EP1234975B1 - Hochdruck-Kolbenzylindereinheit - Google Patents

Hochdruck-Kolbenzylindereinheit Download PDF

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Publication number
EP1234975B1
EP1234975B1 EP02405048A EP02405048A EP1234975B1 EP 1234975 B1 EP1234975 B1 EP 1234975B1 EP 02405048 A EP02405048 A EP 02405048A EP 02405048 A EP02405048 A EP 02405048A EP 1234975 B1 EP1234975 B1 EP 1234975B1
Authority
EP
European Patent Office
Prior art keywords
piston
accordance
cylinder
transverse groove
pressure
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.)
Expired - Lifetime
Application number
EP02405048A
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German (de)
English (en)
French (fr)
Other versions
EP1234975A2 (de
EP1234975A3 (de
Inventor
Roland Alder
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.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP02405048A priority Critical patent/EP1234975B1/de
Publication of EP1234975A2 publication Critical patent/EP1234975A2/de
Publication of EP1234975A3 publication Critical patent/EP1234975A3/de
Application granted granted Critical
Publication of EP1234975B1 publication Critical patent/EP1234975B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the invention relates to a high-pressure piston-cylinder unit according to the Preamble of claim 1.
  • Document WO 89/10479 discloses a high-pressure piston-cylinder unit, which as a high-pressure pump such as High-pressure pump of a diesel engine is suitable.
  • a high-pressure pump such as High-pressure pump of a diesel engine is suitable.
  • High-pressure feed pumps are of the order of magnitude for injection pressures designed by 1000 bar and more. In the operation of such high-pressure feed pumps Due to the high material load, there is a risk that the piston seizes in the guide of the cylinder.
  • a disadvantage of the known high-pressure feed pump is the fact that at high pressures and / or at a high stroke frequency the risk of Seizing up.
  • a high-pressure piston-cylinder unit to form which also at very high pressures and / or stroke frequencies no tendency to seizure of the piston in the Leadership of the cylinder has.
  • a high-pressure piston-cylinder unit comprising a cylinder with a cylinder bore and a piston movably guided therein in a displacement direction, the cylinder opening into the cylinder bore Having fuel supply, and wherein the cylinder bore between the fuel supply port and the low-pressure end one Has bore length, and wherein the piston or the cylinder bore has at least a first and a second transverse groove, which in Displacement direction are arranged spaced such that the first Transverse groove via a connecting channel fluid-conducting with the Fuel supply port is connected, and that the second transverse groove over a connection channel fluid-conducting with the low-pressure end connected is.
  • the first and second transverse grooves are preferably around a sealing length spaced, which is shorter than the bore length.
  • This arrangement has the advantage that the bore length for guiding the piston is designed relatively long, allowing a safe guiding of the piston allows, and that the sealing length is made relatively short, so that a sufficiently large leakage between the Brennstoffzu fürö réelle and the low-pressure end occurs. This leakage allows the piston and the To cool cylinder and / or lubricate so that a hot run the Pump or even eroding the piston is avoided.
  • the High-pressure piston-cylinder unit according to the invention also has the Advantage that they have a high stroke frequency or with a high capacity is operable without excessive wear occurs.
  • the sealing length is about 5 mm, while the bore length is for example 100 mm, so that the Sealing length is significantly shorter than the bore length is designed.
  • the transverse groove is preferably designed annular, which gives the advantage that the fuel and thus also caused by the fuel Pressure distributed over the circumference of the transverse groove, causing the piston in the cylinder is centered.
  • the transverse groove has the property that is in it Collect dirt particles, so that these dirt particles are not or hardly move inside the cylinder.
  • Fig. 1 shows a high-pressure piston-cylinder unit 1 comprising a Cylinder 3 with a cylinder bore 3a and a therein in Displacement direction V movably guided piston 2.
