EP1058001A1 - Pompe d'alimentation haute pression - Google Patents

Pompe d'alimentation haute pression Download PDF

Info

Publication number
EP1058001A1
EP1058001A1 EP00109323A EP00109323A EP1058001A1 EP 1058001 A1 EP1058001 A1 EP 1058001A1 EP 00109323 A EP00109323 A EP 00109323A EP 00109323 A EP00109323 A EP 00109323A EP 1058001 A1 EP1058001 A1 EP 1058001A1
Authority
EP
European Patent Office
Prior art keywords
rolling ring
recess
feed pump
pressure feed
high 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.)
Granted
Application number
EP00109323A
Other languages
German (de)
English (en)
Other versions
EP1058001B1 (fr
Inventor
Fritz Spinnler
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.)
CRT Common Rail Technologies AG
Original Assignee
CRT COMMON RAIL TECHNOLOGIES AG
Schweizerische Industrie Gesellschaft
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 CRT COMMON RAIL TECHNOLOGIES AG, Schweizerische Industrie Gesellschaft filed Critical CRT COMMON RAIL TECHNOLOGIES AG
Publication of EP1058001A1 publication Critical patent/EP1058001A1/fr
Application granted granted Critical
Publication of EP1058001B1 publication Critical patent/EP1058001B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams

