WO2009021865A1 - Pumpe, insbesondere kraftstoffhochdruckpumpe - Google Patents
Pumpe, insbesondere kraftstoffhochdruckpumpe Download PDFInfo
- Publication number
- WO2009021865A1 WO2009021865A1 PCT/EP2008/060172 EP2008060172W WO2009021865A1 WO 2009021865 A1 WO2009021865 A1 WO 2009021865A1 EP 2008060172 W EP2008060172 W EP 2008060172W WO 2009021865 A1 WO2009021865 A1 WO 2009021865A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pump
- drive shaft
- pump piston
- coupling device
- indirectly
- Prior art date
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
- F04B1/0404—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
- the invention relates to a pump, in particular high-pressure fuel pump according to the preamble of claim 1.
- Such a pump in the form of a high-pressure fuel pump is through
- This pump has at least one pump piston, which is tightly guided in a cylinder bore of a housing part of the pump.
- the pump also has a drive shaft, which with a
- Drive section is provided in the form of a cam or eccentric, by which the at least one pump piston is driven at least indirectly in a stroke movement.
- the at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft. During the delivery stroke of the pump piston this is against the force of
- the spring element is moved into the cylinder bore through the drive section and during the suction stroke of the pump piston this is moved out of the cylinder bore by the force of the spring element.
- the spring element is designed as a cylindrical helical compression spring, which surrounds the housing part, in which the cylinder bore is formed and the pump piston is arranged. This arrangement of the spring element causes the wall thickness of the housing part in the cylinder bore surrounding area must be kept relatively low to allow the arrangement of the spring element. As a result of the high pressure generated during the delivery stroke of the pump piston, there may be a widening of the cylinder bore due to the relatively small wall thickness of the housing part, so that leakage losses occur. Disclosure of the invention
- the pump according to the invention with the features of claim 1 has the advantage that by the arrangement of the spring element on the pump piston opposite side of the drive shaft, the housing part in the cylinder bore surrounding area can be formed with a large wall thickness, so that no or only small leakage losses caused by a widening of the cylinder bore.
- FIG. 1 shows a detail of a pump in a longitudinal section
- FIG. 2 shows the pump in a cross section along line N-II in FIG. 1
- FIG. 3 shows a modified embodiment of the pump in cross section N-II.
- a pump which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine.
- the pump has a housing 10, which may be designed in several parts and in which in a housing part 12, a rotationally driven drive shaft 14 is rotatably disposed about an axis of rotation 15.
- the drive shaft 14 is mounted in the housing part 12 via two spaced apart in the direction of the axis of rotation 15 of the drive shaft 14 bearing points.
- the drive shaft 14 has at least one drive section 16, which is a cam or an eccentric can be.
- the pump has at least one or more pump elements, each with a pump piston 20 which is driven by the drive portion 16 of the drive shaft 14 at least indirectly in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14.
- the pump piston 20 is in a cylinder bore 22 of a housing part
- the pump piston 20 in the cylinder bore 22 defines a pump working chamber 26.
- the pump working chamber 26 has an inlet check valve 30 opening into this connection with a feed 34 coming from a feed pump 32, via which the pump working space
- the pump working chamber 26 is directed at the radially inwardly to the rotational axis 15 of the drive shaft 14 directed suction stroke of the pump piston 20 with fuel.
- the pump working chamber 26 also has an outlet check valve 36 which opens out of this connection with a drain 38 which leads, for example, to a high-pressure fuel accumulator 40 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotational axis 15 of the drive shaft 14 the pump working space 26 is displaced.
- the housing part 24 has a flange-like portion 42 which on
- Housing 12 rests, and projecting from the area 42 cylindrical projection 44, which projects into an at least approximately radially to the axis of rotation 15 of the drive shaft 14 extending opening 46, which is formed for example as a bore in the housing part 12.
- the cylinder bore 22 extends from the end face of the projection 44 through the projection 44 into the
- the drive portion 16 of the drive shaft 14 is formed as shown in FIG 2 as a double cam and the pump piston 20 is supported via a roller tappet 48 on the double cam. - A -
- the roller tappet 48 comprises a sleeve-shaped tappet body 50 guided in the bore 46 of the housing part 24, a roller shoe 52 inserted in the tappet body 50 and a roller 54 rotatably mounted in a housing 53 in the roller shoe 52.
- the roller 54 rolls on the double cam 16 and is slid in the receptacle 53.
- the plunger body 50 may also be guided over its inner jacket on the projection 44 of the housing part 24.
- the pump piston 20 has an enlarged diameter in relation to the area guided in the cylinder bore 22 in the area of the piston foot, via which the pump piston 20 is coupled to the roller tappet 48 in the direction of its longitudinal axis.
- the drive portion 16 of the drive shaft 14 is formed as an eccentric, wherein the pump piston 20 directly or via a plunger, such as a cup tappet 148, on the eccentric or on one on the Eccentric rotatably mounted ring 150 is applied.
