WO2014181867A1 - ユニフロー掃気式2サイクルエンジン - Google Patents
ユニフロー掃気式2サイクルエンジン Download PDFInfo
- Publication number
- WO2014181867A1 WO2014181867A1 PCT/JP2014/062473 JP2014062473W WO2014181867A1 WO 2014181867 A1 WO2014181867 A1 WO 2014181867A1 JP 2014062473 W JP2014062473 W JP 2014062473W WO 2014181867 A1 WO2014181867 A1 WO 2014181867A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- injection
- injection unit
- unit group
- cylinder
- scavenging
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
- F02B25/06—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke the cylinder-head ports being controlled by working pistons, e.g. by sleeve-shaped extensions thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
-
- 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
- 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
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02M21/0248—Injectors
- F02M21/0275—Injectors for in-cylinder direct injection, e.g. injector combined with spark plug
-
- 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
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02M21/0248—Injectors
- F02M21/0278—Port fuel injectors for single or multipoint injection into the air intake system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
- F02D19/08—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels
- F02D19/10—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels peculiar to compression-ignition engines in which the main fuel is gaseous
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2400/00—Control systems adapted for specific engine types; Special features of engine control systems not otherwise provided for; Power supply, connectors or cabling for engine control systems
- F02D2400/04—Two-stroke combustion engines with electronic control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
- F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
- F02D41/3035—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode
- F02D41/3041—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode with means for triggering compression ignition, e.g. spark plug
- F02D41/3047—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode with means for triggering compression ignition, e.g. spark plug said means being a secondary injection of fuel
-
- 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
- Y02T10/12—Improving ICE efficiencies
-
- 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
Definitions
- the present invention relates to a uniflow scavenging two-cycle engine that burns a premixed gas generated by injecting fuel gas into active gas sucked from a scavenging port.
- the present application claims priority based on Japanese Patent Application No. 2013-1000052 filed in Japan on May 10, 2013, the contents of which are incorporated herein by reference.
- a scavenging port is provided at one end in the stroke direction of the piston in the cylinder, and an exhaust port is provided at the other end in the stroke direction of the piston in the cylinder. It has been.
- the active gas is sucked into the combustion chamber from the scavenging port in the intake (supply) stroke, the exhaust gas generated by the combustion action is pushed out from the exhaust port by the sucked active gas and exhausted.
- a fuel gas is injected into the sucked active gas to generate a premixed gas, and a combustion action is obtained by compressing the generated premixed gas. Reciprocates within.
- the present invention has been made in view of such a problem, and an object of the present invention is to provide a uniflow scavenging two-cycle engine capable of suppressing fuel gas blowout while uniformly diffusing the fuel gas.
- a uniflow scavenging two-cycle engine includes a cylinder in which a combustion chamber is formed, a piston that slides in the cylinder, and a stroke of the piston in the cylinder.
- a scavenging port that is provided on one end side in the direction and sucks the active gas into the combustion chamber according to the sliding motion of the piston, and an inner peripheral surface of the scavenging port that injects fuel gas into the active gas sucked into the scavenging port; Or, including a plurality of injection parts that include different positions in the stroke direction of the piston, including an opening provided on the outer side of the cylinder from the inner peripheral surface, the plurality of injection parts on the other end side in the stroke direction
- a first injection unit group that is a set of one or a plurality of injection units, and a second injection unit group that is a set of one or a plurality of injection units located on one end side in the stroke direction relative to the first injection unit group Small Divided into Kutomo two sets, the injection of the first injection unit group, from the ejection portion of the second ejection portion group, the injection stop of the fuel gas is low.
- a uniflow scavenging two-cycle engine includes a cylinder in which a combustion chamber is formed, a piston that slides in the cylinder, and a piston in the cylinder.
- a scavenging port that is provided on one end side in the stroke direction and sucks the active gas into the combustion chamber according to the sliding motion of the piston, and an inner periphery of the scavenging port that injects fuel gas into the active gas sucked into the scavenging port
- a plurality of injection portions that include different positions in the stroke direction of the piston, including an opening provided on the outer side of the cylinder than the surface or the inner peripheral surface, and the plurality of injection portions are the other ends in the stroke direction.
- a first injection unit group that is a set of one or a plurality of injection units on the side
- a second injection unit group that is a set of one or a plurality of injection units that are closer to one end side in the stroke direction than the first injection unit group
- the injection of the first injection unit group may stop the fuel gas injection later than the injection unit of the second injection unit group.
- the first to third aspects further include an on-off valve that opens and closes a flow path of the fuel gas supplied to the injection unit, and the distance from the on-off valve to the injection unit is second in the first injection unit group. It may be longer than the jetting unit group.
- the flow path of the fuel gas having the injection section as the outlet end is a flow in a direction perpendicular to the flow of the fuel gas in the first injection section group than in the second injection section group.
- the road area may be small.
- the uniflow scavenging two-cycle engine of the present invention it is possible to suppress the fuel gas from being blown through while uniformly diffusing the fuel gas.
