WO2001079687A1 - Pompe haute pression - Google Patents
Pompe haute pression Download PDFInfo
- Publication number
- WO2001079687A1 WO2001079687A1 PCT/JP2001/003260 JP0103260W WO0179687A1 WO 2001079687 A1 WO2001079687 A1 WO 2001079687A1 JP 0103260 W JP0103260 W JP 0103260W WO 0179687 A1 WO0179687 A1 WO 0179687A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure pump
- reaction force
- fastening
- pressure
- pressurizing chamber
- Prior art date
Links
Classifications
-
- 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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
-
- 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
- F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
-
- 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
- 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
- F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
-
- 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
- F02M59/48—Assembling; Disassembling; Replacing
Definitions
- the present invention relates to a high-pressure pump, and in particular, an intermediate member including a cylinder body for increasing the pressure of a fluid in a pressurized chamber by reciprocating a plunger in a cylinder is disposed between two tightening members.
- the present invention relates to a high-pressure pump in which an intermediate member is fastened via two fastening members by fastening bolts spanned between the attached members.
- Japanese Patent Application Laid-Open No. H11-210598 discloses a high-pressure fuel pump used for an engine such as a direct injection gasoline engine.
- an intermediate member such as a sleeve (equivalent to a “cylinder body”) is sandwiched by brackets and other members along the axial direction to improve workability and assemblability. Fastened to the casing.
- a slit is formed between the tightened portion of the sleeve and the cylinder in consideration that the cylinder shape is likely to be deformed when the sleeve is simply tightened. Is formed. This slit suppresses the distortion generated by the tightening of the cylindrical tightening member from affecting the cylinder shape.
- fastening bolts for fastening sleeves require relatively large initial axial forces.
- the reason is that the initial axial force is not only the axial force required for sealing between the intermediate members such as the sleeve, but also the axial force for coping with the axial force change due to fuel pressure pulsation when the high-pressure pump is operating. Because it includes. Therefore, when manufacturing the high-pressure pump, it is necessary to tighten the intermediate member with a considerably large initial axial force in consideration of such a change in the axial force.
- the intermediate member is tightened with a fastening bolt with a large initial axial force, distortion of the seal surface between the intermediate members ⁇ cylinder shape distortion occurs, and the distortion is sufficiently prevented. It is difficult to stop.
- An object of the present invention is to provide a high-pressure pump that prevents distortion from occurring between a seal surface and a cylinder shape.
- an intermediate body including a plunger, a cylinder accommodating the plunger, and a pressurizing chamber communicated with the cylinder, wherein the cylinder body pressurizes the fluid in the pressurizing chamber by reciprocating the plunger.
- a high-pressure pump including the member.
- the high-pressure pump is provided with two fastening members arranged on both sides of the intermediate member, a fastening bolt bridged between the two fastening members, and for fastening the intermediate member with the two fastening members, and a pressurizing chamber.
- the member receiving the reaction force is attached so that the reaction force from the pressurizing chamber acts on the fastening member in a direction in which the fastening to the intermediate member is eased. Therefore, even if the reaction force of the pressurizing chamber acts on the fastening member due to the fluid pressure pulsation during the operation of the high-pressure pump, the reaction force due to the fastening of the intermediate member is reduced by the member receiving the reaction force. Therefore, the total reaction force is smaller than the sum of the reaction force of the pressurizing chamber and the reaction force of the fastening of the intermediate member. Therefore, a change in axial force due to fluid pressure pulsation during operation of the high-pressure pump is reduced. As a result, the initial axial force of the fastening bolt is set to a low value, thereby preventing distortion from the seal surface to the cylinder shape.
- FIG. 1 (A) is a schematic diagram of a high-pressure pump of the present invention in a static state
- FIG. 1 (B) is a schematic diagram of a conventional high-pressure bomb in a static state
- FIG. 2A is a schematic view of the high-pressure pump of the present invention in a dynamic state
- FIG. 2B is a schematic view of a conventional high-pressure pump in a dynamic state.
- FIG. 3 is a longitudinal sectional view of the high-pressure fuel pump according to one embodiment of the present invention.
- FIG. 4 is a schematic diagram of a fuel supply system of an internal combustion engine incorporating the high-pressure fuel pump of FIG.
- FIG. 5 is a longitudinal sectional view of the high-pressure fuel pump according to one embodiment of the present invention.
- an intermediate member M including a cylinder body is arranged between two fastening members E 1 and E 2.