- the ring 150 may have an at least approximately flat flattening 152 in the region of the abutment of the pump piston 20 or of the plunger 148.
- the spring element 56 is arranged on the pump piston 20 opposite side of the drive shaft 14 in the housing 10 of the pump.
- the spring element 56 engages via a coupling device 58 at least indirectly on the pump piston 20.
- the coupling device 58 is connected to the plunger body 50 of the roller tappet 48 and the plunger 148 and thus indirectly via this with the pump piston 20.
- the coupling device 58 has for example two carrier-shaped parts 60, wherein in each case a carrier 60 laterally adjacent to the drive section 16 of the drive shaft 14 is arranged.
- Carrier 60 are formed so that they have a small thickness as shown in Figure 1 in the direction of the axis of rotation 15 of the drive shaft 14. Viewed in the direction of the axis of rotation 15 of the drive shaft 15, the carriers 60, as shown in FIGS. 2 and 3, have a central hub-like region 62 with a large width in the area of the drive shaft 14 and adjoining it the drive shaft 14 radially extending arms 64 with a smaller width. The arms 64 are arranged at least approximately diametrically opposite each other. In the hub region 62 of the carrier 60, a slot 66 is respectively introduced, through which the drive shaft 14 passes.
- the two carriers 60 of the coupling device 58 are preferably formed identically to the
- the arms 64 of the carriers 60 of the coupling device 58 which extend to the tappet body 50 are connected at their end regions to the tappet body 50 or the tappet 148, for example by means of screws, rivets, by a welded connection or in some other way.
- the arms 64 of the carrier 60 of the coupling device 58 extend approximately to the level of the foot of the pump piston 20 and terminate at a distance in front of the end face of the projection 44 of the housing part 24.
- the spring element 56 is designed, for example, as a cylindrical helical compression spring and clamped between the component 68 and a housing 10 of the pump, the drive portion 16 of the drive shaft 14 arranged adjacent stationary support 70.
- Support 70 is arranged at a sufficient distance from the drive section 16 in order to avoid contact with the drive section 16 during the rotation of the drive shaft 14.
- Roller tappet 48 a lifting movement.
- This lifting movement also carries out the coupling device 58, wherein the spring element 56 is alternately compressed and relaxed.
- the coupling device 58 Through the elongated holes 66 in the carriers 60 of the coupling device 58, the lifting movement of the coupling device 58 with respect to the drive shaft 14 is made possible. Due to the arrangement of the
- Spring element 56 on the pump piston 20 opposite side of the drive shaft 14 is between the portion 44 of the housing part 24 and the bore 46 in the housing part 12, only an annular gap with a small width for receiving the plunger body 50 is required.
- the plunger body 50 can be designed with a small wall thickness, so that the annular gap is correspondingly narrow can be held. This allows an embodiment of the projection 44 of the housing part 24 up to the front side with a large wall thickness, whereby the cylinder bore 22 under the action of the high pressure in the pump working chamber 26 during delivery of the pump piston 20 only slightly expands and correspondingly low leakage losses from the
- the pump may also have a plurality of, for example, two pump pistons 20.
- the two pump piston 20 can thereby at an angle of about
- the coupling devices 58 of the two pump pistons 20 preferably extend in the direction of the axis of rotation 15 of the drive shaft 14 to each other, so that they do not interfere with each other.
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010520528A JP5119332B2 (ja) | 2007-08-16 | 2008-08-01 | ポンプ、特に燃料高圧ポンプ |
AT08802955T ATE517257T1 (de) | 2007-08-16 | 2008-08-01 | Pumpe, insbesondere kraftstoffhochdruckpumpe |
CN2008801029495A CN101779038B (zh) | 2007-08-16 | 2008-08-01 | 泵、尤其燃料高压泵 |
US12/673,500 US8337178B2 (en) | 2007-08-16 | 2008-08-01 | Pump, particularly high-pressure fuel pump |
EP08802955A EP2188525B1 (de) | 2007-08-16 | 2008-08-01 | Pumpe, insbesondere kraftstoffhochdruckpumpe |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007038525.2 | 2007-08-16 | ||
