EP1058001B1 - Pompe d'alimentation haute pression - Google Patents

Pompe d'alimentation haute pression Download PDF

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Publication number
EP1058001B1
EP1058001B1 EP00109323A EP00109323A EP1058001B1 EP 1058001 B1 EP1058001 B1 EP 1058001B1 EP 00109323 A EP00109323 A EP 00109323A EP 00109323 A EP00109323 A EP 00109323A EP 1058001 B1 EP1058001 B1 EP 1058001B1
Authority
EP
European Patent Office
Prior art keywords
rolling ring
recesses
cutouts
feed pump
eccentric
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
EP00109323A
Other languages
German (de)
English (en)
Other versions
EP1058001A1 (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
CRT Common Rail Tech 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 CRT Common Rail Technologies AG, CRT Common Rail Tech AG 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 in particular the drive of feed pumps, which work on the reciprocating principle.
  • High-pressure feed pump have one with respect to the piston diameter relatively long piston stroke and are therefore suitable to generate high pressures.
  • Such high pressure pumps For example, for the generation of the Injection pressure in fuel injection systems (e.g. Common rail) used for internal combustion engines.
  • a High-pressure pump is, for example, in EP-A-881 380 A1 discloses.
  • High-pressure feed pumps of this type have one High pressure cylinder or plunger cylinder and a in this reciprocating cylindrical delivery piston or plunger, wherein the volume of the delivery chamber within the high-pressure cylinder by the lifting movement of the Plunger is changed.
  • the pumping chamber via a filling valve with a Reservoir for a pumped medium connectable to the in Stroke volume increasing delivery chamber with the fluid to fill.
  • the pressure in the delivery chamber increases until a pressure valve opens and thereby the delivery chamber with connects a high pressure room.
  • a generic high pressure feed pump is disclosed in US-A-4,184,817 described.
  • This high-pressure pump has a delivery piston, which in a High pressure cylinder is movable back and forth and on a contact surface of a rotatably mounted on an eccentric Abroll ring rests.
  • the rolling ring points a radially outwardly open U-shaped cross-section with an axially centered arranged on the contact surface forming recess.
  • the circulating Recess serves for the axial positioning of the delivery piston.
  • the drive of the plunger is effected by an eccentric drive, the one mounted on an eccentric shaft eccentric comprises, on which a rolling ring rotatably mounted is.
  • the prestressed Delivery piston with a provided at one end plate-like extension of the rolling ring on. Due to the force conditions when passing through the Upper and lower dead center, the rolling ring rotates this back and forth and changes per revolution of the eccentric shaft twice its direction of rotation. This can be at high Speed of the drive shaft to damage to the components of the eccentric drive.
  • the rolling ring has at least one recess or recess on, so that the moment of inertia the Abdicalzrings is reduced with respect to its axis of rotation. This reduction of the moment of inertia will also the acceleration torque of Abdozenslzrings at a change of direction reduced, causing damage to the Eccentric drive especially in the area of a contact surface be avoided between Abdozenslzring and delivery piston.
  • the recess or Recess formed on the outer circumference of the Abracelzringes be.
  • the stability of the Abracelzringes not reduced, but at the same time the moment of inertia can be reduced.
  • the Abracelzring on its outer circumference and axially outside of 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 thus also the acceleration torque is reduced when the direction of rotation changes.
  • the rolling ring has two revolving rings Having recesses, which the contact surface border laterally, and each at the outer edge of the Abroll ring are provided. This is a symmetrical Arrangement created in terms of reduction of the moment of inertia is optimized. In this embodiment is only in the area of the contact surface the required outer diameter of the Abisselzringes available. Outside the contact surface is the Abconsultedlzring reduced mass.
  • FIG. 1 shows a longitudinal section through a high-pressure feed pump with a housing 4 into which a high-pressure cylinder 8 is inserted, in which a delivery piston 9 back and can move.
  • the high pressure cylinder 8 is of a Base body 11 is clamped in the housing 4, by means of Bolt 18 and 18 'is screwed into the housing 4.