- the intermediate member M is tightened between the tightening members E1 and E2 by the tightening bolts B1 and B2 bridged between the tightening members E1 and E2.
- the member G is attached to the fastening member E1 on the side opposite to the fastening side of the intermediate member M.
- the intermediate member M is elastically deformed by the fastening of the intermediate member M by the fastening bolts Bl and B2, and a reaction force F0 is generated.
- the relationship between this reaction force F0 and the axial force Bf generated in the fastening bolts Bl, B2 is expressed by the following equation [1].
- the member g receives a reaction force from the pressurizing chamber i.
- the member g is arranged between the two fastening members el and e2 together with the intermediate members m1 and m2.
- the intermediate members ml, m2, and member g are elastically deformed by the fastening of the intermediate members ml, m2, and member g by the fastening bolts bl, b2, and a reaction force F0 is generated.
- the relationship between this reaction force F 0 and the axial force bf generated in the fastening bolts b 1 and b 2 is represented by the following equation [2].
- F 0 2 ⁇ bf ⁇ [2]
- the reaction force FN When the reaction force FN is generated due to the increase in the pressure of the pressurizing chamber I, in the high-pressure pump of the present invention shown in FIG. receive. Since the member G is attached to the intermediate member M on the side opposite to the tightening side, the reaction force FN acts as a force FU for lifting the tightening member E1.
- This lifting force FU is one element of the axial force Bf generated in the fastening bolts Bl, B2.
- Another element of the axial force ⁇ ⁇ is the reaction force FM from the intermediate member ⁇ . Therefore, the axial force B f is expressed by the following equation [3].
- the reaction force FM from the intermediate member M reduces the amount of compression of the intermediate member M and reduces the amount of compression of the intermediate member M in accordance with the degree to which the fastening member E1 is pulled up by the lifting force FU. It becomes smaller than the reaction force F 0 of (A).
- the member g receiving the reaction force FN from the pressurizing chamber i is arranged on the tightening side together with the intermediate members ml and m2.
- the pushing force FU of the fastening member e1 due to the reaction force FN is one element of the axial force bf generated in the fastening bolts b1 and b2.
- Another component of the axial force b f is the reaction force Fm from the intermediate members m 1 and m 2 and the member g. Therefore, the axial force b f is expressed by the following equation [4].
- the reaction force FN is almost the same as the reaction force F 0 in Fig. 1 (B). Even if the reaction force FN decreases, the degree of the decrease depends on the reaction force F 0 in FIG.
- the reaction force is less than the difference from FM. That is, FM and Fm. Therefore, in the states of FIGS. 2A and 2B, Bf ⁇ bf.
- the high-pressure pump of the present invention when the pressure of the fluid in the pressurizing chamber is increased, the increase in the axial force of the fastening bolt due to the reaction force received from the pressurizing chamber is suppressed. In other words, the change in axial force due to fluid pressure pulsation during operation of the high-pressure pump is reduced, and the initial axial force of the fastening bolt can be set relatively low. Therefore, distortion between the sealing surface and the cylinder shape is prevented.
- FIG. 3 is a longitudinal sectional view of the high-pressure fuel pump 2 according to one embodiment of the present invention.
- the high-pressure fuel pump 2 is incorporated in the direct injection gasoline engine E, and generates high-pressure fuel for injecting fuel into the combustion chamber of the engine E.
- the high-pressure fuel pump 2 includes a cylinder body 4, a cover 6, a flange 8, and an electromagnetic spill valve 10.
- a cylinder 4a is formed at the center axis position of the cylinder body 4, and a plunger 12 is slidably supported in the cylinder 4a in the axial direction.
- a pressurizing chamber 14 communicated with the cylinder 4a is formed in the cylinder body 4 on the tip side of the cylinder 4a, and the volume of the pressurizing chamber 14 changes as the plunger 12 enters and exits.
- the pressurizing chamber 14 is connected to a check valve 18 via a fuel pressure feed path 16.
- the check valve 18 is connected to a fuel distribution pipe 20 (FIG. 4). The check valve 18 is opened when the fuel in the pressurizing chamber 14 is pressurized, and the high-pressure fuel is supplied to the fuel distribution pipe 20.
- a springer sheet 22 and a lifter guide 24 are laminated on the lower side of the cylinder body 4.
- An oil seal 26 is attached to the inner peripheral surface of the springer sheet 22.