Definitions

  • the present invention relates to a feed pump for high pressures and especially the drive of feed pumps, that work on the reciprocating principle.
  • High pressure feed pumps have one in relation to the piston diameter relatively long piston stroke and are therefore suitable to generate high pressures.
  • Such high pressure feed pumps are for example for the generation of the Injection pressure in fuel injection systems (e.g. Common Rail) used for internal combustion engines.
  • a Generic high-pressure feed pump is in EP-A-881 380 A1.
  • High-pressure feed pumps of the generic type have one High pressure cylinder or plunger cylinder and one in this reciprocating cylindrical feed piston or plunger, the volume of the delivery chamber within the high pressure cylinder by the stroke movement of the Plunger is changed.
  • a filling stroke of the plunger is the delivery chamber via a filling valve with a Storage space for a fluid can be connected to the in Displacement increasing delivery volume with the medium to fill.
  • the pressure in the delivery chamber increases until a pressure valve opens and thereby the delivery chamber connects a high pressure room.
  • the exact design the high pressure pump is in said EP-A-0 881 380 A1 described, the disclosure of which is expressly made by this reference made the content of the present application becomes.
  • the plunger is driven by an eccentric drive, the one eccentric mounted on an eccentric shaft comprises, on which a rolling ring rotatably mounted is.
  • the preload is on Delivery piston with one provided at one end plate-like extension on the rolling ring. Due to the force relationships when passing through the The gear ring rotates at top and bottom dead center here back and forth and changes per revolution of the eccentric shaft twice its direction of rotation. This can happen at high Speed of the drive shaft to damage the components of the eccentric drive.
  • the rolling ring has at least one recess or recess so that the moment of inertia of the rolling ring is reduced with respect to its axis of rotation.
  • This reduction in the moment of inertia also the acceleration torque of the rolling ring when the direction of rotation changes reduced, causing damage to the Eccentric drive especially in the area of a contact surface between the rolling ring and the delivery piston.
  • the recess or Recess formed on the outer circumference of the rolling ring his.
  • the stability of the rolling ring is not reduced, but at the same time the moment of inertia can be reduced.
  • the rolling ring on its outer circumference and axially outside the Area of the contact surface at least one circumferential recess on.
  • the rolling ring lowered symmetrically outside the area of the contact surface, which in turn does not reduce stability, however the moment of inertia and therefore also the acceleration moment is reduced when the direction of rotation changes.
  • the rolling ring has two rotating ones Has recesses which the contact surface limit laterally, and each on the outer edge of the Rolling ring are provided. This is a symmetrical one Arrangement created in terms of reduction the moment of inertia is optimized. In this embodiment is only in the area of the contact surface the required outer diameter of the rolling ring is available. The rolling ring is outside the contact surface reduced mass.
  • FIG. 1 shows a longitudinal section through a high pressure feed pump with a housing 4 in which a high pressure cylinder 8 is inserted, in which a delivery piston 9 and can move here.
  • the high pressure cylinder 8 is one Base body 11 clamped in the housing 4 by means of Bolt 18 and 18 'is screwed into the housing 4.
  • Bolt 18 and 18 ' is screwed into the housing 4.
  • the base body 11 there is also an inlet valve 12 and an exhaust valve 13 is provided, the exhaust valve 13 opens the passage to a high pressure container 14 and closes.
  • Eccentric drive In the housing 4 of the high pressure feed pump is also a Eccentric drive provided, which has a drive shaft 3, over bearings 5 and 5 'freely around an axis of rotation 1 is rotatably supported.
  • the drive shaft 3 carries between the bearing points 5, 5 'with respect to the axis of rotation 1 of the drive shaft 3 arranged eccentrically Eccentric pin 6, the center axis 2 parallel to the axis of rotation 1 of the drive shaft 3 runs.
  • On the eccentric pin 6 On the eccentric pin 6 is a cambered on its outer circumference Rolling ring 7 rotatably mounted with respect to the eccentric pin 6.
  • the delivery piston 9 is sliding slidably guided.
  • the delivery plunger 9 has on its the drive shaft 3 facing end a plate-like extension 15, which rests on the rolling ring 7.
  • the reference numeral 16 denotes the contact point or Contact area between the rolling ring 7 and the extended End 15 of the delivery piston 9.
  • the Delivery piston 9 by the eccentric 3, 6, 7 up and down emotional. If the delivery piston 9 during a filling stroke Moving down, the delivery chamber of the high pressure cylinder fills up 8 via the inlet valve 12 with the pumped medium. If the delivery piston 9 in a following Moving the delivery stroke upwards, the pressure in the delivery chamber increases with inlet valve 12 closed until the outlet valve 13 opens and thereby the delivery room with the high pressure container 14 connects. The pumped medium is in the High pressure container 14 promoted.
  • Figure 2 shows a section along the line II-II of Figure 1, wherein the contact surface 16 along this section plane is hatched. As can be seen is against at high pressure loads on the delivery piston 9 the contact surface 16 occurring in the rolling ring 7 is elliptical, since the rolling ring 7 is slightly convex.
  • Figures 3 and 4 illustrate the operation of the Eccentric drive and the movement of the rolling ring 7 Go through the top and bottom dead center positions.
  • Figure 3 shows the delivery piston 9 in the top dead center position.
  • the contact surface 16 moves to the left, whereby the rolling ring 7 rotates clockwise. This is because the bias of the spring 17 and Pressure in the delivery chamber in the area of the top dead center on is largest, so that the force exerted by the spring 17 greater than the sliding friction force between the plate 15 and the rolling ring 7.
  • FIG. 4 shows the bottom dead center position of the delivery piston 9.
  • the eccentric pin 6 moves in the direction of this lower one Dead center position, the contact surface 16 moves in Figure to the right, causing the rolling ring 7 to rotate counterclockwise. This is because again remember that the force exerted by the spring 17 also greater than that in the area of the bottom dead center position Sliding friction between the plate 15 and the rolling ring 7 is.
  • the rolling ring 7 thus moves relative to the plate 15 during the rotation of the eccentric 6 back and forth and changes its direction of rotation per revolution of the drive shaft 3 twice. This leads to a high speed of the drive shaft 3 to problems because the frequency of change of the direction of rotation Rolling ring 7 and thus also its acceleration torque increases. In the worst case it takes place between the plates 15 and the rolling ring 7 at rotational acceleration peaks Sliding instead of what can lead to damage.
  • a rolling ring 7 'is provided, as in Figure 5 is shown in cross section.
  • the rolling ring 7 ' corresponds essentially the rolling ring 7 of Figures 1 to 4, but two on the outer circumference of the rolling ring 7 ' Recesses or recesses 20, 22 are provided.
  • the Recesses 20, 22 are located axially outside the area the contact surface 16 and are each on the outside Edge of the rolling ring 7 'is provided.
  • the recesses 20, 22 of the rolling ring 7 ' are seen in cross section roughly rectangular.
  • the rolling ring according to the invention has a smaller one Moment of inertia and a correspondingly lower acceleration torque, which is a higher frequency of rotation change of the rolling ring, a higher speed of the Drive shaft and thus a higher delivery capacity of the High pressure pump allows without the rolling ring 7 'on the plate 15 slides at acceleration peaks.
  • a High-pressure pump with an eccentric drive according to the invention can therefore be operated at higher speeds, without damaging the components of the eccentric drive or excessive wear occurs.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
EP00109323A 1999-05-31 2000-05-02 Pompe d'alimentation haute pression Expired - Lifetime EP1058001B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH101399 1999-05-31
CH101399 1999-05-31

Publications (2)

Publication Number Publication Date
EP1058001A1 true EP1058001A1 (fr) 2000-12-06
EP1058001B1 EP1058001B1 (fr) 2005-02-16

Family

ID=4200422

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00109323A Expired - Lifetime EP1058001B1 (fr) 1999-05-31 2000-05-02 Pompe d'alimentation haute pression

