EP1234975A2 - Unité cylindre-piston haute pression - Google Patents

Unité cylindre-piston haute pression Download PDF

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Publication number
EP1234975A2
EP1234975A2 EP02405048A EP02405048A EP1234975A2 EP 1234975 A2 EP1234975 A2 EP 1234975A2 EP 02405048 A EP02405048 A EP 02405048A EP 02405048 A EP02405048 A EP 02405048A EP 1234975 A2 EP1234975 A2 EP 1234975A2
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
pressure
connecting channel
transverse groove
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.)
Granted
Application number
EP02405048A
Other languages
German (de)
English (en)
Other versions
EP1234975B1 (fr
EP1234975A3 (fr
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/fr
Publication of EP1234975A2 publication Critical patent/EP1234975A2/fr
Publication of EP1234975A3 publication Critical patent/EP1234975A3/fr
Application granted granted Critical
Publication of EP1234975B1 publication Critical patent/EP1234975B1/fr
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.
  • the publication WO 89/10479 discloses a high-pressure piston-cylinder unit, which as a high pressure pump such as High pressure feed pump of a diesel engine is suitable.
  • a high pressure pump such as High pressure feed pump of a diesel engine is suitable.
  • High-pressure feed pumps are of the order of magnitude for injection pressures of 1000 bar and more.
  • a disadvantage of the known high-pressure feed pump is the fact that at high pressures and / or at a high stroke frequency there is a risk of Seizure exists.
  • the object of the present invention is a high-pressure piston-cylinder unit to form, which even at very high pressures and / or stroke frequencies no tendency for the piston to seize in the Has leadership of the cylinder.
  • a high-pressure piston-cylinder unit comprising a cylinder with a cylinder bore and a piston movably guided therein in a direction of displacement, the cylinder opening into the cylinder bore Has fuel supply opening, and wherein the cylinder bore between the fuel supply opening and the low-pressure end Has bore length, and wherein the piston or the cylinder bore has at least a first and a second transverse groove, which in Direction of displacement are spaced such that the first Transverse groove fluidly connected to the Fuel supply opening is connected, and that the second transverse groove over a connecting channel fluid-conducting with the low-pressure end connected is.
  • the first and second transverse grooves are preferred by 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 to be relatively long, which means safe guidance of the piston enables, and that the sealing length is relatively short, so that a sufficiently large leakage between the fuel supply opening and the low-pressure end occurs. This leakage allows the piston and the Cooling and / or lubricating cylinders in such a way that overheating of the Pump or even seizing the piston is avoided.
  • the high-pressure piston-cylinder unit according to the invention also has the Advantage on that they with a high stroke frequency or with a high capacity can be operated without excessive wear occurs.
  • the sealing length is approximately 5 mm, whereas the bore length is, for example, 100 mm, so that the Sealing length is significantly shorter than the bore length.
  • the transverse groove is preferably annular, which gives the advantage that the fuel and therefore also that caused by the fuel Pressure is distributed over the circumference of the transverse groove, causing the piston in the cylinder is centered.
  • the transverse groove has the property that it is in it Collect dirt particles so that these dirt particles do not or hardly move within the cylinder.
  • FIG. 1 shows a high-pressure piston-cylinder unit 1 comprising one Cylinder 3 with a cylinder bore 3a and one in Direction of displacement V movably guided piston 2.
  • Two Fuel supply openings 3b open into the cylinder bore 3a.
  • the piston 2 compresses the flowing in via the fuel supply openings 3b Fuel towards the high pressure side 3c of the cylinder 3.
  • Am opposite, low-pressure side end 3c of the cylinder preferably an atmospheric pressure.
  • the outer surface of the cylinder 3 has a first transverse groove 2c and one second transverse groove 2d, which is mutually a sealing length D. are spaced. As shown in Fig. 1, these transverse grooves 2c, 2d are such arranged to move up and down in any position Piston 2 within the cylinder bore 3a between the Fuel supply opening 3b and the low-pressure end 3d to lie come.
  • the first transverse groove 2c is over a first, groove-shaped Connection channel 2b fluid-conducting with the fuel supply opening 3b connected.
  • the second transverse groove 2d is via a second, groove-shaped Connection 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 at least in the uppermost stroke position of the piston 2 a fluid-conducting Connection to the fuel supply opening 3b exists, so that the pressure in the first connecting channel 2b during the entire stroke of the piston 2 maximum the pressure of the fuel in the fuel supply opening 3b corresponds, so that the pressure in the first transverse groove 2c essentially corresponds to the fluid pressure in the fuel supply opening 3b.
  • the second Connection channel 2f is arranged such that a connection is always made to the low-pressure side end 3d, so that in the second Connection channel 2f and in the second transverse groove 2d essentially the atmospheric pressure is present.
  • the pressure of the fuel in the Fuel supply opening 3b is, for example, 5 bar, so that between the first transverse groove 2c and the second transverse groove 2d have a pressure difference of is essentially 5 bar.
  • 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 a hot running or a Avoid seizing of the piston 2.
