WO2004111436A1 - 低温始動進角機構を備える燃料噴射ポンプ - Google Patents
低温始動進角機構を備える燃料噴射ポンプ Download PDFInfo
- Publication number
- WO2004111436A1 WO2004111436A1 PCT/JP2004/006221 JP2004006221W WO2004111436A1 WO 2004111436 A1 WO2004111436 A1 WO 2004111436A1 JP 2004006221 W JP2004006221 W JP 2004006221W WO 2004111436 A1 WO2004111436 A1 WO 2004111436A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- plunger
- fuel injection
- port
- csd
- overflow
- 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
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
- F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
- F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/32—Varying fuel delivery in quantity or timing fuel delivery being controlled by means of fuel-displaced auxiliary pistons, which effect injection
-
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
Definitions
- the present invention relates to a structure of a fuel injection pump for a diesel engine having a low temperature start advance mechanism, and more particularly, to a technique for optimizing a fuel injection timing and an injection amount at a low temperature start.
- a plunger is slid up and down within a plunger barrel to send fuel pressure-fed to a distribution shaft to a plurality of discharge valves by the distribution shaft, and pressure-fed from each discharge valve to a fuel injection nozzle.
- a fuel injection pump for a diesel engine having a configuration is known.
- an overflow subport is formed in the plunger barrel, and an advance angle actuating section is operated, whereby the injection timing is changed by opening and closing the overflow subport.
- an advance mechanism hereinafter referred to as “CSD (Cold Start Device)”.
- the CSD controls the advance of the injection timing by closing the overflow sub-port at the time of low-temperature start, By controlling the advance angle, the startability of the engine is improved.
- the overflow sub-port which is open at normal temperature, is closed by a piston that is operated by an advance actuator, whereby the plunger is operated. Closes the main port with respect to the fuel pressure chamber, and at the same time, starts fuel pumping from the fuel pressure chamber to the distribution shaft.
- the amount of advance and the amount of change in the injection amount when the overflow sub-port is closed (when CSD is activated) with respect to when the overflow sub-port is open (when CSD is not activated) are different from the plan.
- Main port of overflow subport formed in the jar barrel The performance is uniquely determined when the CSD is not operating (at normal temperature (when warm)) and when the CSD is operating (when the temperature is low (cool)) It was difficult to optimize the starting performance of the vehicle.
- the present invention has a low-temperature starting advancement mechanism that changes the injection timing by opening and closing a subport provided in a barrel by a piston that is operated by an advancement actuating mechanism.
- the subport, the main port, and the fuel pressure chamber are connected to each other.
- the barrel is provided with at least one overflow-dedicated subport that is always open regardless of the operation of the piston.
- the fuel injection amount and fuel injection when the CSD is activated (at cold start (cold)) compared to when the CSD is not activated (at normal temperature (during warm))
- the amount of change in timing can be set arbitrarily, and the fuel injection amount and injection timing during CSD operation can be optimized while maintaining the characteristics when CSD is not operating.
- the overflow-dedicated subport is provided between the main port and the subport that can be opened and closed by the piston in the plunger moving direction.
- the fuel injection pump maintains the characteristics when the CSD is not operating (at normal temperature (when in the cold state)) and the fuel injection timing and injection when the CSD is operating (when the cold start (in the cold state)).
- the amount of change in the amount of the CSD when the CSD is not operating can be made smaller than before, ensuring the performance during warm conditions and optimizing the start at low temperatures.
- FIG. 1 is a side sectional view showing a configuration of a fuel injection pump to which the present invention is applied.
- FIG. 2 is a sectional view showing the configuration of the CSD.
- FIG. 3 is a perspective view showing the upper part of the plunger when the plunger is raised.
- FIG. 4 is a partial cross-sectional side view showing the upper part of the plunger when the plunger is raised when the CSD is not operated. .
- FIG. 5 is a graph showing the fuel injection timing with respect to the pump speed.
- FIG. 6 is a graph showing a fuel injection amount with respect to a pump rotation speed.
- the fuel injection pump 1 according to the present invention is mounted on a diesel engine.
- One embodiment of the configuration of the fuel injection pump 1 will be described below.
- the left side of FIG. 1 is the front side.
- the fuel injection pump 1 is configured by vertically joining a pump housing 45 and a hydraulic head 46.
- a casing 8 of an electronic control governor device 7 is attached to the front side surface of the pump housing 45, and a rack case 40 is fixedly fitted from the front side of the casing 8.
- the electronic control governor device 7 is not limited to the electronic control type as in this embodiment, but may be a mechanical governor device.
- the rack actuator 40 moves the sliding shaft 3 back and forth in the front-rear direction.
- the tip of the sliding shaft 3 is pivotally connected to a middle part of the governor lever 23.
- the governor lever 23 is disposed rotatably around a governor lever shaft 24 at a lower portion thereof.
- a link 6 is pivotally connected to the upper end of the governor lever 23.
- a plunger barrel 33 is fitted into the hide lick head 46, and a plunger 32 is vertically slid in the plunger barrel 33. It is movably decorated.