  • Two Fuel supply ports 3b open into the cylinder bore 3a.
  • the piston 2 compresses the incoming via the fuel supply ports 3b Fuel in the direction of the high pressure side 3c of the cylinder 3.
  • Am opposite, low-pressure end 3c of the cylinder is located preferably an atmospheric pressure.
  • the outer surface of the piston 2 has a first transverse groove 2c and a second transverse groove 2d on which a sealing length D each other are spaced.
  • these transverse grooves 2c, 2d are such arranged that they move in every position of the up and down Piston 2 within the cylinder bore 3a between the Fuel supply opening 3b and the low-pressure end to lie 3d come.
  • the first transverse groove 2c is over a first, groove-shaped Connecting channel 2b fluid-conducting with the fuel supply port 3b connected.
  • the second transverse groove 2d is via a second, groove-shaped Connecting channel 2f fluid-conducting with the low-pressure end 3d connected.
  • the first groove-shaped connecting channel 2b is arranged in such a way that that at least in the uppermost stroke position of the piston 2 is a fluid-conducting Connection to the fuel supply opening 3b, so that the pressure in first connecting channel 2b during the entire stroke of the piston 2 maximum the pressure of the fuel in the fuel supply port 3b corresponds, so that the pressure in the first transverse groove 2c substantially corresponds to the fluid pressure in the fuel supply port 3b.
  • the second Connecting channel 2f is arranged such that constantly a connection to the low pressure end 3d exists, so in the second Connecting channel 2f and in the second transverse groove 2d substantially the atmospheric pressure is applied.
  • the pressure of fuel in the Brennstoffzu Foodö réelle 3b is beispeilitate 5 bar, so between the first transverse groove 2c and the second transverse groove 2d a pressure difference of essentially 5 bar is applied.
  • the sealing length D is preferably very short designed, for example, 5 mm, so that between the first and the second transverse groove 2c, 2d a sufficiently large leakage is guaranteed to to cause sufficient cooling and hot running or a To avoid seizing the piston 2.
  • the piston 2 has a plurality between the fuel supply port 3b and the first transverse groove 2c mutually complained, circular transverse grooves 2a, which all fluidly connected to the connecting channel 2b.
  • This arrangement has the advantage that over the circumference of a respective transverse groove 2a a Pressure equalization is achieved, which evenly over the piston circumference acts on the piston 2 and this with respect to the cylinder bore 3a centered.
  • the piston 2, in the position shown in Fig. 1 between the Fuel supply opening 3b and the free end 2h of the piston 2 a A plurality of uniformly spaced transverse grooves 2a. These are preferably arranged such that during the entire stroke of the piston 2 all the aforementioned transverse grooves 2a with the Fuel supply opening 3b fluidly connect, so that in These transverse grooves 2a a relatively low pressure is applied, whereas at the Front side of the free end 2h of the piston 2, a pressure of example 1000 bar is applied.
  • This ensures that the pressure of the fuel in the fuel supply port 3b by the high pressure at the end of the free end 2h hardly or not affected, which has the consequence that the Pressure difference between the fuel supply port 3b and the Low-pressure end 3d has an approximately constant value. Thereby the leakage between the fuel supply port 3b and the Low-pressure end 3d independent of the pressure on the front of the free end 2h.
  • the above-mentioned transverse grooves 2a in the displacement direction V on a mutual distance which is smaller than the diameter of the fuel supply port 3b.
  • Fig. 3 shows in a section along the line A-A a cross section of Cylinder 3 and the piston 2, wherein also the annular transverse groove 2a and the connecting channel 2b can be seen.
  • Fig. 4 shows in a longitudinal section a high-pressure pump 4 for Internal combustion engines, in particular large diesel engines.
  • the high-pressure piston-cylinder unit 1 is within the high pressure feed pump. 4 arranged.
  • the piston 2 performs a pumping movement in Shifting direction V out by this slides up and down, while the Fuel supply opening 3b opens or covering, to a pressure stroke perform.