- FIG. 2B It is explanatory drawing which shows the whole structure of a uniflow scavenging type 2 cycle engine. It is sectional drawing of a part of cylinder and fuel injection part in the same cross section as FIG. 1 for demonstrating a fuel injection part. It is sectional drawing along the II (b) -II (b) line
- FIG. 1 is a diagram showing an overall configuration of a uniflow scavenging two-cycle engine 100.
- the uniflow scavenging two-cycle engine 100 of the present embodiment is used for, for example, ships.
- the uniflow scavenging two-cycle engine 100 includes a cylinder 110 (cylinder head 110a and cylinder block 110b), a piston 112, a pilot injection valve 114, an exhaust port 116, an exhaust valve driving device 118, and an exhaust valve. 120, a scavenging port 122, a scavenging chamber 124, a fuel injection unit 126, a rotary encoder 130, and a combustion chamber 140.
- the governor (governor) 150, the fuel injection control unit 152, exhaust gas It is controlled by a control unit such as the control unit 154.
- a piston 112 connected to a cross head is slidably reciprocated in a cylinder 110 through four successive strokes of intake (supply), compression, combustion, and exhaust.
- intake supply
- compression combustion
- exhaust exhaust
- the stroke in the cylinder 110 can be formed relatively long, and the side pressure acting on the piston 112 can be received by the cross head, so a uniflow scavenging two-cycle engine
- the output of 100 can be increased.
- the cylinder 110 and a crank chamber (not shown) in which the crosshead is accommodated are isolated, deterioration of the crank chamber can be prevented even when low quality fuel oil is used.
- the pilot injection valve 114 is provided in the cylinder head 110a above the top dead center of the piston 112, and injects an appropriate amount of fuel oil at a desired time in the engine cycle.
- fuel oil is spontaneously ignited by the heat of the combustion chamber 140 surrounded by the cylinder head 110a, the cylinder liner in the cylinder block 110b, and the piston 112, and burns in a short time. Make it high. Therefore, the premixed gas containing fuel gas can be reliably burned at a desired timing.
- the exhaust port 116 is an opening provided at the top of the cylinder head 110a above the top dead center of the piston 112, and is opened and closed to exhaust the exhaust gas after combustion generated in the cylinder 110.
- the exhaust valve driving device 118 opens and closes the exhaust port 116 by sliding the exhaust valve 120 up and down at a predetermined timing. The exhaust gas exhausted through the exhaust port 116 in this manner is supplied to the turbine side of a turbocharger (not shown) and then exhausted to the outside.
- the scavenging port 122 is a hole penetrating from the inner peripheral surface (the inner peripheral surface of the cylinder block 110b) on one end side in the stroke direction of the piston 112 in the cylinder 110 to the outer peripheral surface. A plurality of them are provided.
- the scavenging port 122 sucks the active gas into the cylinder 110 according to the sliding motion of the piston 112.
- Such an active gas includes an oxidizing agent such as oxygen and ozone, or a mixture thereof (for example, air).
- the scavenging chamber 124 is filled with active gas (for example, air) pressurized by a compressor of a supercharger (not shown), and the active gas is sucked from the scavenging port 122 with a differential pressure in the scavenging chamber 124 and the cylinder 110. Is done.
- the pressure in the scavenging chamber 124 can be substantially constant, but when the pressure in the scavenging chamber 124 changes, a pressure gauge is provided in the scavenging port 122, and the fuel gas injection amount, etc., according to the measured value, etc. Other parameters may be controlled.
- FIG. 2A to 2C are diagrams for explaining the fuel injection unit 126.
- FIG. 2A shows a part of the cylinder 110 and the fuel injection unit 126 in the same cross section as FIG. 1, and
- FIG. 2C shows a cross-section along the line (b) -II (b), and
- FIG. 2C shows an arrow view along the arrow II (c) in FIG. 2B.
- illustration of the cross-sectional structure of the fuel injection portion 126 and the piston 112 is omitted for easy understanding.
- the fuel injection unit 126 has mixing tubes 126a and 126b formed separately from the cylinder 110.
- the mixing tubes 126a and 126b are annular members that surround the radially outer side of the cylinder 110 along the circumferential direction.
- the mixing pipe 126a is disposed on the other end side (in FIG. 2A) in the stroke direction of the piston 112 with respect to the scavenging port 122, and the mixing pipe 126b is on one end side in the stroke direction of the piston 112 with respect to the scavenging port 122 (see FIG. 2A, lower side).
- a ring 156a is fitted in a groove 110c formed on the upper side of the mixing tube 126a on the outer peripheral surface of the cylinder 110, and the upward movement of the mixing tube 126a is restricted by the ring 156a. is doing.
- a ring 156b is fitted in a groove 110d formed on the lower side of the mixing pipe 126b, and the movement of the mixing pipe 126b to the lower side is restricted by the ring 156b. Yes.
- the mixing tube 126b is composed of two members 158a and 158b that surround the cylinder 110 half by half along the circumferential direction, and the protrusions provided at both ends of each of the members 158a and 158b. 158c and 158d are fastened with a chain, a nut or the like (so-called G coupling). That is, the mixing pipe 126b fastens the cylinder 110 from the outer peripheral side, and the vertical movement of the mixing pipe 126b in FIG. 2A is also limited by the frictional force of the contact portion between the mixing pipe 126b and the cylinder 110.
