US20130017107A1 - Diesel engine fuel injection pump which pistons are sealed with all metal seal rings - Google Patents

Diesel engine fuel injection pump which pistons are sealed with all metal seal rings Download PDF

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Publication number
US20130017107A1
US20130017107A1 US13/548,222 US201213548222A US2013017107A1 US 20130017107 A1 US20130017107 A1 US 20130017107A1 US 201213548222 A US201213548222 A US 201213548222A US 2013017107 A1 US2013017107 A1 US 2013017107A1
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US
United States
Prior art keywords
pump
shaft
seal
piston
metal
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
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US13/548,222
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English (en)
Inventor
Kyong Tae Chang
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Neo Mechanics Ltd
Original Assignee
Neo Mechanics Ltd
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Filing date
Publication date
Application filed by Neo Mechanics Ltd filed Critical Neo Mechanics Ltd
Priority to US13/548,222 priority Critical patent/US20130017107A1/en
Assigned to NEO MECHANICS LIMITED reassignment NEO MECHANICS LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHANG, KYONG TAE
Publication of US20130017107A1 publication Critical patent/US20130017107A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0421—Cylinders
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners

Definitions

  • the presently claimed invention relates generally to diesel engines, diesel engine fuel injection pumps, and related mechanical parts. More specifically, the presently claimed invention relates to the sealing of the mechanical parts including the engine pistons.
  • the piston of a diesel engine fuel injection pump does not have any sealing device.
  • the sealing of the pistons is achieved by the viscosity of the diesel fuel combining with the minimal clearance between the piston and the cylinder bore internal wall with precision in the order of a few microns.
  • Technological advances make it possible for high-pressure fuel injection system with Common Rail Direct Injection (CRDI) to be used in diesel engines.
  • CMDI Common Rail Direct Injection
  • the diameter of the piston is necessary to be as small as possible since the total load on the piston reaches above one metric ton under such high pressure.
  • the piston diameter is 7 mm
  • the total load on the 7 mm piston becomes 1,154 kg under the internal pressure of 3,000 bar.
  • the total load on the shaft, as transferred from the pistons becomes 3,462 kg.
  • the rated load then becomes 5,293 kg when a 50% safety factor is accounted for. This requires excessively large diameter shaft and drive bearings in the pump.
  • the fuel pump of a plain 3,000 cc passenger car diesel engine should pump fuel at 300 cc/min to run the car at the speed of 60 km/hour.
  • a three-piston pump in which the pumping stroke is 7 mm, could pump 0.81 cc per rotation of the pump shaft.
  • the pump shaft rotates at 370 rpm to pump 300 cc/min.
  • the cylinder bore of the fuel injection pump has a cross sectional diameter of 7 mm, the outer diameter of the piston cannot exceed 6.98 mm, which is 0.02 mm smaller in diameter than that of the cylinder bore.
  • the cross sectional area of the piston is then equal to 0.382 square cm.
  • the clearance between the cylinder bore and the piston has an area of 0.003 square cm. This area is 0.8% of the cylinder bore cross sectional area. In other words, there is a minimum of 0.8% of internal leak between the cylinder bore and the piston under atmospheric pressure even the pump is in idle.
  • the internal leak can reach above 60% of total pumping capacity of the pump, which means nearly 60% of fuel pumping energy is lost by internal leaking
  • the internal leaking rate grows rapidly during the life of the pump. It is because the clearance between the cylinder bore and the piston generates vibrations of the piston in the bore during the combustion cycles, and the vibrations widen the clearance over time, so increases the internal leaking over time.
  • a typical fuel injection pumping system includes a pressure accumulator for storing pressurized fuel in the accumulator for maintaining a constant pressure with as little pressure fluctuation as possible for uniform combustion and minimum engine vibration.
  • the fuel injection pump must pump at least 40% more fuel than the engine burning capacity in order to be able to store excessive pressurized fuel in the accumulator. Because of the internal leaking which grows over time, eventually the fuel injection pump cannot pump enough extra fuel for the accumulation of pressurized fuel in the accumulator under the condition which the engine keeps running for a long period of time without idling. The fuel supply to the engine from the fuel pump becomes less than the fuel needed for combustion to maintain speed. At this point, the replacement of the fuel injection pump is needed. Usually this occurs once every year on average. Therefore, this is a general desire in the art of diesel engine technology to find a better fuel injection pump, particularly a better fuel injection pump that does not wear out frequently.