- the oil seal 26 is formed in a substantially cylindrical shape, and has a lower end 26 a that is slidably adhered to the outer peripheral surface of the plunger 12. The fuel leaked from the gap between the plunger 12 and the cylinder 4a is accumulated in the fuel storage chamber 26b of the oil seal 26, and then the fuel discharge path (not shown) connected to the fuel storage chamber 26b Is returned to the fuel tank T via.
- a lifter 28 is housed in the lifter guide 24 so as to be slidable in the axial direction.
- a projecting portion 28b is formed on the inner surface of the bottom plate portion 28a of the lifter 28, and the lower end portion 12a of the plunger 12 is in contact with the projecting portion 28b.
- the lower end 12 a of the plunger 12 is engaged with the retainer 30.
- a spring 32 is arranged in a compressed state between the springer seat 22 and the retainer 30, and the lower end 12 a of the plunger 12 is supported by the spring 32 so that the lifter 28 protrudes. Part 28 is pressed against the b side.
- the bottom plate 28 a of the lifter 28 is in contact with the fuel pump cam 34 by the pressing force from the lower end 12 a of the plunger 12.
- the electromagnetic spill valve 10 disposed opposite to the pressurizing chamber 14 is closed.
- the fuel in the pressurizing chamber 14 flows between the poppet valve 10a of the electromagnetic spill valve 10 and the seat 10b and the fuel path. It returns to the fuel tank T on the low pressure side via 10 c, gallery 10 d and the low pressure fuel passage 35. Therefore, no fuel is supplied from the pressurizing chamber 14 to the fuel distribution pipe 20.
- the electromagnetic spill valve 10 is closed by driving the electromagnetic circuit inside the electromagnetic spill valve 10 so that the port valve 10a comes into contact with the seat 10b, and pressurizes the low-pressure side fuel tank T. Chamber 14 is shut off (state of Fig. 4). Then, the pressure of the fuel in the pressurizing chamber 14 rapidly rises, and the high-pressure fuel generated thereby pushes and opens the check valve 18 to supply the high-pressure fuel to the fuel distribution pipe 20.
- Such a pressurizing process and a suction process are repeated, and by controlling the valve closing timing of the electromagnetic spill valve 10 in the pressurizing process by feedback, the fuel pressure in the fuel distribution pipe 20 is reduced by the fuel injection valve 3 8 The pressure is adjusted to a value appropriate for jetting from.
- the feedback control is performed by the electronic control unit (ECU) 36 according to the fuel pressure in the fuel distribution pipe 20 detected by the fuel pressure sensor 20a and other engine operating conditions.
- the cylinder body 4, the spring seat 22 and the lifter guide 24 are configured as intermediate members of the high-pressure fuel pump 2, and in a stacked state, the cover 6 (first tightening member) and the flange 8 (second (Fastening member).
- the electromagnetic spill valve 10 has a board 10 f, and the board 10 ⁇ is opposite to the tightening side of the cylinder body 4, the spring seat 22 and the lifter guide 24 by the mounting bolt 10 e.
- the cover 6 first tightening member
- the flange 8 second (Fastening member).
- the electromagnetic spill valve 10 has a board 10 f, and the board 10 ⁇ is opposite to the tightening side of the cylinder body 4, the spring seat 22 and the lifter guide 24 by the mounting bolt 10 e.
- FIG. 3 shows a longitudinal sectional view of the high-pressure fuel pump 2 on the same cut surface. As shown in FIG. 5, two fastening bolts 40 are symmetrically arranged about the central axis. In the present embodiment, two sets of fastening bolts 40 are symmetrically arranged around cylinder body 4, spring seat 22 and lifter guide 24, and fasten cover 6 and flange 8.
- mounting bolts 10 e for attaching the electromagnetic spill valve 10 to the cover 16 are also arranged symmetrically about the center axis of the cylinder 12.
- the substrate 10 f of the electromagnetic spill valve 10 is attached to the cover 16 by two sets of mounting bolts 10 e. Have been.
- the entire high-pressure fuel pump 2 is attached to a cylinder head cover 52 as a support by an assembly bolt 54.
- the flange 8 has a fastening bolt hole 8b through which the fastening bolt 40 penetrates, and an assembly bolt hole formed on the outer peripheral side further than the fastening bolt hole 8b to allow the assembly bolt 54 to pass therethrough. 8 c are formed.
- a mounting bolt 54 is inserted through the mounting bolt hole 8c from the opposite direction to the fastening bolt 40, and the mounting bolt 54 is a screw hole provided in the cylinder head cover 152. It is screwed into 52 a.
