WO2013010458A1 - Pompe d'injection de carburant de moteur diesel dont les pistons sont étanchéifiés à l'aide de bagues d'étanchéité entièrement métalliques - Google Patents

Pompe d'injection de carburant de moteur diesel dont les pistons sont étanchéifiés à l'aide de bagues d'étanchéité entièrement métalliques Download PDF

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Publication number
WO2013010458A1
WO2013010458A1 PCT/CN2012/078644 CN2012078644W WO2013010458A1 WO 2013010458 A1 WO2013010458 A1 WO 2013010458A1 CN 2012078644 W CN2012078644 W CN 2012078644W WO 2013010458 A1 WO2013010458 A1 WO 2013010458A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
seal
shaft
piston
metal
Prior art date
Application number
PCT/CN2012/078644
Other languages
English (en)
Inventor
Kyong Tae Chang
Original Assignee
Neo Mechanics Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Neo Mechanics Limited filed Critical Neo Mechanics Limited
Publication of WO2013010458A1 publication Critical patent/WO2013010458A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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 todiesel engines, diesel engine fuel injection pumps,and related mechanical parts. More specifically, the presently claimed invention relates to thesealing 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 rated load then becomes 5,293 kg when a 50% safety factor is accounted for. Thisrequires 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.
  • the pump shaft rotates at 370 rpm to pump 300 cc/min.
  • the outer diameter of the piston cannotexceed 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 rap idly during the life of the pump. It is becausethe 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 aconstant 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 orderto 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 ringson 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/minis 21.8 rpm.
  • FIG.l 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,whereinthe pump drive shaft 31 and the eccentric cam 30are made into a single piece and is assembledintoa 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 thethree cylinder heads 17 comprises a discharge valve22,a discharge port 26, and a pump piston 19 inserted in a cylinder bore.
  • the cylinder heads 17 is attachedtothe pump body 16and are positioned evenly around the circularpump body.
  • the cylinder heads 17 are further fastenedto the pump body 16by tie boltsl8.
  • Rotation of the pump drive shaft31 rotates the eccentric cam 30and together creates a reciprocal motion on the piston drive cam28.
  • the piston drive cam28 pushesup each ofthe pump pistons 19 into its respective cylinder bore.
  • the pump pistonl9 then is returned by the force of a return spring21.
  • the reciprocation of pump pistonl9created by the piston drive cam28 createsthe pumping force, suction force, and compression force.
  • the action of a suction valve23 and the discharge valve22 during the reciprocation of the pump pistonl9 causes liquid fueltoflow into pump bodyl6 through the inlet port24 and hole 25inside of the pump pistonl9.
  • 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.
  • FIG. 2 - 7 Explanation of numbered parts in the drawings FIG. 2 - 7:
  • 5- 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".
  • Amechanical 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.
  • 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.
  • Rotating disk must be able to slide on the rotating block to constantly move toward the stationary disk.
  • the axial direction movement of the rotating disk on the rotating block by wear out of disk is very little distance, within few mm in a year, so the sealing between rotating disk and rotating block could be satisfied by simple rubber O-ring for cheaper model and by metal bellows for higher performance.
  • the real problem in rotary dynamic seal in prior art is in the sealing between rotating disk and rotor block, not only in contacting disks.
  • 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(l) which is the basic source ring of this invention.
  • Partial ring(l) 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(l) in perfect parallel.
  • C-shaped partial ring(l) 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(l).
  • 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(l) by the male dovetail(2) of first partial ring(l) and female dovetail(3) of next partial ring(l).
  • FIG. 4 shows the completed helical spring tube(5) by progressive joining of partial rings(l) 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(l) 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(lO), 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(l l) 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(l 1) is built between the housing seal layer(lO) 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(lO) which is tightly caught inside of the housing(17) prevents the shaft seal layer(12) from rotating.
  • No more contact means no more friction force generates so opening of the ring(12) is ended and spring back to its original position.
  • Back to its original position of the ring(12) means the contacting of the ring(12) and shaft(13) and next instance the friction force opens the ring(12) again.
  • the opening between the ring(12) and the shaft(13) could be a millionths of a mm since the open is open no matter how small value was the opening which is enough distance to eliminate contacting. So the open and close of the ring(12) could arise million times in a second in other words the opening clearance also could be millionths of a mm through which nothing can be leak in a millionths of a second.
  • This condition is as same as the static seal of plain rubber O-ring since the contacting of ring(12) and shaft(13) is virtually never broken during the rotating of the shaft(13).
  • This status is a unique phenomenon arising between helical spring and rotating round bar inserted inside of the spring, the condition should be called contacting non contacting condition.
  • This contacting non-contacting phenomenon is utilized on helical spring over running clutch from long time ago but utilizing this phenomenon on dynamic seal is the first on this invention.
  • 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)