  • the cylinder 3 has a plurality between the fuel supply opening 3b and the first transverse groove 2c mutually objectionable circular transverse grooves 2a, all of which are fluidly connected to the connecting channel 2b.
  • This arrangement has the advantage that a transverse groove 2a extends over the circumference Pressure equalization is achieved, which is evenly over the piston circumference acts on the piston 2 and this with respect to the cylinder bore 3a centered.
  • the piston 2 has in the position shown in Fig. 1 between the Fuel supply opening 3b and the free end 2h of the piston 2 one A plurality of equally 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 Connect the fuel supply opening 3b in a fluid-conducting manner, so that in these transverse grooves 2a are subjected to a relatively low pressure, whereas the Face of the free end 2h of the piston 2, a pressure of, for example 1000 bar is present.
  • the transverse grooves mentioned above have 2a in the direction of displacement V a mutual distance, which is smaller than the diameter of the fuel supply opening 3b.
  • Fig. 3 shows in a section along the line A-A a cross section of the Cylinder 3 and the piston 2, wherein also the annular transverse groove 2a and the connecting channel 2b can be seen.
  • Fig. 4 shows a longitudinal section of a high-pressure feed pump 4 for Internal combustion engines, especially large diesel engines.
  • the high pressure piston cylinder unit 1 is inside the high pressure feed pump 4 arranged.
  • the piston 2 performs a pumping movement in Direction of displacement V out by sliding this up and down and thereby the Fuel supply opening 3b releases or covers a pressure stroke perform.
  • the fuel is thereby conveyed into the high pressure space 4f and passes through the high pressure valves 4b, which are when a Open high pressure limit, in the high pressure chamber 4a.
  • the lifting movement is by a plunger 4e in the clamped end 2e of the piston 2nd initiated, the plunger 4e example of a not shown Cam is driven.
  • the retrograde movement of the piston 2 is by the return spring 4d initiated.
  • High-pressure feed pump 4 is that the High-pressure piston-cylinder unit 1 with a high number of strokes per Unit of time can be operated without overheating or fretting occurs. It is thus possible during the filling of the high pressure chamber 4a to operate the high-pressure feed pump 4 at maximum speed.
  • the fuel is through an inlet opening 4c of the fuel supply opening 3b forwarded.
  • the piston 2 is arranged in a known manner such that it around its longitudinal axis is rotatably mounted.
  • the piston 2 preferably has a sloping control edge, which in connection with a undercut piston surface and the end face of the piston 2 a Volume control enables.
  • the Cross section of the fuel supply opening 3b is executed.
  • Exemplary embodiment has that shown in Figures 5 and 6 Embodiment a groove free piston 2, the transverse grooves 2a, the first and second transverse grooves 2c, 2d and the first and second Connection channel 2b, 2f as a recess in the cylinder bore 3a are designed.
  • the between the fuel supply port 3b and Transverse groove 2c portion of the cylinder bore 3a could also a larger diameter than that along the entire section Have piston 2, so that this section between the Fuel supply opening 3b and the transverse groove 2c a hollow cylindrical Forms connection channel 2b.
  • the cylinder bore 3a have a larger diameter than the piston 2, so that a hollow cylindrical connecting channel 2f is formed therebetween.
  • Fig. 7 shows a piston 2 with a along its surface helically extending groove 2b, which forms the connecting channel, and which mutually fluidly connects the transverse groove 2c with the transverse groove 2a.
  • the spiral on the back of the piston 2 Groove section 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 with transverse groove 2c.
  • Fig. 8 shows a longitudinal section through the piston 2 and the cylinder 3, wherein the piston 2 is arranged in a straight line in the center thereof Movement direction V extending connecting channel 2b.
  • the Pistons 2 are arranged transverse channels 2i, which conduct a fluid Connection between the connection channel 2b; 2f and the transverse groove 2a, 2c; 2d form. From the cross section according to FIG. 9, which is a section along 8 represents the line B-B in the center of the piston 2 extending connecting channel 2b can be seen, which over the transverse channels 2i Is fluidly connected to the transverse groove 2a.
  • the connecting channel 2b; 2f could also be arranged running in the cylinder 3, for example by 5 shown in the cylinder bore 3a Cross grooves 2a, 2c, 2d by one running inside the cylinder 3 Connection channel 2b; 2f with the fuel supply opening 3b and / or with the low pressure side end 3d fluidly connected.
  • FIG. 10 shows another embodiment of a cylindrical one Piston 2, the one between the transverse groove 2a and the first transverse groove 2c smaller cross-sectional area or a reduced one Has diameter. If this piston 2 in the shown in Figure 1 Cylinder 3 is inserted along the reduced diameter a connection channel 2b, which the fuel supply opening 3b fluid connects with the first transverse groove 2c. So it arises hollow cylindrical connecting channel 2b. Likewise, the piston 2 between the second transverse groove 2d and the low-pressure end 3d Forming a connecting channel 2f a reduced diameter exhibit.
  • the connecting channel (2b; 2f) is preferably at least partially as Designed recess which 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 Unité cylindre-piston haute pression Expired - Lifetime EP1234975B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP02405048A EP1234975B1 (fr) 2001-02-26 2002-01-28 Unité cylindre-piston haute pression

