joint rods 28b is connected to the piston rod 37 via a crosshead pin bearing 28C and a crosshead 28 d.
The piston rods 37 are connected to the pistons 11a, 12a, 16a, 17a, and 18a of the cylinders 11, 12, 16, 17, and 18.
The casing 29 covers the compression stages 9, 10, 13, 14, and 15 arranged on both sides with the crankshaft 28a interposed therebetween.
A flywheel is provided at an end of the crankshaft 28a and is coupled to a drive shaft, not shown, via a coupling. In this embodiment, 5 (or 6) cylinders 11, 12, 16, 17, and 18 are mounted on the crankshaft 28 a. The pistons 11a, 12a, 16a, 17a, 18a of the cylinders 11, 12, 16, 17, 18 are driven by a crankshaft 28a via piston rods 37 within the cylinders.
The compressor is not limited to the configuration using the horizontally opposed crank drive mechanism, and may be configured as a vertical compressor.
(for the respective embodiments)
The present invention is not limited to the above-described embodiments, and various improvements and design changes can be made without departing from the scope of the present invention. For example, the cylinder having the cooling mechanism or the like may have each of the structures of embodiments 1 to 5 of the cylinder alone, or may have a plurality of structures.
In addition, it is obvious that the specific detailed structure, the numerical value, and the like, and the control content of the control device, and the like can be appropriately changed. Also, the embodiments disclosed herein are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is indicated by the scope of the claims, rather than the foregoing description, and all changes that come within the meaning and range of equivalency of the claims are intended to be embraced therein.
Claims (11)
1. A compression cylinder, comprising:
a cylinder barrel which is communicated with the suction inlet and the discharge outlet;
a piston disposed in the cylinder tube so as to be capable of sliding in close contact therewith;
a coupling shaft which is integrally connected to the piston coaxially, has a smaller diameter than the piston, and can slide closely in a coupling cylinder formed coaxially with the cylinder;
a rod connected to the connecting shaft and configured to transmit a driving force to the piston through the connecting shaft;
a stem seal sealing an outer periphery of the stem; and
a communication hole that communicates a space inside the coupling cylinder between a rear end portion of the coupling shaft and the rod seal with the outside,
the compression cylinder compresses the gas supplied from the suction port in the cylinder tube by the piston and then sends the compressed gas out from the discharge port.
2. The compression cylinder of claim 1, wherein:
the space in the coupling cylinder between the rear end portion of the coupling shaft and the rod seal communicates with the outside through the communication hole, and thus becomes a pressure lower than the pressure of the gas discharged from the discharge port and higher than the atmospheric pressure.
3. The compression cylinder of claim 1, wherein:
the rod seal does not need to be supplied with lubricating oil.
4. The compression cylinder of claim 2, wherein:
the rod seal does not need to be supplied with lubricating oil.
5. The compression cylinder according to any one of claims 1 to 4, characterized in that:
a piston ring is attached to an outer peripheral surface of the connecting shaft, and an outer peripheral portion of the piston ring slides in close contact with an inner peripheral surface of the connecting cylinder.
6. The compression cylinder according to any one of claims 1 to 4, characterized in that:
a cylindrical cylinder sleeve is arranged in the cylinder barrel,
a piston ring and a guide ring are attached to an outer peripheral surface of the piston, and outer peripheral portions of the piston ring and the guide ring slide in close contact with an inner peripheral surface of the cylinder liner.
7. The compression cylinder of claim 5, wherein:
a cylindrical cylinder sleeve is arranged in the cylinder barrel,
a piston ring and a guide ring are attached to an outer peripheral surface of the piston, and outer peripheral portions of the piston ring and the guide ring slide in close contact with an inner peripheral surface of the cylinder liner.
8. The compression cylinder according to any one of claims 1 to 4, characterized in that:
the compression cylinder is used in such a way that the gas is above 200 bar.
9. The compression cylinder of claim 5, wherein:
the compression cylinder is used in such a way that the gas is above 200 bar.
10. The compression cylinder of claim 6, wherein:
the compression cylinder is used in such a way that the gas is above 200 bar.
11. The compression cylinder of claim 7, wherein:
the compression cylinder is used in such a way that the gas is above 200 bar.