- the fixing means of the mixing tube 126b has been described, but the mixing tube 126a is also fastened with the same structure as the mixing tube 126b.
- a mixing chamber extending in an annular shape is formed inside each of the mixing tubes 126a and 126b.
- Each mixing chamber communicates with a fuel pipe (not shown) through which fuel gas obtained by gasifying LNG (liquefied natural gas) flows and an active pipe (not shown) through which active gas flows.
- LNG liquefied natural gas
- active pipe not shown
- the fuel gas from the fuel pipe and the active gas from the active pipe are mixed to generate a premixed gas.
- the fuel gas is not limited to LNG, and for example, gasified LPG (liquefied petroleum gas), light oil, heavy oil, or the like can be applied.
- the on-off valve 126c is disposed at a communication portion between the mixing chamber of the mixing pipe 126a and the fuel pipe and the active pipe, and the on-off valve 126d is disposed at a communication portion of the mixing chamber 126b with the fuel pipe and the active pipe. .
- the on-off valves 126c and 126d are opened, the fuel gas and the active gas flow into the mixing chamber from the fuel pipe and the active pipe, and when the on-off valves 126c and 126d are closed, the fuel gas from the fuel pipe and the active pipe to the mixing chamber. And the flow of active gas stops.
- the on-off valves 126c and 126d are individually controlled by the exhaust control unit 154.
- the distribution pipes 126e and 126f are arranged in series between the mixing pipe 126a and the mixing pipe 126b as shown in FIG. 2C.
- One end of each of the flow pipes 126e and 126f is disposed opposite to each other, the other end of the flow pipe 126e is fixed to the mixing pipe 126a, and the other end of the flow pipe 126f is fixed to the mixing pipe 126b.
- the flow pipes 126 e and 126 f are located on the outer peripheral surface of the cylinder 110 so as to face the partition 124 a provided between the adjacent scavenging ports 122 (the radial direction of the partition 124 a of the scavenging port 122.
- the distribution pipe 126e communicates with the mixing pipe 126a, and the premixed gas including the fuel gas flowing in from the mixing pipe 126a circulates therethrough.
- the circulation pipe 126f communicates with the mixing pipe 126b, and a premixed gas containing fuel gas flowing from the mixing pipe 126b flows therethrough. In this manner, independent flow paths are formed by the flow pipe 126e and the flow pipe 126f.
- FIG. 3 is a view for explaining the first injection unit 126g and the second injection unit 126h, and shows an enlarged view of a broken line part of FIG. 2C.
- the flow pipe 126e is formed with a plurality of first injection parts 126g
- the flow pipe 126f is formed with a plurality of second injection parts 126h.
- the first injection unit 126g and the second injection unit 126h are holes (openings) that connect the inner peripheral surface and the outer peripheral surface of the flow pipes 126e and 126f.
- the first injection unit 126g and the second injection unit 126h are located on the radially outer side of the cylinder 110 (outside the cylinder 110) between the adjacent scavenging ports 122, and extend from the flow pipes 126e and 126f in the circumferential direction of the cylinder 110. Open. In addition, the first injection unit 126g and the second injection unit 126h have different positions in the stroke direction of the piston 112.
- the first injection unit 126g and the second injection unit 126h are located on the other end side (upper side in FIG. 3) in the stroke direction with the position between the mixing tube 126a and the mixing tube 126b as a boundary.
- a set of first injection units 126g (first injection unit group 160) and a set of four second injection units 126h on the one end side in the stroke direction (lower side in FIG. 3) (second injection unit group 162) It is divided into two groups. That is, the first injection unit group 160 and the second injection unit group 162 are different in the position of the piston 112 in the stroke direction.
- on-off valves 126c and 126d ( 2A to C) is opened. Then, the premixed gas is ejected from the first injection unit group 160 and the second injection unit group 162 that are only open, and the active gas flowing from the scavenging chamber 124 toward the scavenging port 122 is directed to the fuel injection unit 126. Premixed gas is blown from the first injection unit group 160 and the second injection unit group 162. At this time, a vortex is generated in the active gas in the vicinity of the scavenging port 122, and the vortex can promote the mixing of the active gas and the premixed gas.
- FIG. 4A and 4B are diagrams for explaining the flow of the premixed gas in the cylinder 110
- FIG. 4A shows the flow of the premixed gas in the comparative example
- FIG. 4B shows the premixed gas in the present embodiment. Show the flow.
- the broken line indicates the relative velocity difference for each position along the radial direction with respect to the flow velocity of the gas in the cylinder 110
- arrows a and b indicate the flow path of the premixed gas.
- the tips of arrows a and b indicate the position of the beginning of the premixed gas flow at a predetermined timing.
- the premixed gas passing through one end side in the stroke direction of the piston 112 flows on the inner diameter side in the cylinder 110 (indicated by an arrow b).