  • all-metal-seal rings are used for the sealing of the piston and the cylinder bore of a diesel engine fuel injection pump.
  • the diesel engine fuel injection pump equipped with one or more all-metal-seal rings on the pistons can produce absolute zero internal leakage even at very low speed such as 20 rpm.
  • a cylinder bore of a fuel injection pump having a 18 mm cross sectional diameter has a the cross section area of 2.55 square cm.
  • the fuel injection pump has three pistons and if the piston stroke is 18 mm, which is same to the cross sectional diameter of the piston, the displacement of the pump per rotation of shaft is 13.77 cc, so the shaft rotational speed required to pump fuel at 300 cc/min is 21.8 rpm.
  • FIG. 1 shows the cross-sectional view of an embodiment of a diesel engine fuel injection pump equipped with all-metal-seal rings on the pistons in accordance to the presently claimed invention.
  • all-metal-seal rings are used for the sealing of the piston and the cylinder bore of a diesel engine fuel injection pump.
  • the diesel engine fuel injection pump equipped with one or more all-metal-seal rings on the pistons can produce absolute zero internal leakage even at very low speed such as 20 rpm.
  • a cylinder bore of a fuel injection pump having a 18 mm cross sectional diameter has a the cross section area of 2.55 square cm.
  • the fuel injection pump has three pistons and if the piston stroke is 18 mm, which is same to the cross sectional diameter of the piston, the displacement of the pump per rotation of shaft is 13.77 cc, so the shaft rotational speed required to pump fuel at 300 cc/min is 21.8 rpm.
  • An embodiment of a diesel engine fuel injection pump equipped with all-metal-seal rings on the pistons comprises: a pump drive shaft 31 and an eccentric cam 30 , wherein the pump drive shaft 31 and the eccentric cam 30 are made into a single piece and is assembled into a pump body 16 .
  • a three-rod-piston-drive cam 28 is assembled on to the eccentric cam 30 , backed up by a bearing 29 .
  • Each of the three cylinder heads 17 comprises a discharge valve 22 , a discharge port 26 , and a pump piston 19 inserted in a cylinder bore.
  • the cylinder heads 17 is attached to the pump body 16 and are positioned evenly around the circular pump body.
  • the cylinder heads 17 are further fastened to the pump body 16 by tie bolts 18 .
  • Rotation of the pump drive shaft 31 rotates the eccentric cam 30 and together creates a reciprocal motion on the piston drive cam 28 .
  • the piston drive cam 28 pushes up each of the pump pistons 19 into its respective cylinder bore.
  • the pump piston 19 then is returned by the force of a return spring 21 .
  • the reciprocation of pump piston 19 created by the piston drive cam 28 creates the pumping force, suction force, and compression force.
  • the action of a suction valve 23 and the discharge valve 22 during the reciprocation of the pump piston 19 causes liquid fuel to flow into pump body 16 through the inlet port 24 and hole 25 inside of the pump piston 19 .
  • CFS coiled felt seal
  • FIG. 2 Partial ring which could be press stamped out of thin metal sheet, that having male and female dovetail joint shape on two ends to make the joints be strong when progressively joined.
  • FIG. 3 Two partial rings are overlapped to insert male dovetail of first partial ring into female dovetail of next partial ring for progressive joining to construct helical wound tube.
  • FIG. 4 Blank of the tubular shape seal of this invention, which is metal strap wound helical tube.
  • FIG. 5 Partially cutaway view of completed dynamic seal of this invention which is completed by grinding the inside and outside diameter of the blank to have proper function in the seal.
  • FIG. 6 A partial ring with assisting imaginary parts to explain the dynamic rotary seal principle with this invention.
  • FIG. 7 Half cutaway view of example of completed dynamic rotary seal using this invention.
  • Helical spring tube constructed by progressive joining of number of C-type partial rings along the helical track.
  • Category of this invention falls in the dynamic blocking technology of the leak that inevitably arising between stationary housing and rotating shaft when pressure rises in the rotary compression system.
  • the dynamic rotary seal used on screw type compression system is called “mechanical seal”.
  • a mechanical seal is composed of six parts in minimum, which are the stator block, rotor block, stator disk, rotor disk, rotor disk spring and rotor block disk seal. The entire seal function fails if any one of these parts fails.