- the two sets of assembling bolts 54 are arranged symmetrically about the central axis of the cylinder 12.
- the high-pressure fuel pump 2 is attached to the cylinder head cover 52.
- the bottom plate 28 a of the lifter 28 is exposed from the through hole 53 of the cylinder head cover 52 and is in contact with the fuel pump cam 34 of the engine E.
- the plunger 12 reciprocates in the cylinder 4a in conjunction with the rotation of the engine E.
- the high-pressure fuel pump 2 of the present invention has the following advantages.
- the electromagnetic spill valve 10 is attached to the cover 6 on the side opposite to the tightening side of the cylinder body 4, the spring seat 22 and the lifter guide 24.
- the port valve 10a of the electromagnetic spill valve 10 receives a reaction force (arrow in FIG. 3) from the pressurizing chamber 14 when seated on the seat 10b. Therefore, as described in FIG. 1 (A) and FIG. 2 (A), the increase in the axial force of the fastening bonole 40 due to the reaction force that the electromagnetic spill valve 10 receives from the pressurizing chamber 14 is Smaller than when the valve is mounted on the same side as the cylinder body 4, spring seat 22 and lifter guide 24.
- the high-pressure fuel pump of the present invention may be mounted on a cylinder head of an engine.
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/257,651 US7287967B2 (en) | 2000-04-18 | 2001-04-17 | High-pressure pump having small initial axial force of a clamping bolt |
DE60119722T DE60119722T2 (de) | 2000-04-18 | 2001-04-17 | Hochdruckpumpe |
EP01921852A EP1277950B1 (en) | 2000-04-18 | 2001-04-17 | High-pressure pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000-116421 | 2000-04-18 | ||
JP2000116421A JP3905282B2 (ja) | 2000-04-18 | 2000-04-18 | 高圧ポンプ |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001079687A1 true WO2001079687A1 (fr) | 2001-10-25 |
Family
ID=18627889
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2001/003260 WO2001079687A1 (fr) | 2000-04-18 | 2001-04-17 | Pompe haute pression |
Country Status (7)
Country | Link |
---|---|
US (1) | US7287967B2 (ja) |
EP (1) | EP1277950B1 (ja) |
JP (1) | JP3905282B2 (ja) |
KR (1) | KR100579435B1 (ja) |
CN (1) | CN100436809C (ja) |
DE (1) | DE60119722T2 (ja) |
WO (1) | WO2001079687A1 (ja) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004270641A (ja) * | 2003-03-11 | 2004-09-30 | Yanmar Co Ltd | ディーゼルエンジン |
JP2006170184A (ja) | 2004-11-16 | 2006-06-29 | Denso Corp | 高圧燃料ポンプ |
JP2007120492A (ja) * | 2005-09-29 | 2007-05-17 | Denso Corp | 高圧燃料ポンプ |
CN100365267C (zh) * | 2005-11-16 | 2008-01-30 | 中国兵器工业集团第七○研究所 | 压装法兰柱塞套结构 |
WO2007083404A1 (ja) * | 2006-01-20 | 2007-07-26 | Bosch Corporation | 内燃機関の燃料噴射システム |
GB0812888D0 (en) * | 2008-07-15 | 2008-08-20 | Delphi Tech Inc | Improvements relating to fuel pumps |
JP5642925B2 (ja) * | 2008-08-20 | 2014-12-17 | 日産自動車株式会社 | 高圧燃料ポンプ |
EP2278163A1 (en) * | 2009-07-20 | 2011-01-26 | Delphi Technologies Holding S.à.r.l. | Pump assembly |
JP5382548B2 (ja) * | 2011-03-31 | 2014-01-08 | 株式会社デンソー | 高圧ポンプ |
WO2013035131A1 (ja) * | 2011-09-06 | 2013-03-14 | トヨタ自動車株式会社 | 燃料ポンプおよび内燃機関の燃料供給システム |
CN104204519B (zh) * | 2012-02-01 | 2016-08-03 | S.P.M.流量控制股份有限公司 | 具有集成腹板部分的泵流体端 |
GB201418661D0 (en) * | 2014-10-21 | 2014-12-03 | Delphi International Operations Luxembourg S.�.R.L. | Pumping Mechanism |