- the gas in the cylinder 110 is slightly lower in velocity near the inner peripheral surface of the cylinder 110 due to friction and viscosity with the inner peripheral surface.
- the ascending speed is faster on the outer diameter side. This is because the flow velocity on the outer diameter side of the cylinder 110 is increased by the influence of the swirl.
- the exhaust valve 120 is located on the inner diameter side of the cylinder 110 so as to face the exhaust port 116.
- the gap between the exhaust port 116 and the exhaust valve 120 opening to the outer diameter side of the cylinder 110 is also a factor for increasing the flow velocity on the outer diameter side of the cylinder 110 more than the inner diameter side.
- the premixed gas indicated by arrow a has a higher flow rate than the premixed gas indicated by arrow b.
- the head of the premixed gas flow indicated by the arrow a reaches the exhaust port 116 while preceding the head of the premixed gas flow indicated by the arrow b.
- the speed difference of the premixed gas becomes a factor of blow-through from the exhaust valve 120.
- the on-off valve 126c has a later opening timing than the on-off valve 126d. That is, in the first injection unit group 160, the injection start of the premixed gas is later than in the second injection unit group 162.
- the premixed gas (indicated by arrow a) passing through the other end side (upper side in FIG. 4B) of the piston 112 in the stroke direction of the scavenging port 122 is in the stroke direction of the piston 112. It flows in the cylinder 110 later than the premixed gas (indicated by arrow b) passing through one end side (lower side in FIG. 4B).
- the premixed gas indicated by the arrows a and b reaches the cylinder head 110a at almost the same timing and burns in the combustion chamber 140.
- the blow-through of the premixed gas fuel gas
- the risk of the premixed gas being discharged to the exhaust system accompanying the blow-through and the deterioration of fuel consumption are suppressed.
- the start timing of the fuel injection from all the 1st injection part groups 160 and the 2nd injection part group 162 is delayed in order to suppress blow-by, it is from the 2nd injection part 126h of the 2nd injection part group 162.
- the start timing of the fuel injection is advanced. Accordingly, it is possible to ensure a long injection time of the premixed gas.
- the timing for stopping the injection is different between the second injection unit group 162 and the first injection unit group 160. That is, the on-off valve 126c has a closing timing later than that of the on-off valve 126d, and the first injection unit 126g of the first injection unit group 160 is more premixed than the second injection unit 126h of the second injection unit group 162. The injection stop is slow.
- the scavenging port 122 is gradually closed from one end side to the other end side. Temporarily, the injection of the premixed gas from all of the first injection unit group 160 and the second injection unit group 162 is stopped at the limit timing at which the premixed gas from the first injection unit group 160 can flow into the scavenging port 122. In this case, there is a possibility that the premixed gas injected from the second injection unit group 162 is not obstructed by the piston 112 and flows into the cylinder 110. Then, the premixed gas stays in the scavenging port 122 or outside the cylinder 110 (scavenging chamber 124).
- the premixed gas may blow through the exhaust port 116 as the exhaust gas is discharged.
- the first injection unit group 160 is slower to stop the premixed gas injection than the second injection unit group 162. That is, the second injection unit group 162 stops the injection of the premixed gas earlier than the first injection unit group 160. Therefore, in accordance with the timing at which the scavenging port 122 is gradually closed from one end side to the other end side, the injection of the premixed gas is stopped, and the above blow-through can be suppressed. Further, the risk that the premixed gas stays in the scavenging chamber 124 is also suppressed.
- the fuel injection stop timing from the first injection unit group 160 is set to be shorter than that in the case of stopping the fuel injection stop timing from all the first injection unit groups 160 and the second injection unit group 162 in order to suppress the blow-by. Will be late. Accordingly, it is possible to ensure a long injection time of the premixed gas.
- the rotary encoder 130 is provided in a crank mechanism (not shown) and detects a crank angle signal (hereinafter referred to as a crank angle signal).
- the governor 150 derives the fuel injection amount based on the engine output command value input from the host controller and the engine speed based on the crank angle signal from the rotary encoder 130, and outputs the fuel injection amount to the fuel injection control unit 152.
- the fuel injection control unit 152 controls the on-off valves 126c and 126d (see FIG. 2A) based on the information indicating the fuel injection amount input from the governor 150 and the crank angle signal from the rotary encoder 130.
- the exhaust control unit 154 outputs an exhaust valve operation signal to the exhaust valve driving device 118 based on the signal related to the fuel injection amount from the fuel injection control unit 152 and the crank angle signal from the rotary encoder 130.
- FIG. 5 is a diagram for explaining the operation of each control unit. As shown in FIG. 5, in the exhaust stroke after the combustion stroke, the exhaust port 116 and the scavenging port 122 are in a closed state, and the combustion chamber 140 (inside the cylinder 110) is filled with exhaust gas.
- the exhaust control unit 154 opens the exhaust valve 120 through the exhaust valve driving device 118, and the piston 112 slides.
- the scavenging port 122 opens according to the operation (t1 shown in FIG. 5). Then, the active gas is sucked from the scavenging port 122.