  • the stator disk and the rotor disk are the parts that perform the actual sealing function by contacting rubbing rotating under pressure. Those two parts must have not only high wear resistance but also low friction. They must be able to dissipate heat in possible highest speed. Surface area can be adjusted for less contacting area for less friction heat but the less area results faster wear out.
  • High wear resistant materials have high friction but low friction material having low wear resistance. If they are made with high wear resistant material for long life the friction heat could affect the quality of the media in contact, in some cases even bring fire.
  • Two contacting faces in mechanical seal are under pressure and constantly rubbing so they are wearing in all instance even submicron unit range but that submicron wear clearance always causes whole seal failure when the submicron wear is not compensated in every instance along with wear out.
  • one of the contacting disk, rotating disk must move toward the mating disk, the stationary disk, to compensate wear.
  • the rotating disk must travel axial direction toward the stationary disk on the rotating block while the rotating block is rotating.
  • Rotating disk must be able to slide on the rotating block to constantly move toward the stationary disk. Thus there is another place to block leak between rotating disk and rotating block.
  • a rubber O-ring inserted between rotating disk and rotor block shall be burnt in high temperature media and shall be extruded under high pressure media and be attacked in the corrosive media but there are no ways to omit it.
  • Metal bellows are more expensive, sometimes three times of the whole mechanical seal, and the metal bellows makes complicate structure which hinders thin compact design that is very important in precision machines.
  • the ultimate target is to produce single piece rotary dynamic seal which is compact, higher sealing performance, cheaper and lower maintenance while the rotary dynamic sealing system of prior art which generally called mechanical seal having so many parts are inevitably inter related, complicate structure, expensive in production cost, higher maintenance cost and shorter life.
  • FIG. 2 shows the C-shaped partial ring ( 1 ) which is the basic source ring of this invention.
  • Partial ring ( 1 ) must be stamped out by press or fabricated by contour cutting process such as laser cutting or wire cutting from sheet stock to have two faces of partial ring ( 1 ) in perfect parallel.
  • C-shaped partial ring ( 1 ) is a ring that made to have a part of the ring cut away so as to make the partial rings be progressively joined by the male dovetail( 2 ) and female dovetail ( 3 ) made on two ends of the partial ring ( 1 ).
  • the value of the cut away angle should be determined accordingly along with diameter.
  • FIG. 3 shows the method of progressive joining of two partial rings ( 1 ) by the male dovetail ( 2 ) of first partial ring ( 1 ) and female dovetail ( 3 ) of next partial ring ( 1 ).
  • FIG. 4 shows the completed helical spring tube ( 5 ) by progressive joining of partial rings ( 1 ) and those dovetail joint line ( 4 ) must be permanently set by welding or brazing after joining
  • the starting point shows the male dovetail ( 2 ) and the ending point shows female dovetail ( 3 ) on completed helical spring tube ( 5 ).
  • the dovetail joint line( 4 ) shall be distributed on the tube surface on shifted point as much as the cutaway angle of the partial ring ( 1 ) so the dovetail joint line ( 4 ) will be adequately distributed on tube surface evading weak joint points be overlapped.
  • FIG. 5 shows the partial cutaway view of seal assembly ( 24 ) which is completed sealing ring of this invention.
  • the seal assembly ( 24 ) is completed by grinding of inner diameter and outer diameter by making 4 different diameters, two on inside and two on outside of the helical spring tube ( 5 ).
  • the smaller diameter of the inside diameter of seal assembly ( 24 ) is called shaft contacting circle ( 7 ) which is made about 0.5% smaller than the outside diameter of the shaft ( 23 ) so as to tightly contact with shaft ( 13 ) all the time when the shaft ( 13 ) is inserted inside of the seal assembly ( 24 ).
  • the larger diameter of the inside diameter of seal assembly ( 24 ) is called shaft free circle ( 6 ) which made little larger than the outside diameter of the shaft ( 23 ) so as to prevent shaft free circle ( 6 ) from contacting outside diameter of the shaft ( 23 ) at anytime.
  • the larger diameter of the outside diameter of seal assembly ( 24 ) is called housing contact circle ( 8 ) which is made about 0.5% larger than the inside diameter of the housing ( 18 ) so as to keep the housing contact circle ( 8 ) tightly contact all the time with inside diameter of the housing ( 18 ) when the seal assembly ( 24 ) is assembled inside of the housing ( 17 ).
