EP1714030A1 - Hochdruckpumpe, insbesondere für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine - Google Patents
Hochdruckpumpe, insbesondere für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschineInfo
- Publication number
- EP1714030A1 EP1714030A1 EP04802795A EP04802795A EP1714030A1 EP 1714030 A1 EP1714030 A1 EP 1714030A1 EP 04802795 A EP04802795 A EP 04802795A EP 04802795 A EP04802795 A EP 04802795A EP 1714030 A1 EP1714030 A1 EP 1714030A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive shaft
- pressure pump
- support element
- pump
- housing part
- 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
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
- 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
- F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
-
- 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
- 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
- F04B1/0404—Details or component parts
- F04B1/0413—Cams
-
- 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
- F04B1/0404—Details or component parts
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
-
- 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
- F04B1/0404—Details or component parts
- F04B1/0439—Supporting or guiding means for the pistons
Definitions
- High-pressure pump in particular for a fuel injection device of an internal combustion engine
- the invention is based on a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
- Such a high pressure pump is known from DE 199 07 311 AI.
- This high-pressure pump has a housing and a plurality of pump elements arranged in the housing.
- the pump elements each have a pump piston driven in one stroke by a drive shaft of the high-pressure pump.
- the pump piston is tightly guided in a cylinder bore of a housing part of the high-pressure pump and delimits a pump work space in the cylinder bore.
- the pump piston is supported on the drive shaft via a support element in the form of a push ice.
- the pump piston is acted upon by a prestressed return spring towards the plunger and the plunger is acted upon by the return spring towards the drive shaft.
- a roller is rotatably mounted in the tappet, by means of which the tappet lies against a cam of the drive shaft.
- the plunger is slidably guided in a bore of a housing part of the high-pressure pump other than the housing part in which the cylinder bore is formed, the bore and the plunger having a substantially larger diameter than the cylinder bore.
- a disadvantage of this known High-pressure pump is that the cylinder bore, in which the pump piston is guided, and the bore, in which the plunger is guided, are arranged in different housing parts, so that to ensure exact alignment of the cylinder bore and the bore for the plunger, expensive centering measures of the two Housing parts to each other are required.
- the tappet is heavy, which in turn requires a return spring with high rigidity and correspondingly high weight in order to prevent the ice from jumping off the drive shaft at high speeds, as a result of which the high-pressure pump is heavy overall.
- the high pressure pump according to the invention with the features according to claim 1 has the advantage that the cylinder bore for the pump piston and the receptacle for the support element are arranged on the same housing part and therefore no complex centering measures are required when installing the high pressure pump.
- the support element can be made compact, as a result of which its weight is low and the return spring can be designed with a correspondingly low rigidity, as a result of which the weight of the high-pressure pump can be kept low.
- FIG. 1 shows a high pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
- Figure 2 shows a section of the high pressure pump designated II in Figure 1 in an enlarged view according to a first exemplary embodiment
- Figure 3 shows the section II in a view in the direction of arrow III in Figure 2
- Figure 4 shows the section II of the high pressure pump according to a second exemplary embodiment
- FIG. 5 the detail in a view in the direction of arrow V in FIG. 4.
- the high-pressure pump has a multi-part housing 10, in which a drive shaft 12, which can be driven in rotation by the internal combustion engine, is arranged.
- the drive shaft 12 is rotatably mounted in a base body 14 of the housing 10 via two bearing points spaced apart in the direction of the axis of rotation 13 of the drive shaft 12.
- the basic body 14 of the housing 10 can in turn be formed in several parts and the bearing points can be arranged in different parts of the basic body 14.
- the drive shaft 12 has at least one cam 16, wherein the cam 16 can also be designed as a multiple cam.
- the high-pressure pump has at least one or more pump elements 18 arranged in the housing 10, each with a pump piston 20, which is driven by the cam 16 of the drive shaft 12 in a stroke movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
- a housing part 22 which is connected to the base body 14 and is designed as a cylinder head.
- the housing part 22 has a flange 24 abutting on an outer side of the base body 14 and one through a Opening 15 in the base body 14 protruding toward the drive shaft 12, at least approximately cylindrical projection 26 with a smaller diameter than the flange 24.
- the pump piston 20 is guided in a tightly displaceable manner in a cylindrical bore 28 formed in the shoulder 26 in the housing part 22 and, with its end face remote from the drive shaft 12, delimits a pump work chamber 30 in the cylindrical bore 28.