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP01810197 2001-02-26
EP01810197 2001-02-26
EP02405048A EP1234975B1 (fr) 2001-02-26 2002-01-28 Unité cylindre-piston haute pression

Publications (3)

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

Family

ID=8183760

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02405048A Expired - Lifetime EP1234975B1 (fr) 2001-02-26 2002-01-28 Unité cylindre-piston haute pression

Country Status (7)

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

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1881191A3 (fr) * 2006-07-20 2009-04-29 Hitachi, Ltd. Pompe à carburant haute pression
EP2743492A1 (fr) 2012-12-17 2014-06-18 Robert Bosch Gmbh Unité de vérin à piston
EP1881189B1 (fr) * 2006-07-21 2014-10-29 Continental Automotive GmbH Système piston-cylindre et dispositif de compensation hydraulique
WO2015120930A1 (fr) * 2014-02-13 2015-08-20 Delphi International Operations Luxembourg S.À R.L. Pompe à carburant
DE102015016314A1 (de) * 2015-12-15 2017-06-22 L'orange Gmbh Kolbenpumpe
DE102007019909B4 (de) 2007-04-27 2019-07-11 Man Energy Solutions Se Kraftstoffpumpe mit Leckagenuten

Families Citing this family (12)

* 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
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
EP2530315A1 (fr) * 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Lubrification de pompe à carburant
EP2530316A1 (fr) * 2011-06-02 2012-12-05 Delphi Technologies Holding S.à.r.l. Lubrification de pompes à carburant
KR101450771B1 (ko) * 2013-02-25 2014-10-16 한국기계연구원 실린더와 피스톤의 마모방지 구조 및 이를 포함하는 피스톤 펌프
DE102014010718B4 (de) * 2014-07-19 2020-03-19 Woodward L'orange Gmbh Kolbenpumpe für ein Kraftstoffeinspritzsystem
DE102017207044B4 (de) * 2017-04-26 2023-12-28 Vitesco Technologies GmbH Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem
WO2022030431A1 (fr) * 2020-08-04 2022-02-10 京セラ株式会社 Dispositif de coulissement, pompe à plongeur, dispositif d'alimentation en liquide et dispositif de chromatographie en phase liquide

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989010479A1 (fr) 1988-04-22 1989-11-02 Hei-Tech B.V. Unite de cylindre et piston a haute pression

Family Cites Families (2)

* 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
NL8801198A (nl) * 1988-05-09 1989-12-01 Hei Tech Bv Plunjerpompinrichting.

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1989010479A1 (fr) 1988-04-22 1989-11-02 Hei-Tech B.V. Unite de cylindre et piston a haute pression

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1881191A3 (fr) * 2006-07-20 2009-04-29 Hitachi, Ltd. Pompe à carburant haute pression
US8382458B2 (en) 2006-07-20 2013-02-26 Hitachi, Ltd. High-pressure fuel pump
EP1881189B1 (fr) * 2006-07-21 2014-10-29 Continental Automotive GmbH Système piston-cylindre et dispositif de compensation hydraulique
DE102007019909B4 (de) 2007-04-27 2019-07-11 Man Energy Solutions Se Kraftstoffpumpe mit Leckagenuten
EP2743492A1 (fr) 2012-12-17 2014-06-18 Robert Bosch Gmbh Unité de vérin à piston
DE102012223334A1 (de) 2012-12-17 2014-06-18 Robert Bosch Gmbh Kolbenzylindereinheit
WO2015120930A1 (fr) * 2014-02-13 2015-08-20 Delphi International Operations Luxembourg S.À R.L. Pompe à carburant
DE102015016314A1 (de) * 2015-12-15 2017-06-22 L'orange Gmbh Kolbenpumpe

Also Published As

Publication number Publication date
DE50204735D1 (de) 2005-12-08
DK1234975T3 (da) 2005-12-05
EP1234975B1 (fr) 2005-11-02
PL199298B1 (pl) 2008-09-30
EP1234975A3 (fr) 2004-08-11
JP4111716B2 (ja) 2008-07-02
CN1372074A (zh) 2002-10-02
CN1280537C (zh) 2006-10-18
KR20020070080A (ko) 2002-09-05
JP2002276508A (ja) 2002-09-25
PL352345A1 (en) 2002-09-09
KR100773437B1 (ko) 2007-11-05

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