Applications Claiming Priority (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018170879A JP7146539B2 (en) | 2018-09-12 | 2018-09-12 | compression cylinder |
| JP2018-170879 | 2018-09-12 | ||
| JP2018-170880 | 2018-09-12 | ||
| JP2018170878A JP7146538B2 (en) | 2018-09-12 | 2018-09-12 | Compressor and LNG tanker |
| JP2018170881A JP6926371B2 (en) | 2018-09-12 | 2018-09-12 | Compression cylinder |
| JP2018170880A JP6930686B2 (en) | 2018-09-12 | 2018-09-12 | Compression cylinder |
| JP2018-170881 | 2018-09-12 | ||
| JP2018-170878 | 2018-09-12 | ||
| PCT/JP2019/035725 WO2020054770A1 (en) | 2018-09-12 | 2019-09-11 | Compressor, lng tanker, and compression cylinder |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112703316A CN112703316A (en) | 2021-04-23 |
| CN112703316B true CN112703316B (en) | 2021-08-03 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980058200.3A Active CN112703316B (en) | 2018-09-12 | 2019-09-11 | Compression cylinder |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN112703316B (en) |
| WO (1) | WO2020054770A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GR1010064B (en) * | 2020-06-12 | 2021-08-20 | Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) | Compressor unit |
| CN114439728B (en) * | 2022-02-15 | 2024-04-09 | 西安佰能达动力科技有限公司 | Circulation liquid seal compressor |
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| GB1003258A (en) * | 1961-07-05 | 1965-09-02 | Basf Ag | Piston and piston rod seals for a multistage high pressure gas compressor |
| JPH1061547A (en) * | 1996-06-03 | 1998-03-03 | American Standard Inc | Multiple stage gas compressor, operating method therefor, and intercooler system of thermostat control |
| JP2006152975A (en) * | 2004-12-01 | 2006-06-15 | Hitachi Industries Co Ltd | Reciprocating compressor |
| EP3009676A2 (en) * | 2014-09-26 | 2016-04-20 | Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) | Reciprocating compression apparatus |
| JP2017194038A (en) * | 2016-04-22 | 2017-10-26 | 三井造船株式会社 | Compressibility fluid supply device |
| CN107882815A (en) * | 2017-12-25 | 2018-04-06 | 宣城***机械有限公司 | A kind of energy saving cylinder piston rod |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57169856U (en) * | 1981-04-21 | 1982-10-26 | ||
| JPS6032541U (en) * | 1983-08-10 | 1985-03-05 | 川崎重工業株式会社 | Borecool type cooled cylinder liner |
| JP3789691B2 (en) * | 1999-09-14 | 2006-06-28 | 三洋電機株式会社 | High pressure compressor compressor |
| JP2006266217A (en) * | 2005-03-25 | 2006-10-05 | Isuzu Motors Ltd | Heat shield engine sealing structure |
| JP6363488B2 (en) * | 2014-12-11 | 2018-07-25 | 株式会社神戸製鋼所 | Compressor |
| JP6665383B2 (en) * | 2016-01-14 | 2020-03-13 | 株式会社三井Ｅ＆Ｓマシナリー | Fuel gas supply system and fuel gas supply method |
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2019
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- 2019-09-11 WO PCT/JP2019/035725 patent/WO2020054770A1/en active Application Filing
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1003258A (en) * | 1961-07-05 | 1965-09-02 | Basf Ag | Piston and piston rod seals for a multistage high pressure gas compressor |
| JPH1061547A (en) * | 1996-06-03 | 1998-03-03 | American Standard Inc | Multiple stage gas compressor, operating method therefor, and intercooler system of thermostat control |
| JP2006152975A (en) * | 2004-12-01 | 2006-06-15 | Hitachi Industries Co Ltd | Reciprocating compressor |
| EP3009676A2 (en) * | 2014-09-26 | 2016-04-20 | Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) | Reciprocating compression apparatus |
| JP2017194038A (en) * | 2016-04-22 | 2017-10-26 | 三井造船株式会社 | Compressibility fluid supply device |
| CN107882815A (en) * | 2017-12-25 | 2018-04-06 | 宣城***机械有限公司 | A kind of energy saving cylinder piston rod |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2020054770A1 (en) | 2020-03-19 |
| CN112703316A (en) | 2021-04-23 |
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