- the cylindrical bore 28 can extend into the flange 24, in which then the pump work space 30 is arranged.
- the pump work chamber 30 has a connection to a fuel inlet, for example a feed pump, via a fuel inlet channel 32 running in the housing 10.
- An inlet valve 34 opening into the pump work chamber 30 is arranged at the mouth of the fuel feed channel 32 into the pump work chamber 30.
- the pump work chamber 30 also has a connection to an outlet via a fuel drain channel 36 running in the housing 10, which outlet is connected, for example, to a high-pressure accumulator 110.
- One or preferably a plurality of injectors 120 which are arranged on the cylinders of the internal combustion engine, are connected to the high-pressure accumulator 110 and are used to inject fuel into the cylinders of the internal combustion engine.
- An outlet valve 38 opening out of the pump work chamber 30 is arranged at the mouth of the fuel drain channel 36 into the pump work chamber 30.
- a support element 40 is arranged between the pump piston 20 and the cam 16 of the drive shaft 12.
- the support element 40 has on its side facing the cam 16 a concave recess 42 in which a cylindrical roller 44 is rotatably mounted.
- the axis of rotation 45 of the roller 44 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12 and the roller 44 rolls on the cam 16 of the drive shaft 12.
- the support element 40 is in a receptacle 46 of the housing part 22 in the direction of Stroke movement of the pump piston 20, which is guided displaceably along its longitudinal axis 21.
- FIGS. 2 and 3 show the high-pressure pump according to a first exemplary embodiment.
- the receptacle 46 for the support element 40 is designed as a slot formed in the extension 26 of the housing part 22 and adjoining the cylinder bore 28, which extends to the front end of the extension 26 facing the drive shaft 12.
- the slot 46 is delimited by two at least approximately parallel walls 48 of the extension 26.
- the support element 40 is at least approximately rectangular in cross-section and is arranged between the two walls 48 with little play.
- the surfaces of the walls 46 facing the support element 40 and / or the surfaces 41 of the support element 40 facing the walls 46 are preferably machined such that they are flat and have a low surface roughness, for example these surfaces are ground. Between the parallel walls 48, the support element 40 is displaceable in the direction of the longitudinal axis 21 of the pump piston 20, but is guided non-rotatably about the longitudinal axis 21.
- the pump piston 20 is coupled to the support element 40 in the direction of its longitudinal axis 21.
- the support element 40 can have, for example, on its side facing the pump piston 20 a bore 50 into which the end of the pump piston 20 projects.
- the bore 50 has an annular groove 52 on its circumference, into which a radially elastic spring ring 54 is inserted.
- the pump piston 20 also has an annular groove 56 in its end region, into which the spring ring 54 engages when the pump piston 20 is pushed into the bore 50, whereby the coupling of the pump piston 20 to the support element 40 is achieved.
- the support element 40 protrudes laterally through the slot 46 from the extension 26 and a spring plate 58 rests on the ends of the support element 40 protruding from the slot 46.
- the spring plate 58 can be connected to the support element 40, for example by means of a latching connection. Between the spring plate 58 and the housing part 22 a prestressed return spring 60 is arranged, which is designed as a helical compression spring which surrounds the extension 26. The return spring 60 forces the support element 40 and the pump piston 20 coupled to the cam 16 of the drive shaft 12 so that the roller 44 abuts the cam 16 even during the suction stroke of the pump piston 20 toward the drive shaft 12 and also at high speed the drive shaft 12 is ensured.
- the pump working chamber 30 is filled with fuel through the fuel inlet channel 32 with the inlet valve 34 open, the outlet valve 38 being closed.
- the pump piston 20 delivers fuel under high pressure through the fuel drain channel 36 to the high-pressure accumulator 110 with the outlet valve 38 open, the inlet valve 34 being closed.
- the support element 40 is rotatably guided in the receptacle 46 about the longitudinal axis 21 of the pump piston 20 and absorbs any transverse forces that may occur, so that these do not act on the pump piston 20.
- the receptacle 46 can be aligned very precisely with the cylinder bore 28, since this is formed on the same housing part 22 as the cylinder bore 28.
- the support element 40 can be made compact, since it only needs to have the recess 42 for receiving the roller 44 and via it lateral, flat surfaces 41 is guided. The production the slot 46 as a receptacle for the support element 40 and the rectangular support element 40 is easily possible.