  • the fuel is thereby conveyed into the high pressure space 4f and passes through the high pressure valves 4b, which when reaching a Open boundary high pressure, in the high pressure chamber 4a.
  • the lifting movement is by a plunger 4e in the clamped end 2e of the piston. 2 introduced, the plunger 4e videspieslweise by a not shown Cam is driven.
  • the retrograde movement of the piston 2 is through the return spring 4d initiated.
  • An advantage of the high pressure feed pump 4 is the fact that the High-pressure piston-cylinder unit 1 with a high number of strokes per Time unit is operable without a hot run or a seizure occurs. Thus, it is possible during filling of the high pressure chamber 4a to operate the high pressure feed pump 4 at maximum speed.
  • the fuel is introduced via an inlet opening 4c of the fuel supply opening 3b forwarded.
  • the piston 2 is arranged in a known manner such that this order its longitudinal axis is rotatably mounted.
  • the piston 2 preferably has an oblique control edge, which in conjunction with a undercut piston skirt surface and the end face of the piston 2 a Volume control allows.
  • the Cross section of the fuel supply opening 3b as for example in a Suction choke is executed.
  • a groove-free piston 2 wherein the transverse grooves 2a, the first and second transverse groove 2c, 2d and the first and second Connecting channel 2b, 2f as a recess of the cylinder bore 3a are designed.
  • the between the Brennstoffzu Foodö réelle 3b and the Quernut 2c seconded section of the cylinder bore 3a could also along the entire section a larger diameter than the Have piston 2, so that this section between the Brennstoffzu Switzerlandö réelle 3b and the transverse groove 2c is a hollow cylindrical Connecting channel 2b forms.
  • the cylinder bore 3 a have a larger diameter than the piston 2, so between a hollow cylindrical connecting channel 2 f is formed.
  • Fig. 7 shows a piston 2 with a along the surface thereof helically extending groove 2b, which forms the connecting channel, and which mutually fluid-conductively connects the transverse groove 2c with the transverse groove 2a.
  • the on the back of the piston 2 extending, helical Groove portion is not visible in Fig. 7.
  • the entire groove 2b extends however, helical along the surface of the piston, starting at the Transverse groove 2a and ending at the transverse groove 2c.
  • Fig. 8 shows a longitudinal section through the piston 2 and the cylinder 3, wherein the piston 2 arranged in the center, straight in Displacement direction V extending connecting channel 2b. in the Piston 2 transverse channels 2i are arranged, which conduct a fluid Connection between the connection channel 2b; 2f and the transverse groove 2a, 2c; Form 2d. From the cross section according to FIG. 9, which is a section along the line B-B according to FIG. 8, which is in the center of the piston. 2 extending connecting channel 2b can be seen, which on the transverse channels 2i Fluid is conductively connected to the transverse groove 2a.
  • the connecting channel 2b; 2f could also be arranged running in the cylinder 3, for example by that shown in Fig. 5, embedded in the cylinder bore 3a Transverse grooves 2a, 2c, 2d by a running within the cylinder 3 Connecting channel 2b, 2f with the fuel supply port 3b and / or with the Low-pressure end 3d fluid conductively connected.
  • Fig. 10 shows another embodiment of a cylindrical Piston 2, between the transverse groove 2a and the first transverse groove 2c a smaller cross-sectional area or a reduced Diameter.
  • Cylinder 3 is introduced results along the reduced diameter a connection channel 2b, which fluid the fuel supply 3b conductively connects with the first transverse groove 2c. It thus arises hollow cylindrical connecting channel 2b.
  • the piston could be 2 between the second transverse groove 2d and the low-pressure end 3d to Forming a connection channel 2f a reduced diameter exhibit.
  • the connecting channel (2b; 2f) is preferably at least partially as Recess formed in the surface of the piston (2) and / or the cylinder bore (3a) is inserted and along the same runs.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP02405048A 2001-02-26 2002-01-28 Hochdruck-Kolbenzylindereinheit Expired - Lifetime EP1234975B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP02405048A EP1234975B1 (de) 2001-02-26 2002-01-28 Hochdruck-Kolbenzylindereinheit