- the plunger 32 rotates the cam 11 formed on the pump cam shaft 2 to rotate the tut 11 and the lower spring receiver 12. It is configured to move up and down through.
- the upper part of the plunger 32 is a fuel pressure chamber 17, and the fuel compressed in the fuel pressure chamber 1 ⁇ ⁇ ⁇ is supplied to the distribution shaft 9.
- a rotation sensor 122 for detecting the number of rotations of the pump camshaft 2 is attached to a lower portion of the casing 8.
- a cold start advancing mechanism (hereinafter referred to as “CSD 30”) is provided behind the plunger barrel 33 in the hydraulic head 4 6. 6, the piston barrel 34 of the CSD 30 is fitted. In a piston sliding portion of the piston barrel 34, a piston for a CSD timer (hereinafter, referred to as a "piston 35") is provided so as to be vertically slidable. Then, the piston 35 is vertically slid by the advance actuator 38.
- the lead angle actuators 38 are electromagnetic actuators whose operation is electronically controlled according to the water temperature by a controller connected to a water temperature sensor or the like, or a thermos that expands and contracts by sensing temperature changes. A warm sensation member such as a tut.
- the overflow subport (hereinafter, referred to as “subport 36 a”) formed in the plunger barrel 33 is connected to the inside of the piston barrel 34 via a drain oil passage 37. I understand.
- the CSD 30 At normal temperature (at the time of operation), the CSD 30 is in a non-operating state. In this state, the piston 35 is located at the lowest position, and the sub port 36 a is connected to the low pressure via the drain oil passage 37. Rooms 47 are communicated. As a result, a part of the fuel compressed by the plunger 32 overflows into the low-pressure chamber 47 formed in the hydraulic head 46, so that the normal fuel injection timing is set.
- the CSD 30 is operated, and the advance angle actuator 38 is operated, whereby the piston 35 is moved upward, and the drain oil passage is moved.
- the communication between the sub-port 36a and the low-pressure chamber 47 via 37 is disconnected, and the advance control of the fuel injection timing is performed.
- the advance control is performed by operating the advance function 38 of the CSD 30.
- the details of the fuel injection structure of the fuel injection pump 1 having such a configuration and the structure of the CSD 30 will be described below with reference to FIGS. 1 and 2.
- a main port 39 provided in the plunger barrel 33 is configured such that fuel pumped from a fuel supply unit (not shown) is constantly supplied, and the plunger 32 has a vertical movement range.
- the fuel pressure chamber 17 formed above the plunger 32 in the plunger barrel 33 communicates with the main port 39 to form the fuel pressure chamber 17
- Fuel is introduced into When the plunger 32 is pushed up by the cam 4 and rises, the outer wall of the plunger 32 closes the communication port of the main port 39 to the fuel pressure chamber 17.
- the fuel in the fuel pressure chamber 17 is pressure-fed to the delivery pulp 18 via the distribution shaft 9 from the distribution port 49 passing through the plunger barrel 33 as the plunger 32 rises.
- the fuel is injected into the cylinder of the engine from the delivery valve 18 via a fuel injection valve or the like provided in the cylinder head of the engine.
- the plunger lead 32 a formed on the plunger 32 communicates with the main port 39 and the fuel pressure chamber 17 communicates with the main port 39.
- the fuel in the fuel pressure chamber 17 flows backward to the fuel supply section side of the main port 39.
- the plunger 32 is rotated around the axis by the electronic control governor device 7 to change the vertical position of the plunger 32 when the plunger lead 3 2a and the main port 39 communicate with each other.
- the fuel injection amount from the fuel injection valve can be adjusted.
- a sub port 36a which can be opened and closed by sliding the piston 35 of the CSD 30 is provided at a position facing the main port 39, as described above. Has a smaller diameter than the main port 39.
- the CSD 30 is operated to control the advance of the injection timing.
- the piston 35 operated by the advancing actuator 38 connects the piston port 34 with the piston port 34 via the drain oil passage 37 of the sub port 36a, which is in communication at normal temperature. Cut off by closing. As a result, the plunger 32 is moved to the fuel pressure chamber. At the same time as closing the main port 39 with respect to 17, the fuel pressure supply from the fuel pressure chamber 17 to the distribution shaft 9 is started.
- the CSD 30 is in a non-operating state, and the subport 36 a and the inside of the piston barrel 34 are in communication with each other via a drain oil passage 37.
- the sub-port 36a and the low-pressure chamber 47 are in communication with each other, and the fuel is discharged from the sub-port 36a to delay the start of the fuel pressure supply from the fuel pressure chamber 17. To control the retard.
- an overflow-specific subport 36b is provided.
- the overflow-dedicated subport 36b is formed in the plunger barrel 33, and its height is higher than the main port 39 and lower than the subport 36a. That is, the overflow exclusive sub-port 36b is provided between the main port 39 and the sub-port 36a in the sliding direction of the plunger 132.
- the provision of the overflow-dedicated subport 36b optimizes the advance amount (change in injection timing) and the fuel injection amount when the CSD 30 is activated compared to when the CSD 30 is not activated. .
