EP2464853A1 - Hochdruckpumpe - Google Patents
HochdruckpumpeInfo
- Publication number
- EP2464853A1 EP2464853A1 EP10728173A EP10728173A EP2464853A1 EP 2464853 A1 EP2464853 A1 EP 2464853A1 EP 10728173 A EP10728173 A EP 10728173A EP 10728173 A EP10728173 A EP 10728173A EP 2464853 A1 EP2464853 A1 EP 2464853A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- roller
- central bore
- pressure pump
- cam
- plunger
- 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
- 230000033001 locomotion Effects 0.000 claims abstract description 7
- 238000002485 combustion reaction Methods 0.000 claims abstract description 4
- 239000000446 fuel Substances 0.000 claims abstract description 4
- 238000002347 injection Methods 0.000 claims abstract description 4
- 239000007924 injection Substances 0.000 claims abstract description 4
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 230000007423 decrease Effects 0.000 claims description 4
- 230000007704 transition Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000009933 burial Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
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
-
- 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
-
- 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
-
- 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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
Definitions
- the invention relates to a high-pressure pump for a fuel injection device of an internal combustion engine having the features of the preamble of claim 1.
- a high-pressure pump for example, from the published patent application DE 10 2006 041 673 A1.
- the high-pressure pump described herein comprises a drive shaft having at least one cam or eccentric and at least one pump element comprising a pump piston which is driven in a reciprocating motion by the cam or eccentric of the drive shaft.
- the pump piston is supported via a support member and a rotatably mounted in this support roller on the cam or eccentric of the drive shaft.
- Support member and roller are taken together in a bucket tappet for support, wherein contact areas between the roller and the bucket tappet and / or the support member are formed. Due to the rotational movement of the roller, these contact areas are subject to increased wear, so that it is proposed in the aforementioned document to provide the respective contact areas with a surface which has a high resistance to wear.
- the invention is based on the object to improve a high pressure pump of the type mentioned in terms of their wear resistance.
- the wear in the contact area of a roller with a cam or an eccentric of a drive shaft and / or with a roller receiving support element is to be reduced.
- the proposed high-pressure pump has at least one pump element which has a pump piston, which via a cam or eccentric a
- the roller has at least one central bore which extends along the longitudinal axis A of the roller and has at least one conical, partially spherical and / or partially ellipsoidal section for forming an inner contour which runs obliquely to the longitudinal axis A at least in a partial region.
- a roller designed in this way for supporting a pump piston on a cam or eccentric of the drive shaft has the advantage that the rigidity of the roller can be adjusted via the inner contour of the at least one central bore. Because in the im
- Essentially hollow cylindrical sections has the role of a less rigidity than in the sections which do not have a central bore.
- the central bore can also extend through the entire roller body, wherein an inner contour of the bore can be determined by juxtaposing conical, partially spherical and / or partially ellipsoidal sections, which leads to an optimization of the roller stiffness.
- the roller stiffness must be high enough to support the pump piston against the cam or eccentric, on the other hand, it should be so low that errors are compensated without fatigue.
- the weight of the roller can be significantly reduced by a central bore, this is especially true when the central bore through the entire
- Rolling body extends.
- a low weight and an optimized roller stiffness lead to an improved pressure behavior of the roller on the cam or eccentric, so that the dynamic load in the contact area of the roller with the cam or the
- the high-pressure pump according to the invention is therefore characterized by a long service life.
- the at least one central unit is therefore characterized by a long service life.
- the two blind holes are preferably mirror-symmetrical with respect to a perpendicular bisector to the longitudinal axis A, ie that they extend over an equally long axial section a and have an inner contour which is mirrored.
- the two blind holes may be formed, for example, cone-shaped, part-spherical and / or nerllipsoid.
- the mirrored design of the two blind bores also contributes to a uniform running of the roller on the cam or eccentric and is therefore to be preferred.
- the extent of the axial extent of the two blind holes is selected according to the requirements.
- the two end face side loosened blind holes cause the role in the region of its two end faces has a lower rigidity, so that the contact pressure of the roller is reduced in this area and the tread on the cam or eccentric due to less load has less tracks. This also leads to the edge area of the roll edge pressure is reduced, so that the role is exposed to less wear.
- the two blind holes or a continuous central bore are formed such that the diameter from the inside to the outside, ie towards at least one end face, is larger. This also means that the rigidity of the roller decreases towards an end face. This not only has a favorable effect on the edge pressure on the roller, but also simplifies the production of such a roller. Because the diameter of the central
- the central bore has no undercuts.
- the central bore can thus be set from the outside, from an end face.
- the at least one central bore can also be produced in one working step together with the roller, for example using a closed mold, since demolding is unproblematic owing to the lack of undercuts.
- other manufacturing methods are possible.
- the central bore is rotationally symmetrical with respect to the longitudinal axis A of the roller.
- the roller in the cross section in the area of the central bore has circumferentially equal wall thicknesses. This ensures that the roller runs smoothly on the cam or on the eccentric of the drive shaft. The shape stiffness of the roll thus changes only along its axial extent.