- FIGS. 4 and 5 show sections of the high-pressure pump according to a second exemplary embodiment, in which the basic structure of the high-pressure pump is unchanged from the first exemplary embodiment and only the housing part 22 is modified.
- the housing part 122 has the flange 124 and the cylindrical projection 126 projecting therefrom.
- an annular groove 170 is introduced from the end face facing the drive shaft 12, through which an inner, at least approximately cylindrical shoulder 172 is formed within the shoulder 126, in which the cylinder bore 28 is arranged, in which the pump piston 20 is guided.
- the annular groove 170 extends in depth to close to the flange 124 of the housing part 122.
- the inner shoulder 172 ends at a greater distance from the drive shaft 12 than the outer shoulder 126 and the outer shoulder 126 has two in its end region projecting beyond the inner shoulder 172 diametrically opposed slots 146.
- the support element 140 is at least approximately rectangular in cross-section, is arranged in the end region of the outer extension 126 protruding beyond the inner extension 172 and projects with its lateral ends into the slots 146.
- the support element 140 is guided in the receptacle for the slits 146 of the outer extension 126 in the direction of the stroke movement of the pump piston 20 so that it can be moved over its flat side surfaces 141 protruding into the slits 146.
- the pump piston 20 can be coupled to the use element 140.
- a spring plate 158 bears against the support element 140, on which the prestressed return spring 160 is supported, which on the other hand is supported on the base of the annular groove 170.
- the spring plate 158 can be connected to the support element 140, for example by means of a locking connection.
- the return spring 160 is arranged in the annular groove 170 and surrounds the inner shoulder 172.
- the spring plate 158 can also be supported on the pump piston 20, for example via a locking ring or on a piston foot of the pump piston 20 which has an enlarged diameter Return spring 160 held in contact with the support element 140 and need not be additionally coupled to the support element 140.
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)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004004705A DE102004004705A1 (de) | 2004-01-30 | 2004-01-30 | Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
PCT/DE2004/002584 WO2005073554A1 (de) | 2004-01-30 | 2004-11-23 | Hochdruckpumpe, insbesondere für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1714030A1 true EP1714030A1 (de) | 2006-10-25 |
EP1714030B1 EP1714030B1 (de) | 2008-02-27 |
Family
ID=34801270
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04802795A Expired - Fee Related EP1714030B1 (de) | 2004-01-30 | 2004-11-23 | Hochdruckpumpe, insbesondere für eine kraftstoffeinspritzeinrichtung einer brennkraftmaschine |
Country Status (7)
Country | Link |
---|---|
US (1) | US7775193B2 (de) |
EP (1) | EP1714030B1 (de) |
JP (1) | JP4340289B2 (de) |
CN (1) | CN100458150C (de) |
DE (2) | DE102004004705A1 (de) |
ES (1) | ES2298845T3 (de) |
WO (1) | WO2005073554A1 (de) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007034036A1 (de) * | 2007-07-20 | 2009-01-22 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe mit Rollenstößel |
DE102008008438A1 (de) * | 2008-02-11 | 2009-08-13 | Continental Automotive Gmbh | Hochdruckpumpe |
DE102008001019A1 (de) | 2008-04-07 | 2009-10-08 | Robert Bosch Gmbh | Hochdruckpumpenanordnung mit einstempliger Hochdruckpumpe |
DE102008001718A1 (de) * | 2008-05-13 | 2009-11-19 | Robert Bosch Gmbh | Hochdruckkraftstoffpumpe |
DE102008043436A1 (de) * | 2008-11-04 | 2010-05-06 | Robert Bosch Gmbh | Kolbenpumpe mit einem Kolbenhalter |
DE102008044298A1 (de) | 2008-12-03 | 2010-06-10 | Robert Bosch Gmbh | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
