EP1058001A1 - Hochdruckförderpumpe - Google Patents
Hochdruckförderpumpe Download PDFInfo
- 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
Links
Images
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)
Abstract
Description
- Fig. 1
- eine Schnittansicht einer Hochdruckförderpumpe mit einem Exzentertrieb;
- Fig. 2
- eine Schnittansicht entlang der in Fig. 1 gezeigten Ebene II-II, welche die Kontaktfläche zwischen dem Abwälzring und dem Förderkolben darstellt;
- Fig. 3
- eine Schnittansicht eines Exzentertriebs in der oberen Totpunktlage des Föderkolbens;
- Fig. 4
- eine Schnittansicht eines Exzentertriebs in der unteren Totpunktlage des Föderkolbens; und
- Fig. 5
- eine Schnittansicht eines Abwälzrings gemäss der vorliegenden Erfindung.
Claims (11)
- Hochdruckförderpumpe mit einem Hochdruckzylinder (8), einem darin verschiebbaren Förderkolben (9) und einem auf einer Antriebswelle (3) angeordneten Exzenter (6), auf dem ein Abwälzring (7, 7') drehbar gelagert ist, an dem der Förderkolben (9) oder ein damit verbundenes Teil über eine Kontaktfläche (16) anliegt, dadurch gekennzeichnet, dass der Abwälzring (7') zumindest eine Ausnehmung oder Aussparung (20, 22) aufweist.
- Hochdruckförderpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die Ausnehmung oder Aussparung (20, 22) am Aussenumfang des Abwälzringes (7') ausgebildet ist.
- Hochdruckförderpumpe nach Anspruch 1, dadurch gekennzeichnet, dass der Abwälzring (7') an seinem Aussenumfang und axial ausserhalb des Bereichs der Kontaktfläche (16) zumindest eine umlaufende Ausnehmung (20, 22) aufweist.
- Hochdruckförderpumpe nach Anspruch 1, dadurch gekennzeichnet, dass zwei umlaufende Ausnehmungen (20, 22) vorgesehen sind, die die Kontaktfläche (16) seitlich begrenzen und die jeweils am äusseren Rand des Abwälzringes (7') vorgesehen sind.
- Hochdruckförderpumpe nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass die Ausnehmung (20, 22) des Abwälzringes (7') im Querschnitt gesehen etwa rechteckförmig ist.
- Hochdruckförderpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Umfangsfläche des Abwälzringes (7, 7') bombiert ist.
- Abwälzring (7') für eine Hochdruckförderpumpe nach zumindest einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass dieser zumindest eine Ausnehmung oder Aussparung (20, 22) aufweist.
- Abwälzring nach Anspruch 7, dadurch gekennzeichnet, dass die Ausnehmung oder Aussparung (20, 22) am Aussenumfang des Abwälzringes (7') ausgebildet ist.
- Abwälzring nach Anspruch 7, dadurch gekennzeichnet, dass zwei umlaufende Ausnehmungen (20, 22) vorgesehen sind, die jeweils am äusseren Rand des Abwälzringes (7') vorgesehen sind.
- Abwälzring nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, dass die Ausnehmung (20, 22) im Querschnitt gesehen etwa rechteckförmig ist.
- Abwälzring nach einem der Ansprüche 7 bis 11, dadurch gekennzeichnet, dass die Umfangsfläche des Abwälzringes (7, 7') bombiert ist.
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 (de) | 2000-12-06 |
EP1058001B1 EP1058001B1 (de) | 2005-02-16 |
Family
ID=4200422
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00109323A Expired - Lifetime EP1058001B1 (de) | 1999-05-31 | 2000-05-02 | Hochdruckförderpumpe |
Country Status (5)
Country | Link |
---|---|
US (1) | US6205980B1 (de) |
EP (1) | EP1058001B1 (de) |
JP (1) | JP3609693B2 (de) |
DE (1) | DE50009529D1 (de) |
ES (1) | ES2233236T3 (de) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003014569A1 (de) * | 2001-08-08 | 2003-02-20 | Crt Common Rail Technologies Ag | Hochdruckförderpumpe |
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 (de) * | 2009-07-20 | 2011-01-26 | Delphi Technologies Holding S.à.r.l. | Pumpenanordnung |
WO2013037543A1 (de) * | 2011-09-15 | 2013-03-21 | Robert Bosch Gmbh | Pumpe, insbesondere kraftstoffhochdruckpumpe |
US11879455B2 (en) | 2021-07-16 | 2024-01-23 | Denso Corporation | Supply pump |
Families Citing this family (2)
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)
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)
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 (de) * | 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 (de) * | 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 |
-
2000
- 2000-05-02 ES ES00109323T patent/ES2233236T3/es not_active Expired - Lifetime
- 2000-05-02 EP EP00109323A patent/EP1058001B1/de not_active Expired - Lifetime
- 2000-05-02 DE DE50009529T patent/DE50009529D1/de not_active Expired - Lifetime
- 2000-05-29 JP JP2000158194A patent/JP3609693B2/ja not_active Expired - Fee Related
- 2000-05-31 US US09/584,116 patent/US6205980B1/en not_active Expired - Lifetime
Patent Citations (3)
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)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003014569A1 (de) * | 2001-08-08 | 2003-02-20 | Crt Common Rail Technologies Ag | Hochdruckförderpumpe |
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 (de) * | 2009-07-20 | 2011-01-26 | Delphi Technologies Holding S.à.r.l. | Pumpenanordnung |
WO2011009839A1 (en) * | 2009-07-20 | 2011-01-27 | Delphi Technologies Holding S.À.R.L. | Pump assembly |
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 (de) * | 2011-09-15 | 2013-03-21 | Robert Bosch Gmbh | Pumpe, insbesondere kraftstoffhochdruckpumpe |
US11879455B2 (en) | 2021-07-16 | 2024-01-23 | Denso Corporation | Supply pump |
Also Published As
Publication number | Publication date |
---|---|
EP1058001B1 (de) | 2005-02-16 |
JP2000356184A (ja) | 2000-12-26 |
JP3609693B2 (ja) | 2005-01-12 |
ES2233236T3 (es) | 2005-06-16 |
US6205980B1 (en) | 2001-03-27 |
DE50009529D1 (de) | 2005-03-24 |
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