  • an inlet valve 12 In the base body 11 is also an inlet valve 12 as well an exhaust valve 13 is provided, wherein the exhaust valve 13 opens the passage to a high-pressure vessel 14 and concludes.
  • the housing 4 of the high pressure pump is also a Exzentertrieb provided which has a drive shaft 3, the bearings 5 and 5 'freely about a rotation axis 1 is rotatably supported.
  • the drive shaft 3 carries between the bearings 5, 5 'one with respect to the axis of rotation 1 of the drive shaft 3 arranged eccentrically Eccentric 6, the center axis 2 parallel to the axis of rotation 1 of the drive shaft 3 extends.
  • On the eccentric pin 6 is a cambered on its outer circumference Abrolling ring 7 rotatably mounted relative to the eccentric pin 6.
  • the delivery piston 9 is slidable slidably guided.
  • the delivery piston 9 has at its the drive shaft 3 facing the end of a plate-like extension 15, which sits on the rolling ring 7.
  • there reference numeral 16 denotes the contact point or Contact surface between the rolling ring 7 and the extended End 15 of the delivery piston 9.
  • the Delivery piston 9 For compression and delivery of a pumped medium is the Delivery piston 9 through the eccentric drive 3, 6, 7 up and down emotional.
  • the delivery piston 9 at a Gear moved down the delivery chamber of the high-pressure cylinder fills 8 via the inlet valve 12 with the fluid.
  • the delivery piston 9 at a following Delivery stroke moves upwards, the pressure in the delivery chamber increases with closed inlet valve 12 to the exhaust valve 13 opens and thereby the delivery chamber with the high-pressure vessel 14 connects.
  • the fluid is in the Promoted high pressure vessel 14.
  • Figure 2 shows a section along the line II-II of Figure 1, wherein the contact surface 16 along this cutting plane hatched. As you can see, is at high pressure loads of the delivery piston 9 against the rolling ring 7 occurring contact surface 16 elliptical, since the rolling ring 7 is slightly cambered.
  • Figures 3 and 4 illustrate the operation of the Exzentertriebes and the movement of the rolling ring 7 at Passing through the top and bottom dead center.
  • figure 3 shows the delivery piston 9 in the top dead center position. at a progressive rotation of the eccentric pin 6 or the drive shaft 3 in the illustrated counterclockwise direction the contact surface 16 in FIG. 3 moves to the left, whereby the rolling ring 7 rotates clockwise. This is because the bias of the spring 17 and the Pressure in the pumping chamber in the area of the top dead center position on largest, so that the force exerted by the spring 17 greater than the sliding frictional force between the plate 15th and the rolling ring 7 is.
  • FIG. 4 shows the bottom dead center position of the delivery piston 9. Moves the eccentric pin 6 in the direction of this lower Dead center, so the contact surface 16 moves in Figure to the right, whereby the rolling ring 7 a rotational movement in the counterclockwise direction. This is in turn, that the force exerted by the spring 17 also in the area of the bottom dead center position greater than the Gleitreibungskraft between the plate 15 and the Abconsultedlzring 7 is.
  • the rolling ring 7 thus moves relative to the plate 15th during the rotational movement of the eccentric 6 back and forth and changes its direction of rotation per revolution of the drive shaft 3 twice. This leads at high speed of the drive shaft 3, because the rotational direction change frequency of the Abroll ring 7 and thus also its acceleration torque increases. In the worst case takes place between the plate 15 and the rolling ring 7 at spin peaks Slip instead, which can lead to damage.
  • a rolling ring 7 ' is provided, as shown in FIG 5 is shown in cross section.
  • the rolling ring 7 ' corresponds essentially the Abdozens of the Abdozens of the Abdozens of the Abdozens of the Abdozens of the Abdozens of the Abdozens of the Abdozensringes 7 'two Recesses or recesses 20, 22 are provided.
  • the Recesses 20, 22 are located axially outside the range the contact surface 16 and are each on the outside Edge of Abicalzringes 7 'provided.
  • the recesses 20, 22 of the rolling ring 7 ' are seen in cross section about rectangular.
  • the inventive Abracelzring has a lower Moment of inertia and a correspondingly lower acceleration moment, what a higher rotation change frequency of Abicalzrings, a higher speed of Drive shaft and thus a higher flow rate of High pressure pump allows without the rolling ring 7 'on the plate 15 slides at spin peaks.
  • a Hochdruckpörderpume with an inventive Exzentertrieb can therefore be operated at higher speeds, without damage to 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)