- the central bore of the roller can also have a cylindrical section b.
- the roller has a constant stiffness, so that this section preferably forms a central portion of the roller TeN.
- a cylindrical portion b may have a continuous central bore extending from one end face of the roll to the other.
- the cylindrical section b preferably has a smaller diameter than a subsequent section a. In this way, it is ensured that the inner contour has no undercuts.
- a cylindric portion is thus particularly easy to manufacture.
- the end faces of the roller are convexly curved and / or tapered at least over a partial region.
- an end face has a central bore
- the at least partially convexly curved and / or conically extending end face has a central recess.
- the end face may be rounded in the transition to the central bore. If the roller has a central bore on both end faces, only the remaining edge regions of the end faces that surround the respective bore form contact regions between the roller and the tappet.
- the roller is at least partially received in the plunger, wherein preferably the plunger is formed in the region of the roller receiving hollow cylindrical, so that the end faces of the roller at least partially bear against an inner peripheral surface of the plunger.
- Support may also be arranged a roller shoe in the bucket tappet. Since the roller shoe also experiences a dynamic load in the area of contact with the roller, the above-mentioned advantages also come into play in the contact area of the roller with the roller shoe.
- FIG. 1 shows a partial longitudinal section through a pump element of a high pressure pump according to the invention according to a first embodiment
- FIG. 2 shows a longitudinal section through a roller according to an alternative embodiment.
- the pump element shown in detail in FIG. 1 of a high-pressure pump according to the invention has a pump piston 1 which indirectly supports a drive shaft (not shown) via a roller 4 on a cam 2 is.
- the roller 4 is at least partially received in a plunger 3, which has a cup-shaped end.
- a roller shoe 9 is further provided, which is arranged between the plunger 3 and the roller 4.
- the rotation of the drive shaft is transmitted via the cam 2 to the roller 4, which rolls on the outer peripheral side on the cam 2.
- the outer circumference side of the cam 2 thus forms a running surface 8.
- the roller 4 is hollow formed by having a central bore 5 extending from one end face 6 to the other end face 6 'along the longitudinal axis A of the roller 4 extends.
- the bore 5 has various sections, the sections a conical and the section b are cylindrical.
- the central bore 5 thus has a profiled inner contour, which allows optimization of the roller stiffness.
- Bore 5 is arranged in the middle. On both sides of the section b is followed in each case by a partial section a, which runs conically, wherein the diameter of the central bore 5 increases from the inside to the outside, to the side surfaces 6 and 6 '.
- the substantially hollow cylindrical roller 4 thus has a smaller thickness in the area of the side surfaces 6 and 6 '. As the wall thickness is reduced, the roller stiffness also decreases, so that it is the lowest in the area of the side surfaces 6 and 6 '. Accordingly, the roller stiffness can be adjusted via the inner contour of the central bore 5 such that the contact pressure of the roller 4 on the running surface 8 of the cam 2 in the region of the partial section a is less than in the region of the partial section b.
- the embodiment of the central bore 5 shown in FIG. 1, the inner contour of which is composed of a first conically extending partial section a, a cylindrical partial section b and a second conically extending partial section a, is selected merely by way of example.
- the inner contour of the central bore 5 can also be composed of two or more than three subsegments, which moreover can also be of partial spherical or partially ellipsoidal design.
- the transitions of the sections may be flattened or rounded. The same applies to the transition of the central bore 5 in one of the end faces 6 and 6 '. These too can be flattened or rounded.
- the central bore 5 In order to allow a smooth running of the roller 4 on the tread 8 of the cam 2, the central bore 5 - regardless of the selected inner contour - rotationally symmetrical with respect to the longitudinal axis A. That is, in the cross section, the roller 4 in the region of the central bore 5 circumferentially has the same wall thickness. A uniform drainage is also ensured by the fact that the central bore 5 is mirror-symmetrical with respect to a central axis perpendicular to the longitudinal axis A.
- FIG. 4 An alterantive embodiment of the roller 4 of a pump element of a further high-pressure pump according to the invention is shown in FIG. Instead of a continuous central bore 5, this roller 4 on two blind holes 5, each extending from an end face 6 and 6 'inwards. These are also rotationally symmetrical with respect to the longitudinal axis A angordnet and have a mirrored inner contour.
- the illustrated embodiment shows two blind holes with elliptical inner contour. The transition of the holes 5 in the end faces 6 and 6 'is executed in each case rounded. The blind holes 5 on the end faces 6 and 6 'of the roller 4 cause them to have a lower rigidity in the sections a.
- the roller stiffness can also be optimized by forming two blind holes. The roller stiffness is determined via the respective inner contour of the bores 5, ie in particular over its length and the respective diameter ratios. Wear and tear on the exterior zsymmetrics phase 10 of the roller 4 and the tread 8 of the cam 2 are thus significantly reduced.
- each pump element has a roller 4 with at least one central bore 5, which has an inner contour that determines the roller stiffness.
- the roll material is preferably also taken into account.
- a wear-reducing effect has the proposed role training also in relation to a possibly provided roller shoe 9, on which the roller 4 can be additionally supported.