Abstract

L'invention concerne une pompe d'injection de carburant qui comprend un corps de pompe (16), un arbre d'entraînement (31) assemblé au corps de pompe, une came d'entraînement du piston (30) montée sur l'arbre d'entraînement, et une ou plusieurs culasses (17), chacune des culasses comprenant un piston de pompe (19) introduit dans un alésage de cylindre, le piston de pompe étant équipé d'une ou plusieurs bagues d'étanchéité entièrement métalliques (20), le piston de pompe qui est équipé d'une ou plusieurs bagues d'étanchéité entièrement métalliques possédant une superficie transversale qui est la même que celle de l'alésage de cylindre, ce qui ne crée ainsi aucune fuite interne. Dans un mode de réalisation, les bagues d'étanchéité entièrement métalliques sont des joints en feutre hélicoïdal. La pompe d'injection de carburant peut travailler à basse vitesse, ce qui prolonge la durée de vie de la pompe, garantit une haute performance constante de la pompe sur toute sa durée de vie et amortit les vibrations du moteur diesel, ce qui assure une conduite plus silencieuse et plus confortable du véhicule.
PCT/CN2012/078644 2011-07-14 2012-07-13 Pompe d'injection de carburant de moteur diesel dont les pistons sont étanchéifiés à l'aide de bagues d'étanchéité entièrement métalliques WO2013010458A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201161508048P 2011-07-14 2011-07-14
US61/508,048 2011-07-14

Publications (1)

Publication Number Publication Date
WO2013010458A1 true WO2013010458A1 (fr) 2013-01-24

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PCT/CN2012/078644 WO2013010458A1 (fr) 2011-07-14 2012-07-13 Pompe d'injection de carburant de moteur diesel dont les pistons sont étanchéifiés à l'aide de bagues d'étanchéité entièrement métalliques

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Country Link
US (1) US20130017107A1 (fr)
CN (1) CN202937392U (fr)
WO (1) WO2013010458A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015176649A1 (fr) * 2014-05-20 2015-11-26 Neo Mechanics Limited Ensemble piston-cylindre-bielle de moteur alternatif à combustion interne
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
DK179161B1 (en) * 2016-05-26 2017-12-18 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland A 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

Citations (6)

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Publication number Priority date Publication date Assignee Title
US3682572A (en) * 1970-07-27 1972-08-08 Donald L Yarger Piston type pump
US5876186A (en) * 1995-06-27 1999-03-02 Robert Bosch Gmbh High pressure pump for a fuel injection device
EP1283366B1 (fr) * 2001-08-10 2005-11-09 Robert Bosch Gmbh Pompe à pistons radiaux et méthode de contròle
CN1711417A (zh) * 2002-10-31 2005-12-21 罗伯特·博世有限公司 在低压入口中设有球阀的燃料高压泵
CN101109347A (zh) * 2006-07-20 2008-01-23 株式会社日立制作所 高压燃料泵
EP1985853A1 (fr) * 2007-04-17 2008-10-29 Golle Motor AG Pompe à piston radial, en particulier pour systèmes d'injection Common Rail (CR)

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US484188A (en) * 1892-10-11 Frank k ethridge
US206695A (en) * 1878-08-06 Improvement in packings for steam-engines
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
DE10239728A1 (de) * 2002-08-29 2004-03-11 Robert Bosch Gmbh Pumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
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.

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3682572A (en) * 1970-07-27 1972-08-08 Donald L Yarger Piston type pump
US5876186A (en) * 1995-06-27 1999-03-02 Robert Bosch Gmbh High pressure pump for a fuel injection device
EP1283366B1 (fr) * 2001-08-10 2005-11-09 Robert Bosch Gmbh Pompe à pistons radiaux et méthode de contròle
CN1711417A (zh) * 2002-10-31 2005-12-21 罗伯特·博世有限公司 在低压入口中设有球阀的燃料高压泵
CN101109347A (zh) * 2006-07-20 2008-01-23 株式会社日立制作所 高压燃料泵
EP1985853A1 (fr) * 2007-04-17 2008-10-29 Golle Motor AG Pompe à piston radial, en particulier pour systèmes d'injection Common Rail (CR)

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US20130017107A1 (en) 2013-01-17
CN202937392U (zh) 2013-05-15

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