DE102009028394A1 (de) * | 2009-08-10 | 2011-02-17 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102010011456A1 (de) * | 2010-03-15 | 2011-09-15 | Schaeffler Technologies Gmbh & Co. Kg | Pumpe, insbesondere Kolbenpumpe für Hoch- oder Niederdruck |
DE102010038468A1 (de) * | 2010-07-27 | 2012-02-02 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102010041178A1 (de) | 2010-09-22 | 2012-03-22 | Robert Bosch Gmbh | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
DE102010043510A1 (de) | 2010-11-05 | 2012-05-10 | Robert Bosch Gmbh | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
DE102010062678A1 (de) | 2010-12-09 | 2012-06-14 | Robert Bosch Gmbh | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
DE102011003396A1 (de) | 2011-01-31 | 2012-08-02 | Continental Automotive Gmbh | Pumpeneinheit für eine Hochdruckpumpe |
JP2012172537A (ja) * | 2011-02-18 | 2012-09-10 | Denso Corp | 燃料供給ポンプ、および燃料供給ポンプの製造方法 |
DE102011077535A1 (de) | 2011-06-15 | 2012-12-20 | Robert Bosch Gmbh | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
DE102011083571A1 (de) * | 2011-09-28 | 2013-03-28 | Robert Bosch Gmbh | Stößelbaugruppe für eine Kraftstoffhochdruckpumpe sowie Kraftstoffhochdruckpumpe |
JP5472340B2 (ja) | 2012-02-10 | 2014-04-16 | 株式会社デンソー | 燃料供給ポンプ |
DE102013210036A1 (de) * | 2013-05-29 | 2014-12-04 | Robert Bosch Gmbh | Hochdruckpumpe für ein Kraftstoffeinspritzsystem |
DE102016203768B4 (de) * | 2015-11-12 | 2017-10-26 | Robert Bosch Gmbh | Pumpe, insbesondere Hochdruckpumpe eines Kraftstoffeinspritzsystems, mit einem Montageverbund von Stößel-Baugruppe und Pumpenzylinderkopf, insbesondere durch eine Rastverbindung zwischen Federteller und Stößelkörper |
JP7120081B2 (ja) * | 2019-03-01 | 2022-08-17 | 株式会社デンソー | 燃料噴射ポンプ |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2301407A (en) * | 1940-06-22 | 1942-11-10 | Dayton Liquid Meter Company | Fuel injection pump |
US2351908A (en) * | 1942-09-18 | 1944-06-20 | Beeh Louis | High-pressure pump |
US4008009A (en) * | 1975-09-30 | 1977-02-15 | Endre Kovacs | Fuel injection pump |
EP0083579A1 (de) * | 1981-03-16 | 1983-07-20 | ANDREW FRASER & COMPANY LIMITED | Radialkolbenpumpe |
DE3380993D1 (de) * | 1982-01-19 | 1990-01-25 | Unipat Ag | Hydraulische radialkolbenmaschinen. |
JP3990732B2 (ja) * | 1996-06-07 | 2007-10-17 | イドロ レデュク | 任意の流体用に使用できる高圧ポンプ |
US5980214A (en) * | 1997-09-12 | 1999-11-09 | Stanadyne Automotive Corp. | Fluid pump with split plungers |
DE19907311A1 (de) * | 1999-02-22 | 2000-08-31 | Bosch Gmbh Robert | Hydraulikpumpeneinheit |
IL128934A (en) * | 1999-03-11 | 2002-11-10 | Mapple Technology Ltd | Power unit |
-
2004
- 2004-01-30 DE DE102004004705A patent/DE102004004705A1/de not_active Withdrawn
- 2004-11-23 EP EP04802795A patent/EP1714030B1/de not_active Expired - Fee Related
- 2004-11-23 ES ES04802795T patent/ES2298845T3/es active Active
- 2004-11-23 WO PCT/DE2004/002584 patent/WO2005073554A1/de active IP Right Grant
- 2004-11-23 US US10/586,871 patent/US7775193B2/en not_active Expired - Fee Related
- 2004-11-23 JP JP2006521395A patent/JP4340289B2/ja not_active Expired - Fee Related
- 2004-11-23 DE DE502004006367T patent/DE502004006367D1/de active Active
- 2004-11-23 CN CNB200480041080XA patent/CN100458150C/zh not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2005073554A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102004004705A1 (de) | 2005-08-18 |
JP2007500303A (ja) | 2007-01-11 |
ES2298845T3 (es) | 2008-05-16 |
US20070154326A1 (en) | 2007-07-05 |
JP4340289B2 (ja) | 2009-10-07 |
DE502004006367D1 (de) | 2008-04-10 |
CN1906411A (zh) | 2007-01-31 |
CN100458150C (zh) | 2009-02-04 |
US7775193B2 (en) | 2010-08-17 |
WO2005073554A1 (de) | 2005-08-11 |
EP1714030B1 (de) | 2008-02-27 |
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