  • the smaller diameter of the outside diameter of the seal assembly ( 24 ) is called housing free circle ( 9 ) which made little smaller than the inside diameter of the housing ( 18 ) to prevent the housing free circle ( 9 ) from contacting the inside diameter of the housing ( 18 ) at anytime.
  • the purpose of making these 4 different diameter circle is to build three different functioned layers in the seal assembly ( 24 ).
  • the first layer is called housing seal layer ( 10 ), which is the stacking of the housing seal rings whose outside diameter is housing contact circle ( 8 ) and inside diameter is shaft free circle ( 6 ).
  • the function of the housing seal layer is blocking the leak between inside diameter of the housing ( 18 ) and seal assembly ( 24 ) and the number of the rings to construct layer for optimum sealing performance shall be determined by designer according to different sizes.
  • the second layer is called shaft seal layer ( 12 ) which is the stacking of the shaft seal rings whose outside diameter is housing free circle ( 9 ) and inside diameter is shaft contact circle ( 7 ).
  • the function of the shaft seal layer is blocking the leak between outside diameter of the shaft ( 23 ) and seal assembly ( 24 ) and the number of the rings to construct layer for optimum sealing performance shall be determined by designer according to different sizes.
  • the third layer is called displacement absorption layer ( 11 ) which is stacking of the suspended rings whose outside diameter is housing free circle ( 9 ) and the inside diameter is shaft free circle ( 6 ).
  • the displacement absorption layer ( 11 ) is built between the housing seal layer ( 10 ) and the shaft seal layer ( 12 ) to absorb eccentric vibration of the shaft and also absorbs the dimensional change of the whole system by wearing along with use.
  • FIG. 6 shows the principle of the sealing of this invention. Since those three different functioned layers are constructed on a single strand of metal strap any force put to any point of the seal assembly ( 24 ) is immediately affects to all over the seal assembly ( 24 ).
  • the seal assembly ( 24 ) is inserted inside of the housing ( 17 ) with force the seal assembly ( 24 ) is tightly caught inside of the housing ( 17 ) because the outmost diameter of the seal assembly ( 24 ) is the housing contact circle ( 8 ) which is 0.5% larger than the inside diameter of the housing ( 18 ).
  • the housing seal layer ( 10 ) is tightly caught to the housing ( 17 ) whole seal assembly ( 24 ) is caught in the housing ( 17 ) so is the shaft seal layer ( 12 ).
  • the innermost diameter of the seal assembly ( 24 ) which is the inner diameter of the shaft seal layer ( 12 ) is shaft contact circle ( 7 ) which is made about 0.5% smaller than the outside diameter of the shaft ( 23 ) so if the shaft ( 13 ) is inserted into shaft seal layer ( 12 ) by force whole shaft seal layer ( 13 ) must be tightly stick to shaft ( 13 ). If the shaft ( 13 ) starts rotate the shaft seal layer ( 12 ) also starts to rotate together with shaft ( 13 ) but the housing seal layer ( 10 ) which is tightly caught inside of the housing ( 17 ) prevents the shaft seal layer ( 12 ) from rotating.
  • This condition is as same as the FIG. 6 that shows one partial ring of the shaft seal layer ( 12 ) is about to start rotate by the rotating force of the shaft ( 13 ), the stopping action of the housing seal layer ( 10 ) is shown by imaginary stop pin ( 16 ).
  • the shaft contact circle( 7 ) is holding shaft diameter ( 23 ) but the shaft ( 13 ) starts to rotate to arrow ( 14 ) direction while the stop pin ( 16 ) prevents the ring ( 12 ) from rotate, then the friction force between shaft contact circle( 7 ) and shaft diameter ( 23 ) is converted to open the partial ring ( 12 ) to the arrow ( 15 ) direction.
  • FIG. 7 is the representative drawing which shows the cutout view of completed dynamic rotary seal using seal assembly ( 24 ).
  • seal assembly ( 24 ) There must be some means to hold the seal assembly ( 24 ) inside the cylinder ( 17 ) including holding ring ( 20 ) and snap ring ( 19 ) which is inserted in the snap ring groove ( 25 ).
  • the compression ring ( 21 ) also provided to push source rings together to block leak between source rings by the spring force of the compression springs ( 22 ) which inserted in the holes made on the compression ring ( 21 ).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Sealing Devices (AREA)
US13/548,222 2011-07-14 2012-07-13 Diesel engine fuel injection pump which pistons are sealed with all metal seal rings Abandoned US20130017107A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US13/548,222 US20130017107A1 (en) 2011-07-14 2012-07-13 Diesel engine fuel injection pump which pistons are sealed with all metal seal rings