Claims (6)

  1. Pompe d'alimentation à haute pression avec un cylindre à haute pression (8), un piston d'alimentation (9) coulissant dans celui-ci et un excentrique (6) monté sur un arbre d'entraínement (3) et sur lequel est montée en rotation une bague de roulement (7'), qui présente un évidement ou un retrait circonférentiel (20, 22) sur sa périphérie extérieure et sur laquelle le piston d'alimentation (9) ou une pièce liée à celui-ci repose au moyen d'une surface de contact (16), caractérisée en ce que la bague de roulement (7') présente deux évidements ou retraits (20, 22), chaque évidement ou retrait (20, 22) étant disposé sur un bord extérieur de la bague de roulement (7'), axialement à l'extérieur de la zone de la surface de contact (16) et les deux évidements ou retraits (20, 22) délimitant latéralement entre eux la surface de contact (16).
  2. Pompe d'alimentation à haute pression selon la revendication 1, caractérisée en ce que les évidements (20, 22) de la bague de roulement (7') sont sensiblement rectangulaires, dans une vue en section transversale.
  3. Pompe d'alimentation à haute pression selon la revendication 1 ou 2, caractérisée en ce que la surface périphérique de la bague de roulement (7') est bombée (courbe).
  4. Bague de roulement (7') pour une pompe d'alimentation à haute pression selon l'une quelconque des revendications 1 à 3, caractérisée par deux évidements ou retraits (20, 22), chaque évidement ou retrait (20, 22) étant disposé sur un bord extérieur de la bague de roulement (7'), axialement à l'extérieur de la zone de la surface de contact (16), et les deux évidements ou retraits (20, 22) délimitant latéralement entre eux la surface de contact (16).
  5. Bague de roulement selon la revendication 4, caractérisée en ce que les évidements (20, 22) sont sensiblement rectangulaires, dans une vue en section transversale.
  6. Bague de roulement selon la revendication 4 ou 5, caractérisée en ce que la surface périphérique de la bague de roulement (7') est bombée (courbe).
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 EP1058001A1 (fr) 2000-12-06
EP1058001B1 true 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 (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102575667B (zh) * 2009-07-20 2015-10-21 德尔福国际运营卢森堡有限公司 泵组件

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1101931B1 (fr) * 1999-11-19 2006-08-30 CRT Common Rail Technologies AG Système d'injection à haute pression avec common rail
WO2003014569A1 (fr) * 2001-08-08 2003-02-20 Crt Common Rail Technologies Ag Pompe d'alimentation haute pression
US7134846B2 (en) * 2004-05-28 2006-11-14 Stanadyne Corporation Radial piston pump with eccentrically driven rolling actuation ring
DE102011082733A1 (de) * 2011-09-15 2013-03-21 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
DE102012024924A1 (de) * 2012-12-19 2014-06-26 Volkswagen Aktiengesellschaft Vorrichtung zum Antrieb einer Kolbenpumpe
JP2023013759A (ja) 2021-07-16 2023-01-26 株式会社Soken サプライポンプ

Family Cites Families (14)

* 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
US2213994A (en) * 1939-03-01 1940-09-10 John R Rankin Fuel feeding device
US4184817A (en) * 1977-12-01 1980-01-22 Lear Siegler, Inc. High pressure multi-cylinder pump
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
DE19635164A1 (de) * 1996-08-30 1998-03-05 Bosch Gmbh Robert Kolbenpumpe
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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102575667B (zh) * 2009-07-20 2015-10-21 德尔福国际运营卢森堡有限公司 泵组件

Also Published As

Publication number Publication date
US6205980B1 (en) 2001-03-27
JP2000356184A (ja) 2000-12-26
EP1058001A1 (fr) 2000-12-06
DE50009529D1 (de) 2005-03-24
ES2233236T3 (es) 2005-06-16
JP3609693B2 (ja) 2005-01-12

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