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP01810197 2001-02-26
EP01810197 2001-02-26
EP02405048A EP1234975B1 (de) 2001-02-26 2002-01-28 Hochdruck-Kolbenzylindereinheit

Publications (3)

Publication Number Publication Date
EP1234975A2 EP1234975A2 (de) 2002-08-28
EP1234975A3 EP1234975A3 (de) 2004-08-11
EP1234975B1 true EP1234975B1 (de) 2005-11-02

Family

ID=8183760

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02405048A Expired - Lifetime EP1234975B1 (de) 2001-02-26 2002-01-28 Hochdruck-Kolbenzylindereinheit

Country Status (7)

Country Link
EP (1) EP1234975B1 (pl)
JP (1) JP4111716B2 (pl)
KR (1) KR100773437B1 (pl)
CN (1) CN1280537C (pl)
DE (1) DE50204735D1 (pl)
DK (1) DK1234975T3 (pl)
PL (1) PL199298B1 (pl)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006016702A1 (de) * 2006-04-08 2007-10-18 Man Diesel Se Kraftstoffgespülte Kolbenpumpe
DE102006040468A1 (de) * 2006-08-29 2008-03-06 Man Diesel Se Kolbenpumpe mit Ablagerungsschutz
DE102007019909A1 (de) * 2007-04-27 2008-11-06 Man Diesel Se Kraftstoffpumpe
DE102014010718A1 (de) * 2014-07-19 2016-01-21 L'orange Gmbh Kolbenpumpe für ein Kraftstoffeinspritzsystem

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
EP1881189B1 (en) * 2006-07-21 2014-10-29 Continental Automotive GmbH Piston-cylinder system and hydraulic compensation device
JP4650403B2 (ja) * 2006-11-27 2011-03-16 株式会社デンソー サプライポンプ
JP4842293B2 (ja) * 2008-04-02 2011-12-21 株式会社日本自動車部品総合研究所 燃料噴射弁
KR101400580B1 (ko) 2010-01-15 2014-07-01 현대중공업 주식회사 연료분사펌프의 분사장치
KR101219987B1 (ko) 2011-04-28 2013-01-09 현대중공업 주식회사 윤활유 유로를 갖는 플런저를 포함한 연료분사펌프와 이를 구비한 디젤엔진
EP2530316A1 (en) * 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Fuel pump lubrication
EP2530315A1 (en) * 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Fuel pump lubrication
DE102012223334A1 (de) 2012-12-17 2014-06-18 Robert Bosch Gmbh Kolbenzylindereinheit
KR101450771B1 (ko) * 2013-02-25 2014-10-16 한국기계연구원 실린더와 피스톤의 마모방지 구조 및 이를 포함하는 피스톤 펌프
GB201402535D0 (en) * 2014-02-13 2014-04-02 Delphi Int Operations Luxembourg Sarl Fuel pump
DE102015016314A1 (de) * 2015-12-15 2017-06-22 L'orange Gmbh Kolbenpumpe
DE102017207044B4 (de) * 2017-04-26 2023-12-28 Vitesco Technologies GmbH Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem
WO2022030431A1 (ja) * 2020-08-04 2022-02-10 京セラ株式会社 摺動装置、プランジャポンプ、送液装置および液体クロマトグラフィー装置

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT307808B (de) * 1971-04-09 1973-06-12 Friedmann & Maier Ag Einspritzpumpe
WO1989010479A1 (en) * 1988-04-22 1989-11-02 Hei-Tech B.V. High-pressure piston cylinder unit
NL8801198A (nl) * 1988-05-09 1989-12-01 Hei Tech Bv Plunjerpompinrichting.

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006016702A1 (de) * 2006-04-08 2007-10-18 Man Diesel Se Kraftstoffgespülte Kolbenpumpe
DE102006040468A1 (de) * 2006-08-29 2008-03-06 Man Diesel Se Kolbenpumpe mit Ablagerungsschutz
DE102007019909A1 (de) * 2007-04-27 2008-11-06 Man Diesel Se Kraftstoffpumpe
DE102014010718A1 (de) * 2014-07-19 2016-01-21 L'orange Gmbh Kolbenpumpe für ein Kraftstoffeinspritzsystem
DE102014010718B4 (de) * 2014-07-19 2020-03-19 Woodward L'orange Gmbh Kolbenpumpe für ein Kraftstoffeinspritzsystem

Also Published As

Publication number Publication date
JP4111716B2 (ja) 2008-07-02
DK1234975T3 (da) 2005-12-05
EP1234975A2 (de) 2002-08-28
EP1234975A3 (de) 2004-08-11
KR20020070080A (ko) 2002-09-05
PL199298B1 (pl) 2008-09-30
CN1372074A (zh) 2002-10-02
CN1280537C (zh) 2006-10-18
PL352345A1 (en) 2002-09-09
DE50204735D1 (de) 2005-12-08
KR100773437B1 (ko) 2007-11-05
JP2002276508A (ja) 2002-09-25

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