- the fuel injection control unit 152 opens the on-off valves 126c and 126d based on the information indicating the fuel injection amount input from the governor 150, the engine speed derived from the crank angle signal from the rotary encoder 130, and the like. Then, the premixed gas is injected from the fuel injection portion 126 to the outside of the cylinder 110 in the scavenging port 122 in the radial direction. As a result, the premixed gas is included in the active gas before being sucked into the scavenging port 122.
- the fuel injection control unit 152 opens the on-off valve 126c to start injection of the premixed gas from the second injection unit group 162 (t2 shown in FIG. 5), and then opens the on-off valve 126d.
- the injection of the premixed gas from the first injection unit group 160 is started (t3 shown in FIG. 5).
- the premixed gas rises while forming a swirl for promoting the mixing of the active gas and the fuel gas contained in the premixed gas, and pushes the exhaust gas in the combustion chamber 140 (inside the cylinder 110) from the exhaust port 116. .
- the fuel injection control unit 152 closes the on-off valve 126c and injects the premixed gas from the second injection unit group 162.
- the on-off valve 126d is closed to stop the injection of the premixed gas from the first injection unit 160 (t5 shown in FIG. 5).
- the scavenging port 122 is closed, and the suction of the active gas is stopped.
- the exhaust control unit 154 maintains the exhaust valve 120 in an open state, and the exhaust gas in the combustion chamber 140 (inside the cylinder 110) continues to be exhausted from the exhaust port 116 as the piston 112 rises. .
- the premixed gas is combusted in the combustion chamber 140, whereby the exhaust, intake, compression, and combustion stroke are repeated as described above.
- FIG. 6A to 6C are diagrams for explaining the fuel injection units 226 and 326 in the modified example of the present invention.
- FIG. 6A shows an enlarged view of a position corresponding to FIG. 3 in the first modified example
- FIG. FIG. 6 shows an enlarged view of a position corresponding to FIG. 3 in the second modified example
- FIG. 6C shows a diagram corresponding to FIG. 5 in the third modified example.
- the mixing pipe 226a is further away from the scavenging chamber 124 than the mixing pipe 226b, and the length of the flow pipe 226e is longer than the flow pipe 226f. . That is, the distance from the on-off valve 126c to the first injection unit 226g of the first injection unit group 160 is longer than the distance from the on-off valve 126d to the second injection unit 226h of the second injection unit group 162.
- the second injection unit group 162 is automatically first.
- the injection start and stop of the premixed gas are earlier than those of the injection unit group 160. Therefore, the control process for the on-off valves 126c and 126d is facilitated, and the control system for controlling the on-off valves 126c and 126d can be shared.
- the flow pipe 326e has a smaller flow path area along the direction perpendicular to the flow of the premixed gas (fuel gas) than the flow pipe 326f. That is, in the premixed air flow path having the injection units (the first injection unit 326g and the second injection unit 326h) as the outlet ends, the first injection unit group 160 is more premixed than the second injection unit group 162.
- the channel area in the direction perpendicular to the air flow is small.
- the fuel injection control unit 152 does not have to perform control for shifting the opening / closing timings of the on-off valves 126c and 126d. Therefore, the control process for the on-off valves 126c and 126d is facilitated, and the control system for controlling the on-off valves 126c and 126d can be used by branching the common wiring.
- a third injection unit is provided in addition to the first injection unit 126g and the second injection unit 126h.
- the third injection unit is arranged on one end side in the stroke direction with respect to the second injection unit 126h, and a third injection unit group is configured by the third injection unit. That is, the injection unit is divided into a first injection unit group 160, a second injection unit group 162, and a third injection unit group, with the positions in two different stroke directions as boundaries.
- the pre-mixed gas injection starts sequentially from the third injection unit of the third injection unit group on the one end side in the stroke direction to the second injection unit 126h and the first injection unit 126g.
- the second injection unit 126h and the first injection unit 126g and the injection of the premixed gas are sequentially stopped.
- the group is divided into three groups depending on the position in the stroke direction, and the group on the other end side in the stroke direction stops the injection of the premixed gas than the group on the one end side. And the injection start is slow. According to such a configuration, the injection timing of the premixed gas from the injection unit can be further finely controlled for each position in the stroke direction, and the effect of suppressing the blow-through is improved.
- the injection units (the first injection units 126g, 226g, 326g, the second injection units 126h, 226h, 326h) are provided outside the cylinder 110 with respect to the inner peripheral surface of the scavenging port 122.
- the opening has been described, the opening provided on the inner peripheral surface of the scavenging port 122 may be used.
- the second injection units 126h, 226h, and 326h divided into the second injection unit group 162, and the first injection units 126g, 226g, and 326g divided into the first injection unit group 160 Although the case where four each is provided in the stroke direction of the piston 112 has been described, the number of the first injection units 126g, 226g, 326g and the second injection units 126h, 226h, 326h arranged in the stroke direction of the piston 112 is as follows. One each may be sufficient and multiple other than four may be sufficient.
- the first injection units 126g, 226g, and 326g of the first injection unit group 160 are more premixed (fuel gas) than the second injection units 126h, 226h, and 326h of the second injection unit group 162.