Country Status (5)

Country Link
US (1) US6205980B1 (fr)
EP (1) EP1058001B1 (fr)
JP (1) JP3609693B2 (fr)
DE (1) DE50009529D1 (fr)
ES (1) ES2233236T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003014569A1 (fr) * 2001-08-08 2003-02-20 Crt Common Rail Technologies Ag Pompe d'alimentation haute pression
FR2870895A1 (fr) * 2004-05-28 2005-12-02 Stanadyne Corp Pompe a piston radiaux avec une bague d'actionnement par roulement entrainee de facon excentrique.
EP2278163A1 (fr) * 2009-07-20 2011-01-26 Delphi Technologies Holding S.à.r.l. Ensemble de pompe
WO2013037543A1 (fr) * 2011-09-15 2013-03-21 Robert Bosch Gmbh Pompe, notamment pompe à carburant haute pression
US11879455B2 (en) 2021-07-16 2024-01-23 Denso Corporation Supply pump

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE50013384D1 (de) * 1999-11-19 2006-10-12 Crt Common Rail Tech Ag Hochdruckeinspritzsystem mit Common Rail
DE102012024924A1 (de) * 2012-12-19 2014-06-26 Volkswagen Aktiengesellschaft Vorrichtung zum Antrieb einer Kolbenpumpe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2292728A (en) * 1939-02-08 1942-08-11 Sulzer Ag Cam mechanism
US4184817A (en) * 1977-12-01 1980-01-22 Lear Siegler, Inc. High pressure multi-cylinder pump
DE19635164A1 (de) * 1996-08-30 1998-03-05 Bosch Gmbh Robert Kolbenpumpe

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2213994A (en) * 1939-03-01 1940-09-10 John R Rankin Fuel feeding device
CH645435A5 (de) * 1979-06-20 1984-09-28 Hydrowatt Syst Kolbenpumpe.
JPS633362Y2 (fr) * 1980-04-14 1988-01-27
US4739675A (en) * 1980-11-14 1988-04-26 Connell Calvin C Cylindrical tappet
US4548124A (en) * 1984-02-23 1985-10-22 Riva Calzoni S.P.A. Radial piston hydraulic motor with variable eccentricity
JPH02145670U (fr) * 1989-05-16 1990-12-11
JPH0741901Y2 (ja) * 1990-06-12 1995-09-27 株式会社ナブコ ポンプ装置
JPH08144717A (ja) * 1994-11-16 1996-06-04 Isuzu Motors Ltd カム装置
JPH1136831A (ja) * 1997-07-18 1999-02-09 Toyota Motor Corp 三次元カムシャフト及びその製造方法
US5860398A (en) * 1997-10-28 1999-01-19 Koerner; Jeffrey Scott Engine tappet
JPH11351136A (ja) * 1998-06-15 1999-12-21 Unisia Jecs Corp プランジャポンプ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2292728A (en) * 1939-02-08 1942-08-11 Sulzer Ag Cam mechanism
US4184817A (en) * 1977-12-01 1980-01-22 Lear Siegler, Inc. High pressure multi-cylinder pump
DE19635164A1 (de) * 1996-08-30 1998-03-05 Bosch Gmbh Robert Kolbenpumpe

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003014569A1 (fr) * 2001-08-08 2003-02-20 Crt Common Rail Technologies Ag Pompe d'alimentation haute pression
FR2870895A1 (fr) * 2004-05-28 2005-12-02 Stanadyne Corp Pompe a piston radiaux avec une bague d'actionnement par roulement entrainee de facon excentrique.
EP2278163A1 (fr) * 2009-07-20 2011-01-26 Delphi Technologies Holding S.à.r.l. Ensemble de pompe
WO2011009839A1 (fr) * 2009-07-20 2011-01-27 Delphi Technologies Holding S.À.R.L. Ensemble pompe
CN102575667A (zh) * 2009-07-20 2012-07-11 德尔福技术控股有限公司 泵组件
US9518546B2 (en) 2009-07-20 2016-12-13 Delphi International Operations Luxembourg S.A.R.L. Pump assembly
WO2013037543A1 (fr) * 2011-09-15 2013-03-21 Robert Bosch Gmbh Pompe, notamment pompe à carburant haute pression
US11879455B2 (en) 2021-07-16 2024-01-23 Denso Corporation Supply pump

Also Published As

Publication number Publication date
JP2000356184A (ja) 2000-12-26
JP3609693B2 (ja) 2005-01-12
DE50009529D1 (de) 2005-03-24
ES2233236T3 (es) 2005-06-16
US6205980B1 (en) 2001-03-27
EP1058001B1 (fr) 2005-02-16

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