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201161508048P 2011-07-14 2011-07-14
US13/548,222 US20130017107A1 (en) 2011-07-14 2012-07-13 Diesel engine fuel injection pump which pistons are sealed with all metal seal rings

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US (1) US20130017107A1 (zh)
CN (1) CN202937392U (zh)
WO (1) WO2013010458A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190003406A1 (en) * 2016-05-26 2019-01-03 Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland Large two-stroke compression-ignited internal combustion engine with fuel injection system for low flashpoint fuel and a fuel valve therefore
US11255319B2 (en) * 2019-03-09 2022-02-22 Neo Mechanics Limited Shaft-cylinder assembly for high temperature operation

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI564494B (zh) * 2014-05-20 2017-01-01 昱曦機械高新科技有限公司 往復式內燃機及活塞汽缸連桿總成
TW201615301A (zh) * 2014-07-28 2016-05-01 昱曦機械高新科技有限公司 製造螺旋彈簧式密封件的方法及其製造裝置

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US206695A (en) * 1878-08-06 Improvement in packings for steam-engines
US484188A (en) * 1892-10-11 Frank k ethridge
US2325196A (en) * 1940-01-13 1943-07-27 Coil Piston Ring Company Of Am Piston ring
US4333661A (en) * 1980-12-05 1982-06-08 Hughes Aircraft Company Expanding helical seal for pistons and the like
US4576381A (en) * 1984-11-23 1986-03-18 Rix Industries Spiral piston ring with tapered ends and recesses
US5980214A (en) * 1997-09-12 1999-11-09 Stanadyne Automotive Corp. Fluid pump with split plungers
KR100688250B1 (ko) * 2006-04-07 2007-03-02 장경태 다수(多數)의 C-형 부분환(部分環)(C-type partial ring)을열장이음(Dovetail join) 방식으로 연결하여 나선을 따라감긴 관 형태로 성형한 회전체 동적 밀봉 장치.
US7210463B2 (en) * 2002-08-29 2007-05-01 Robert Bosch Gmbh Pump, especially for a fuel injection device for an internal combustion engine

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US3682572A (en) * 1970-07-27 1972-08-08 Donald L Yarger Piston type pump
DE19523283B4 (de) * 1995-06-27 2006-01-19 Robert Bosch Gmbh Pumpe, insbesondere Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung eines Verbrennungsmotors
DE10139519A1 (de) * 2001-08-10 2003-02-27 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung, sowie Verfahren zum Betreiben einer Brennkraftmaschine, Computerprogramm und Steuer- und/oder Regelgerät
DE10302043A1 (de) * 2002-10-31 2004-05-19 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit Kugelventil im Niederdruck-Einlass
JP4625789B2 (ja) * 2006-07-20 2011-02-02 日立オートモティブシステムズ株式会社 高圧燃料ポンプ
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US206695A (en) * 1878-08-06 Improvement in packings for steam-engines
US484188A (en) * 1892-10-11 Frank k ethridge
US2325196A (en) * 1940-01-13 1943-07-27 Coil Piston Ring Company Of Am Piston ring
US4333661A (en) * 1980-12-05 1982-06-08 Hughes Aircraft Company Expanding helical seal for pistons and the like
US4576381A (en) * 1984-11-23 1986-03-18 Rix Industries Spiral piston ring with tapered ends and recesses
US5980214A (en) * 1997-09-12 1999-11-09 Stanadyne Automotive Corp. Fluid pump with split plungers
US7210463B2 (en) * 2002-08-29 2007-05-01 Robert Bosch Gmbh Pump, especially for a fuel injection device for an internal combustion engine
KR100688250B1 (ko) * 2006-04-07 2007-03-02 장경태 다수(多數)의 C-형 부분환(部分環)(C-type partial ring)을열장이음(Dovetail join) 방식으로 연결하여 나선을 따라감긴 관 형태로 성형한 회전체 동적 밀봉 장치.

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20190003406A1 (en) * 2016-05-26 2019-01-03 Man Diesel & Turbo, Filial Af Man Diesel & Turbo Se, Tyskland Large two-stroke compression-ignited internal combustion engine with fuel injection system for low flashpoint fuel and a fuel valve therefore
US10344686B2 (en) 2016-05-26 2019-07-09 Man Energy Solutions, Filial Af Man Energy Solutions Se, Tyskland Large two-stroke compression-ignited internal combustion engine with fuel injection system for low flashpoint fuel and a fuel valve therefore
US10400682B2 (en) * 2016-05-26 2019-09-03 Man Energy Solutions, Filial Af Man Energy Solutions Se, Tyskland Large two-stroke compression-ignited internal combustion engine with fuel injection system for low flashpoint fuel and a fuel valve therefore
US10400683B2 (en) 2016-05-26 2019-09-03 Man Energy Solutions, Filial Afman Energy Solutions Se, Tyskland Large two-stroke compression-ignited internal combustion engine with fuel injection system for low flashpoint fuel and a fuel valve therefore
US11255319B2 (en) * 2019-03-09 2022-02-22 Neo Mechanics Limited Shaft-cylinder assembly for high temperature operation

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WO2013010458A1 (en) 2013-01-24

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