- the case where both the injection start and injection stop of () are slow has been described.
- the second injection unit group 162 may be slower than the first injection unit group 160 in either one of the start and stop of injection of the premixed gas. Even in this case, it is possible to suppress blow-through of the fuel gas.
- the premixed gas of the fuel gas and the active gas is ejected from the first injection unit group 160 and the second injection unit group 162 toward the active gas flowing from the scavenging chamber 124 toward the scavenging port 122.
- the case of making it explained was explained.
- a configuration may be adopted in which only the fuel gas is injected from the first injection unit group 160 and the second injection unit group 162, and the premixed gas is generated by mixing with the active gas in the cylinder 110.
- the present invention can be used in a uniflow scavenging two-cycle engine that burns a premixed gas generated by injecting fuel gas into active gas sucked from a scavenging port.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Fuel-Injection Apparatus (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
Description
本願は、2013年5月10日に日本に出願された特願2013-100527号に基づき優先権を主張し、その内容をここに援用する。
図1は、ユニフロー掃気式2サイクルエンジン100の全体構成を示す図である。本実施形態のユニフロー掃気式2サイクルエンジン100は、例えば、船舶等に用いられる。具体的に、ユニフロー掃気式2サイクルエンジン100は、シリンダ110(シリンダヘッド110a、シリンダブロック110b)と、ピストン112と、パイロット噴射弁114と、排気ポート116と、排気弁駆動装置118と、排気弁120と、掃気ポート122と、掃気室124と、燃料噴射部126と、ロータリエンコーダ130と、燃焼室140と、を含んで構成され、ガバナー(調速機)150、燃料噴射制御部152、排気制御部154等の制御部によって制御される。
図6Aに示すように、燃料噴射部226においては、混合管226aが、混合管226bよりも掃気室124から離隔しており、流通管226eの長さが、流通管226fよりも長くなっている。すなわち、開閉弁126cから第1噴射部群160の第1噴射部226gまでの距離は、開閉弁126dから第2噴射部群162の第2噴射部226hまでの距離よりも長い。
図6Bに示すように、燃料噴射部326においては、流通管326eの方が流通管326fよりも、予混合気(燃料ガス)の流れに垂直な方向に沿った流路の面積が小さい。すなわち、噴射部(第1噴射部326g、第2噴射部326h)を出口端とする予混合気の流路は、第1噴射部群160の方が第2噴射部群162よりも、予混合気の流れに垂直な方向の流路面積が小さい。流路面積が小さい方が、圧力損失の影響によって予混合気の流速が遅くなり、噴射部に到達するタイミングが遅れる。
第3変形例においては、第1噴射部126g、第2噴射部126hの他に、第3噴射部が設けられている。第3噴射部は、第2噴射部126hよりもストローク方向の一端側に配され、第3噴射部で第3噴射部群が構成される。すなわち、噴射部は、2つの異なるストローク方向の位置を境界として、第1噴射部群160と、第2噴射部群162と、第3噴射部群に分けられる。
110 シリンダ
112 ピストン
122 掃気ポート
126、226、326 燃料噴射部
126g、226g、326g 第1噴射部(噴射部)
126h、226h、326h 第2噴射部(噴射部)
160 第1噴射部群
162 第2噴射部群
Claims (7)
- 内部に燃焼室が形成されるシリンダと、
前記シリンダ内を摺動するピストンと、
前記シリンダにおける前記ピストンのストローク方向の一端側に設けられ、前記ピストンの摺動動作に応じて前記燃焼室に活性ガスを吸入する掃気ポートと、
前記掃気ポートに吸入される活性ガスに燃料ガスを噴射する、前記掃気ポートの内周面、または、この内周面よりも前記シリンダの外側に設けられた開口を含む、前記ピストンのストローク方向の位置を異にする複数の噴射部と、
を備え、
前記複数の噴射部は、前記ストローク方向の他端側にある1または複数の噴射部の組である第1噴射部群と、第1噴射部群よりも、前記ストローク方向の一端側にある1または複数の噴射部の組である第2噴射部群との、少なくとも2つの組に分けられ、
前記第1噴射部群の前記噴射部は、前記第2噴射部群の前記噴射部より、前記燃料ガスの噴射停止が遅いユニフロー掃気式2サイクルエンジン。 - 内部に燃焼室が形成されるシリンダと、
前記シリンダ内を摺動するピストンと、
前記シリンダにおける前記ピストンのストローク方向の一端側に設けられ、前記ピストンの摺動動作に応じて前記燃焼室に活性ガスを吸入する掃気ポートと、
前記掃気ポートに吸入される活性ガスに燃料ガスを噴射する、前記掃気ポートの内周面、または、この内周面よりも前記シリンダの外側に設けられた開口を含む、前記ピストンのストローク方向の位置を異にする複数の噴射部と、
を備え、
前記複数の噴射部は、前記ストローク方向の他端側にある1または複数の噴射部の組である第1噴射部群と、第1噴射部群よりも、前記ストローク方向の一端側にある1または複数の噴射部の組である第2噴射部群との、少なくとも2つの組に分けられ、
前記第1噴射部群の前記噴射部は、前記第2噴射部群の前記噴射部より、前記燃料ガスの噴射開始が遅いユニフロー掃気式2サイクルエンジン。 - 前記第1噴射部群の前記噴射部は、前記第2噴射部群の前記噴射部より、前記燃料ガスの噴射停止が遅い、請求項2に記載のユニフロー掃気式2サイクルエンジン。