DE102007038525A DE102007038525A1 (de) | 2007-08-16 | 2007-08-16 | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2009021865A1 true WO2009021865A1 (de) | 2009-02-19 |
Family
ID=40010491
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2008/060172 WO2009021865A1 (de) | 2007-08-16 | 2008-08-01 | Pumpe, insbesondere kraftstoffhochdruckpumpe |
Country Status (8)
Country | Link |
---|---|
US (1) | US8337178B2 (de) |
EP (1) | EP2188525B1 (de) |
JP (1) | JP5119332B2 (de) |
KR (1) | KR20100042646A (de) |
CN (1) | CN101779038B (de) |
AT (1) | ATE517257T1 (de) |
DE (1) | DE102007038525A1 (de) |
WO (1) | WO2009021865A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008000824A1 (de) * | 2008-03-26 | 2009-10-01 | Robert Bosch Gmbh | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
DE102010041340A1 (de) * | 2010-09-24 | 2012-03-29 | Robert Bosch Gmbh | Spannstift |
CN101985920B (zh) * | 2010-10-27 | 2012-07-04 | 牛彦波 | 一种水切割机或水清洗机用环形超高压增压器 |
JP2013130114A (ja) * | 2011-12-21 | 2013-07-04 | Bosch Corp | 燃料供給ポンプ |
JP5677329B2 (ja) * | 2012-01-20 | 2015-02-25 | 日立オートモティブシステムズ株式会社 | 電磁駆動型の吸入弁を備えた高圧燃料供給ポンプ |
DE102014220878A1 (de) * | 2014-10-15 | 2016-04-21 | Continental Automotive Gmbh | Kraftstoffhochdruckpumpe |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE7305570U (de) | 1973-02-14 | 1973-08-16 | Zahnradfabrik Friedrichshafen Ag | Federnde Halterung des Kolbens in einer Radialkolbenmaschine |
DE19503621A1 (de) | 1995-02-03 | 1996-08-08 | Bosch Gmbh Robert | Hubkolbenpumpe |
DE19848040A1 (de) * | 1998-10-17 | 2000-04-20 | Bosch Gmbh Robert | Kolbenpumpe zur Kraftstoffhochdruckversorgung |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1893216A (en) * | 1928-03-15 | 1933-01-03 | Abraham M Babitch | Linkage for fuel pumps |
US1893217A (en) * | 1928-09-10 | 1933-01-03 | Abraham M Babitch | Fuel pump with lost motion lever |
US2036452A (en) * | 1934-12-06 | 1936-04-07 | Gen Motors Corp | Fuel pump |
US2139347A (en) * | 1936-04-08 | 1938-12-06 | Gen Motors Corp | Fuel pump |
US2359960A (en) * | 1943-08-12 | 1944-10-10 | Chicago & Southern Air Lines I | Pumping mechanism |
US3314365A (en) * | 1964-08-24 | 1967-04-18 | Douglas E Ritchie | Direct acting variable pump |
US3924970A (en) * | 1973-11-28 | 1975-12-09 | Gen Motors Corp | Electrically controlled fuel pump |
DE4027794C2 (de) * | 1990-09-01 | 2002-06-20 | Continental Teves Ag & Co Ohg | Hydraulische Radialkolbenpumpe |
US6506033B2 (en) * | 2000-10-26 | 2003-01-14 | Okenseiko Co., Ltd. | Miniature pump with ball-plate drive |
JP4439723B2 (ja) * | 2000-12-28 | 2010-03-24 | 株式会社ミクニ | 燃料ポンプ |
DE102008000824A1 (de) * | 2008-03-26 | 2009-10-01 | Robert Bosch Gmbh | Pumpe, insbesondere Kraftstoffhochdruckpumpe |
-
2007
- 2007-08-16 DE DE102007038525A patent/DE102007038525A1/de not_active Withdrawn
-
2008
- 2008-08-01 WO PCT/EP2008/060172 patent/WO2009021865A1/de active Application Filing
- 2008-08-01 AT AT08802955T patent/ATE517257T1/de active
- 2008-08-01 JP JP2010520528A patent/JP5119332B2/ja not_active Expired - Fee Related
- 2008-08-01 EP EP08802955A patent/EP2188525B1/de not_active Not-in-force
- 2008-08-01 CN CN2008801029495A patent/CN101779038B/zh not_active Expired - Fee Related
- 2008-08-01 US US12/673,500 patent/US8337178B2/en not_active Expired - Fee Related
- 2008-08-01 KR KR1020107003190A patent/KR20100042646A/ko not_active Application Discontinuation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE7305570U (de) | 1973-02-14 | 1973-08-16 | Zahnradfabrik Friedrichshafen Ag | Federnde Halterung des Kolbens in einer Radialkolbenmaschine |
DE19503621A1 (de) | 1995-02-03 | 1996-08-08 | Bosch Gmbh Robert | Hubkolbenpumpe |
DE19848040A1 (de) * | 1998-10-17 | 2000-04-20 | Bosch Gmbh Robert | Kolbenpumpe zur Kraftstoffhochdruckversorgung |
Also Published As
Publication number | Publication date |
---|---|
CN101779038B (zh) | 2012-11-14 |
ATE517257T1 (de) | 2011-08-15 |
JP2010537096A (ja) | 2010-12-02 |
JP5119332B2 (ja) | 2013-01-16 |
CN101779038A (zh) | 2010-07-14 |
EP2188525A1 (de) | 2010-05-26 |
EP2188525B1 (de) | 2011-07-20 |
US20110200463A1 (en) | 2011-08-18 |
KR20100042646A (ko) | 2010-04-26 |
DE102007038525A1 (de) | 2009-02-19 |
US8337178B2 (en) | 2012-12-25 |
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