DE102015222065A1 (de) * | 2015-11-10 | 2017-05-11 | Robert Bosch Gmbh | Kolbenpumpe mit Auslassventil im Kolben |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS51132321A (en) * | 1975-03-27 | 1976-11-17 | Vysoke Uceni Tech Brne | Injection unit of injection pump for diesel engine |
JPS5399131A (en) * | 1977-02-10 | 1978-08-30 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engine |
JPS57181967A (en) * | 1981-04-16 | 1982-11-09 | Mach Terumitsuku Soc Et | Regulator for moment of fuel injection for fuel injection pump of internal combustion engine |
Family Cites Families (27)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1500164A (en) * | 1974-04-01 | 1978-02-08 | Bosch Gmbh Robert | Fuel injection pumps for internal combustion engines |
DE2503324C2 (de) * | 1975-01-28 | 1985-10-31 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
DE3141654A1 (de) * | 1981-10-21 | 1983-05-05 | L'Orange GmbH, 7000 Stuttgart | Kraftstoffeinspritzpumpe, insbesondere fuer eine dieselbrennkraftmaschine |
DE3141653A1 (de) | 1981-10-21 | 1983-05-05 | L'Orange GmbH, 7000 Stuttgart | Kraftstoffeinspritzpumpe, insbesondere fuer eine dieselbrennkraftmaschine |
US4450685A (en) * | 1982-06-02 | 1984-05-29 | Mechanical Technology Incorporated | Dynamically balanced, hydraulically driven compressor/pump apparatus for resonant free piston Stirling engines |
DE3302294A1 (de) | 1983-01-25 | 1984-07-26 | Klöckner-Humboldt-Deutz AG, 5000 Köln | Kraftstoffeinspritzvorrichtung fuer luftverdichtende, selbstzuendende brennkraftmaschinen |
JPH0657526B2 (ja) * | 1985-05-20 | 1994-08-03 | 株式会社日本自動車部品総合研究所 | 車両用アンチスキツド・ブレ−キ装置 |
GB8822901D0 (en) * | 1988-09-29 | 1988-11-02 | Mactaggart Scot Holdings Ltd | Apparatus & method for controlling actuation of multi-piston pump &c |
DE3934953A1 (de) * | 1989-10-20 | 1991-04-25 | Bosch Gmbh Robert | Magnetventil, insbesondere fuer kraftstoffeinspritzpumpen |
US5092744A (en) * | 1990-03-14 | 1992-03-03 | Possis Corporation | Intensifier |
DE4225302C2 (de) * | 1992-07-31 | 2003-05-15 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
US5362215A (en) * | 1993-05-10 | 1994-11-08 | Halliburton Company | Modular pump cylinder-head having integral over-pressure protection |
JPH08285125A (ja) * | 1995-04-12 | 1996-11-01 | Koganei Corp | 弁装置および弁装置を有する薬液供給装置 |
DE19527720A1 (de) | 1995-07-31 | 1997-02-06 | Woodward Governor Germany Gmbh | Verfahren zur Veränderung des Förderbeginns von Kraftstoffeinspritzpumpen und Kraftstoffeinspritzpumpe |
JPH09250427A (ja) | 1996-03-15 | 1997-09-22 | Zexel Corp | 燃料噴射ポンプ |
JPH1018941A (ja) | 1996-07-01 | 1998-01-20 | Mitsubishi Electric Corp | 可変吐出量高圧ポンプ |
JP3581861B2 (ja) * | 1996-07-05 | 2004-10-27 | 株式会社日本自動車部品総合研究所 | 高圧供給ポンプ |
JP3750203B2 (ja) | 1996-07-12 | 2006-03-01 | 株式会社デンソー | 高圧サプライポンプ |
JP3257423B2 (ja) * | 1996-12-12 | 2002-02-18 | 三菱自動車工業株式会社 | 排気昇温装置 |
JP3309765B2 (ja) * | 1997-05-16 | 2002-07-29 | 三菱電機株式会社 | 高圧燃料供給ポンプ |
JPH1182236A (ja) | 1997-09-12 | 1999-03-26 | Denso Corp | 点火式内燃機関用の燃料供給装置 |
JPH1182239A (ja) | 1997-09-12 | 1999-03-26 | Denso Corp | 燃料供給装置及びその製造方法 |
JP2857139B1 (ja) | 1998-01-30 | 1999-02-10 | 三菱電機株式会社 | 高圧燃料供給ポンプ |
US6171081B1 (en) * | 1998-02-17 | 2001-01-09 | Keihin Corporation | Fuel pump assembly |
JP2000045907A (ja) | 1998-08-04 | 2000-02-15 | Toyota Motor Corp | 燃料ポンプ |
JP3851056B2 (ja) * | 2000-04-18 | 2006-11-29 | トヨタ自動車株式会社 | 高圧ポンプ |