- a roller shoe 9 need not necessarily be provided.
- the roller 4 may also be supported via other support elements in addition to the plunger 3.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009028373A DE102009028373A1 (de) | 2009-08-10 | 2009-08-10 | Hochdruckpumpe |
PCT/EP2010/058765 WO2011018260A1 (de) | 2009-08-10 | 2010-06-22 | Hochdruckpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2464853A1 true EP2464853A1 (de) | 2012-06-20 |
EP2464853B1 EP2464853B1 (de) | 2014-01-01 |
Family
ID=42710733
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10728173.5A Not-in-force EP2464853B1 (de) | 2009-08-10 | 2010-06-22 | Hochdruckpumpe |
Country Status (7)
Country | Link |
---|---|
EP (1) | EP2464853B1 (de) |
JP (1) | JP2013501876A (de) |
KR (1) | KR20120069659A (de) |
CN (1) | CN102472221A (de) |
DE (1) | DE102009028373A1 (de) |
RU (1) | RU2555062C2 (de) |
WO (1) | WO2011018260A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010032056B4 (de) * | 2010-07-23 | 2019-11-28 | Robert Bosch Gmbh | Kolbeneinheit |
US9835123B2 (en) | 2015-01-13 | 2017-12-05 | Roller Bearing Company Of America, Inc. | Roller for a fuel pump actuator |
KR101730993B1 (ko) * | 2016-01-27 | 2017-04-27 | 주식회사 트리보테크 | 플런저 펌프 |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CS212800B2 (en) | 1976-07-15 | 1982-03-26 | Ivan J Cyphelly | Delivery apparatus with hydrostatic torque transfer by cylindrical pistons |
JPS56131021U (de) * | 1980-03-07 | 1981-10-05 | ||
RU2032106C1 (ru) * | 1992-01-22 | 1995-03-27 | Рамазан Сабеевич Цаголов | Двигатель внутреннего сгорания с подачей воды в рабочее тело |
RU2079695C1 (ru) * | 1994-06-22 | 1997-05-20 | Михаил Григорьевич Сандомирский | Топливный насос |
IT1279049B1 (it) * | 1995-10-27 | 1997-12-04 | Eaton Automotive Spa | Punteria meccanica ad azione diretta dotata di un rullino di contatto con la camma dell'albero a camme di un motore a combustione interna |
CN2560786Y (zh) * | 2002-08-10 | 2003-07-16 | 大连铁道学院 | 深穴空心滚子轴承 |
DE10337847A1 (de) * | 2003-08-18 | 2005-03-17 | Robert Bosch Gmbh | Pumpenanordnung mit einer Hochdruckpumpe und einer dieser vorgeschalteten Niederdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
US7311087B2 (en) * | 2004-11-23 | 2007-12-25 | Cummins Inc. | Fuel pump with a guided tappet assembly and methods for guiding and assembly |
JP2007198518A (ja) * | 2006-01-27 | 2007-08-09 | Ntn Corp | ころおよびころ軸受 |
DE102006041673A1 (de) * | 2006-02-20 | 2007-08-23 | Robert Bosch Gmbh | Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
DE102006019228A1 (de) * | 2006-04-26 | 2007-10-31 | Schaeffler Kg | Radialwälzlager, insbesondere einreihiges Kugelrollenlager, sowie Verfahren zu dessen Montage |
DE102006045933A1 (de) * | 2006-09-28 | 2008-04-03 | Robert Bosch Gmbh | Stößelbaugruppe für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einer Stößelbaugruppe |
JP2008133851A (ja) * | 2006-11-27 | 2008-06-12 | Ntn Corp | ころ軸受 |
JP2009058033A (ja) * | 2007-08-31 | 2009-03-19 | Jtekt Corp | ころ |
CN201103619Y (zh) * | 2007-10-22 | 2008-08-20 | 中机洛阳轴承科技有限公司 | 特大型轴承用空心滚子 |
-
2009
- 2009-08-10 DE DE102009028373A patent/DE102009028373A1/de not_active Withdrawn
-
2010
- 2010-06-22 KR KR1020127003486A patent/KR20120069659A/ko not_active Application Discontinuation
- 2010-06-22 RU RU2012108436/06A patent/RU2555062C2/ru not_active IP Right Cessation
- 2010-06-22 CN CN201080035403XA patent/CN102472221A/zh active Pending
- 2010-06-22 JP JP2012524165A patent/JP2013501876A/ja active Pending
- 2010-06-22 EP EP10728173.5A patent/EP2464853B1/de not_active Not-in-force
- 2010-06-22 WO PCT/EP2010/058765 patent/WO2011018260A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2011018260A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2011018260A1 (de) | 2011-02-17 |
RU2555062C2 (ru) | 2015-07-10 |
JP2013501876A (ja) | 2013-01-17 |
EP2464853B1 (de) | 2014-01-01 |
RU2012108436A (ru) | 2013-10-20 |
KR20120069659A (ko) | 2012-06-28 |
CN102472221A (zh) | 2012-05-23 |
DE102009028373A1 (de) | 2011-02-17 |
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