- 前記噴射部に供給される前記燃料ガスの流路を開閉する開閉弁をさらに備え、
前記開閉弁から前記噴射部までの距離は、前記第1噴射部群の方が前記第2噴射部群よりも長い、請求項1に記載のユニフロー掃気式2サイクルエンジン。 - 前記噴射部に供給される前記燃料ガスの流路を開閉する開閉弁をさらに備え、
前記開閉弁から前記噴射部までの距離は、前記第1噴射部群の方が前記第2噴射部群よりも長い、請求項2に記載のユニフロー掃気式2サイクルエンジン。 - 前記噴射部に供給される前記燃料ガスの流路を開閉する開閉弁をさらに備え、
前記開閉弁から前記噴射部までの距離は、前記第1噴射部群の方が前記第2噴射部群よりも長い、請求項3に記載のユニフロー掃気式2サイクルエンジン。 - 前記噴射部を出口端とする前記燃料ガスの流路は、前記第1噴射部群の方が前記第2噴射部群よりも、燃料ガスの流れに垂直な方向の流路面積が小さい、請求項1から6のいずれか1項に記載のユニフロー掃気式2サイクルエンジン。
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1020157030422A KR101809697B1 (ko) | 2013-05-10 | 2014-05-09 | 유니플로 소기식 2사이클 엔진 |
EP14794160.3A EP2995794B1 (en) | 2013-05-10 | 2014-05-09 | Uniflow scavenging 2-cycle engine |
DK14794160.3T DK2995794T3 (en) | 2013-05-10 | 2014-05-09 | LENGTH RINSE TOTAL ENGINE |
CN201480025832.7A CN105189968B (zh) | 2013-05-10 | 2014-05-09 | 单流扫气式二冲程发动机 |
JP2015515909A JP5974379B2 (ja) | 2013-05-10 | 2014-05-09 | ユニフロー掃気式2サイクルエンジン |
US14/935,300 US20160061099A1 (en) | 2013-05-10 | 2015-11-06 | Uniflow scavenging 2-cycle engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013-100527 | 2013-05-10 | ||
JP2013100527 | 2013-05-10 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/935,300 Continuation US20160061099A1 (en) | 2013-05-10 | 2015-11-06 | Uniflow scavenging 2-cycle engine |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014181867A1 true WO2014181867A1 (ja) | 2014-11-13 |
Family
ID=51867339
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2014/062473 WO2014181867A1 (ja) | 2013-05-10 | 2014-05-09 | ユニフロー掃気式2サイクルエンジン |
Country Status (7)
Country | Link |
---|---|
US (1) | US20160061099A1 (ja) |
EP (1) | EP2995794B1 (ja) |
JP (1) | JP5974379B2 (ja) |
KR (1) | KR101809697B1 (ja) |
CN (1) | CN105189968B (ja) |
DK (1) | DK2995794T3 (ja) |
WO (1) | WO2014181867A1 (ja) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5949183B2 (ja) | 2012-06-06 | 2016-07-06 | 株式会社Ihi | 2ストロークユニフローエンジン |
JP5983196B2 (ja) | 2012-08-31 | 2016-08-31 | 株式会社Ihi | ユニフロー掃気式2サイクルエンジン |
CN105209729B (zh) | 2013-05-10 | 2017-07-28 | 株式会社 Ihi | 直流扫气式二冲程发动机 |
CN110352294B (zh) * | 2017-03-06 | 2021-09-14 | 株式会社 Ihi | 单流扫气式二冲程发动机 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62129518A (ja) * | 1985-11-28 | 1987-06-11 | Mitsubishi Heavy Ind Ltd | 掃気ポ−ト管制式内燃機関 |
JPH06346737A (ja) * | 1993-06-07 | 1994-12-20 | Mitsubishi Heavy Ind Ltd | ディーゼル機関の掃気装置 |
JPH07208171A (ja) * | 1993-10-29 | 1995-08-08 | New Sulzer Diesel Ag | ディーゼル式往復動型ピストン内燃機関 |
JP3908855B2 (ja) | 1997-04-29 | 2007-04-25 | マーン・ベー・オグ・ドバルドヴェー・ディーゼール・アクティーゼルスカブ | ディーゼル型のターボ過給式複式燃料内燃機関の運転方法 |
JP2010209464A (ja) * | 2009-03-09 | 2010-09-24 | Waertsilae Schweiz Ag | 加工物の着座表面に被覆を付与する方法、及び被覆された着座表面を有する加工物 |
JP2012154189A (ja) * | 2011-01-24 | 2012-08-16 | Ihi Corp | 2サイクルエンジン |
JP2012167666A (ja) * | 2011-02-10 | 2012-09-06 | Man Diesel & Turbo Se | 2サイクル内燃機関及び該2サイクル内燃機関の運転方法 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1031808C (zh) * | 1993-03-26 | 1996-05-15 | 西安电子科技大学 | 滚锥蜗杆传动机构 |
AT6291U1 (de) * | 2001-06-19 | 2003-07-25 | Avl List Gmbh | Zweitakt-brennkraftmaschine mit kurbelgehäusespülung |
JP2011122465A (ja) * | 2009-12-08 | 2011-06-23 | Denso Corp | 燃料噴射制御装置 |