US6783333B2 (en) * | 2003-01-15 | 2004-08-31 | Min-Hsieng Wang | Air compressor |
-
2000
- 2000-04-18 JP JP2000116421A patent/JP3905282B2/ja not_active Expired - Fee Related
-
2001
- 2001-04-17 CN CNB018113826A patent/CN100436809C/zh not_active Expired - Lifetime
- 2001-04-17 US US10/257,651 patent/US7287967B2/en not_active Expired - Lifetime
- 2001-04-17 DE DE60119722T patent/DE60119722T2/de not_active Expired - Lifetime
- 2001-04-17 KR KR1020027013900A patent/KR100579435B1/ko active IP Right Grant
- 2001-04-17 EP EP01921852A patent/EP1277950B1/en not_active Expired - Lifetime
- 2001-04-17 WO PCT/JP2001/003260 patent/WO2001079687A1/ja active IP Right Grant
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS51132321A (en) * | 1975-03-27 | 1976-11-17 | Vysoke Uceni Tech Brne | Injection unit of injection pump for diesel engine |
JPS5399131A (en) * | 1977-02-10 | 1978-08-30 | Bosch Gmbh Robert | Fuel injection pump for internal combustion engine |
JPS57181967A (en) * | 1981-04-16 | 1982-11-09 | Mach Terumitsuku Soc Et | Regulator for moment of fuel injection for fuel injection pump of internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
CN100436809C (zh) | 2008-11-26 |
US7287967B2 (en) | 2007-10-30 |
JP3905282B2 (ja) | 2007-04-18 |
EP1277950A1 (en) | 2003-01-22 |
CN1437681A (zh) | 2003-08-20 |
KR100579435B1 (ko) | 2006-05-15 |
JP2001295730A (ja) | 2001-10-26 |
EP1277950B1 (en) | 2006-05-17 |
DE60119722T2 (de) | 2006-10-12 |
KR20020089484A (ko) | 2002-11-29 |
US20030103853A1 (en) | 2003-06-05 |
EP1277950A4 (en) | 2005-02-16 |
DE60119722D1 (de) | 2006-06-22 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7114928B2 (en) | High-pressure fuel pump and assembly structure of high-pressure pump | |
JP3823060B2 (ja) | 高圧燃料供給ポンプ | |
JP4415929B2 (ja) | 高圧燃料供給ポンプ | |
JP5501272B2 (ja) | 高圧燃料供給ポンプ | |
EP2410167B1 (en) | Pulsation damper | |
WO2001079687A1 (fr) | Pompe haute pression | |
WO2017203861A1 (ja) | 高圧燃料供給ポンプ | |
JP4199930B2 (ja) | 燃料高圧供給用のピストンポンプ | |
JP5589121B2 (ja) | 高圧燃料供給ポンプ | |
CN109072846B (zh) | 高压泵 | |
WO2018092538A1 (ja) | 高圧燃料供給ポンプ | |
JP2007218213A (ja) | 高圧燃料供給ポンプ及びその組立方法 | |
US6520156B2 (en) | High-pressure fuel supply system | |
JP4552834B2 (ja) | 燃料噴射装置 | |
CN108779766B (zh) | 具有流体阻尼器的高压泵 | |
JP5703893B2 (ja) | 高圧ポンプ | |
JP6681487B2 (ja) | 高圧燃料供給ポンプ | |
JP5910143B2 (ja) | 燃料ポンプ構造 | |
JP3744329B2 (ja) | 高圧燃料ポンプ | |
JP5178618B2 (ja) | 高圧燃料供給ポンプ | |
WO2022014150A1 (ja) | 燃料ポンプ | |
JP2014148980A (ja) | 高圧燃料供給ポンプ | |
JP5942816B2 (ja) | 高圧燃料ポンプ | |
JP2004285967A (ja) | 燃料供給システム及び高圧燃料供給装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): CN KR US |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
DFPE | Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 10257651 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1020027013900 Country of ref document: KR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2001921852 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 1020027013900 Country of ref document: KR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 018113826 Country of ref document: CN |
|
WWP | Wipo information: published in national office |
Ref document number: 2001921852 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 1020027013900 Country of ref document: KR |
|
WWG | Wipo information: grant in national office |
Ref document number: 2001921852 Country of ref document: EP |