JP5587091B2 (ja) * | 2010-08-05 | 2014-09-10 | 株式会社ディーゼルユナイテッド | 2ストロークガス機関 |
CN103026034B (zh) * | 2010-08-05 | 2015-08-05 | 株式会社Ihi | 二循环发动机 |
JP5811538B2 (ja) * | 2011-01-24 | 2015-11-11 | 株式会社Ihi | 2サイクルエンジン |
DE102011050087A1 (de) * | 2011-05-04 | 2012-11-22 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Hubkolbenverbrennungskraftmaschine |
JP2013060863A (ja) * | 2011-09-13 | 2013-04-04 | Hitachi Automotive Systems Ltd | 内燃機関の制御装置 |
-
2014
- 2014-05-09 WO PCT/JP2014/062473 patent/WO2014181867A1/ja active Application Filing
- 2014-05-09 JP JP2015515909A patent/JP5974379B2/ja active Active
- 2014-05-09 EP EP14794160.3A patent/EP2995794B1/en active Active
- 2014-05-09 CN CN201480025832.7A patent/CN105189968B/zh active Active
- 2014-05-09 DK DK14794160.3T patent/DK2995794T3/en active
- 2014-05-09 KR KR1020157030422A patent/KR101809697B1/ko active IP Right Grant
-
2015
- 2015-11-06 US US14/935,300 patent/US20160061099A1/en not_active Abandoned
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62129518A (ja) * | 1985-11-28 | 1987-06-11 | Mitsubishi Heavy Ind Ltd | 掃気ポ−ト管制式内燃機関 |
JPH06346737A (ja) * | 1993-06-07 | 1994-12-20 | Mitsubishi Heavy Ind Ltd | ディーゼル機関の掃気装置 |
JPH07208171A (ja) * | 1993-10-29 | 1995-08-08 | New Sulzer Diesel Ag | ディーゼル式往復動型ピストン内燃機関 |
JP3908855B2 (ja) | 1997-04-29 | 2007-04-25 | マーン・ベー・オグ・ドバルドヴェー・ディーゼール・アクティーゼルスカブ | ディーゼル型のターボ過給式複式燃料内燃機関の運転方法 |
JP2010209464A (ja) * | 2009-03-09 | 2010-09-24 | Waertsilae Schweiz Ag | 加工物の着座表面に被覆を付与する方法、及び被覆された着座表面を有する加工物 |
JP2012154189A (ja) * | 2011-01-24 | 2012-08-16 | Ihi Corp | 2サイクルエンジン |
JP2012167666A (ja) * | 2011-02-10 | 2012-09-06 | Man Diesel & Turbo Se | 2サイクル内燃機関及び該2サイクル内燃機関の運転方法 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2995794A4 |
Also Published As
Publication number | Publication date |
---|---|
EP2995794B1 (en) | 2018-03-14 |
JPWO2014181867A1 (ja) | 2017-02-23 |
DK2995794T3 (en) | 2018-05-22 |
JP5974379B2 (ja) | 2016-08-23 |
CN105189968A (zh) | 2015-12-23 |
KR20150132586A (ko) | 2015-11-25 |
CN105189968B (zh) | 2018-04-13 |
EP2995794A4 (en) | 2017-01-04 |
US20160061099A1 (en) | 2016-03-03 |
EP2995794A1 (en) | 2016-03-16 |
KR101809697B1 (ko) | 2017-12-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6115045B2 (ja) | ユニフロー掃気式2サイクルエンジン | |
JP6065974B2 (ja) | ユニフロー掃気式2サイクルエンジン | |
JP6075086B2 (ja) | ユニフロー掃気式2サイクルエンジンおよびユニフロー掃気式2サイクルエンジンの燃料噴射方法 | |
JP6019941B2 (ja) | ユニフロー掃気式2サイクルエンジン | |
JP5983196B2 (ja) | ユニフロー掃気式2サイクルエンジン | |
WO2014054732A1 (ja) | ユニフロー掃気式2サイクルエンジン | |
JP5974379B2 (ja) | ユニフロー掃気式2サイクルエンジン | |
WO2015108144A1 (ja) | ユニフロー掃気式2サイクルエンジン | |
JP6222244B2 (ja) | ユニフロー掃気式2サイクルエンジン | |
JP6061026B2 (ja) | ユニフロー掃気式2サイクルエンジン | |
JP2016089642A (ja) | ユニフロー掃気式2サイクルエンジン |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201480025832.7 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 14794160 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2015515909 Country of ref document: JP Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 20157030422 Country of ref document: KR Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2014794160 Country of ref document: EP |