- the sub port 36a When the CSD 30 shown on the left side of Fig. 4 is not operating, that is, at room temperature, the sub port 36a is not closed by the piston 35, so that the sub port 36a communicates with the low-pressure chamber 47.
- the fuel is overflowing from the subport 36a and the overflow-dedicated subport 36b. Therefore, when the plunger 32 rises, the communication between the main port 39 and the fuel pressure chamber 17 is cut off by the outer wall of the plunger 32, and then the sub-port 36a by the outer wall of the plunger 32. Is closed, and the fuel in the fuel pressure chamber 17 is pumped to the distribution shaft 9.
- the amount of fuel injection and the amount of change in the injection timing when the CSD 30 is not operating are determined by the position of the subport 36a, and the fuel due to the provision of the overflow exclusive subport 36b There is no change in the injection amount and the injection timing.
- the overflow-dedicated subport 3613 plays the role of the subport 36a when it is not operating, and the overflow-dedicated subport 36b rises and the plunger 3
- the fuel injection timing is determined by the position closed by step 2. That is, advance control of the fuel injection timing is performed by the overflow exclusive subport 36b. Therefore, the position (height) of the overflow exclusive subport 36b and the fuel injection timing and The injection amount is determined.
- the distance from when plunger 3 2 closes main port 39 to when sub port 36 a is closed is determined by plunger step ⁇ A, after closing main port 39 as well.
- the plunger step ⁇ ⁇ Assuming that the distance until the overflow exclusive subport 36b is closed is the plunger step ⁇ ⁇ , the plunger step ⁇ ⁇ ⁇ when the CSD 30 is not operating, and the plunger step B when the CSD 30 is operating.
- the fuel injection timing and injection amount at each time are determined. That is, the difference ( ⁇ —SB) between the plunger step ⁇ A when CS 30 is not operated and the plunger step ⁇ C when CS 30 is operated is the advance amount of the fuel injection timing.
- the plunger step is ⁇ A regardless of the presence or absence of the overflow-dedicated subport 36b.
- the plunger step B occurs. In other words, by providing the sub port 36 b dedicated to overflow, the position of the plunger 32 that starts pumping the fuel from the fuel pressure chamber 17 when the CSD 30 is activated changes from the position where the plunger level difference becomes ⁇ .
- the advance amount of the fuel injection timing generated by operating the CSD 30 is conventionally uniquely determined to be ⁇ A depending on the position of the subport 36a.
- the plunger step ⁇ B can be changed by arbitrarily setting the position where the overflow-dedicated subport 36b is provided. Can be set arbitrarily. That is, in this case, the amount of advance angle at the time of operation of the CSD 30 can be set arbitrarily within a range where the plunger step difference ⁇ ⁇ 0 is 0 and ⁇ ⁇ ⁇ .
- FIG. 5 is a graph showing the relationship between the fuel injection timing T and the pump rotation speed N of the fuel injection pump 1 in the case where the overflow-specific subport 36b is provided, as shown in FIG.
- FIG. 6 is a graph showing the relationship between the pump speed and the pump rotational speed N.
- the timing characteristic 50 representing the injection timing T with respect to the pump rotation speed N when the CSD 30 is not operating shows a substantially constant value.
- the injection timing T is advanced. That is, it is advanced.
- the timing characteristic 51b when the CSD 30 is activated according to the present invention is substantially the same as the conventional timing characteristic 51a with respect to the slope, but the timing characteristic 50b when the CSD 30 is not activated is shown. It can be seen that the change amount (advance angle amount) of the injection timing T with respect to the pressure is reduced. That is, the amount of advance when the CSD 30 is operated is smaller than in the conventional case.
- the characteristic curve 6 lb showing the injection amount Q with respect to the pump rotation speed N when the overflow-specific subport 36b of the present invention is provided is the characteristic curve of the shape when the CSD30 is not operated. 60 and the characteristic curve 61a when the conventional CSD30 is activated, but the change in the injection amount Q from when the CSD30 is not activated to when it is activated is smaller than in the conventional case. You can see that
- the advance amount and the injection amount of the fuel injection timing with respect to the pump rotation speed N which were uniquely determined by the position where the subport 36a is provided in the past, are provided by the overflow exclusive subport 36b. It can be set arbitrarily depending on the position where the subport 36b is provided. In this embodiment, one overflow-dedicated subport 36b is provided at one place, but a plurality of overflow-dedicated subports 36b may be provided. That is, the present invention provides a sub port 3 dedicated to overflow within a range of the advance amount and the fuel injection amount when the CSD 30 is activated with respect to the non-operated CSD 30 secured by the position where the sub port 36 a is provided. Adjust the fuel injection timing and the amount of fuel that overflows from the overflow sub port 36b by adjusting the position of the hole 6b and the hole diameter, etc., and adjust the appropriate fuel injection timing when the CSD 30 operates. And the injection amount can be set.
- the fuel injection timing and injection amount can be set arbitrarily by setting the position of the overflow exclusive subport 36b provided in the plunger barrel 33, so that the CSD 30 in the fuel injection pump 1 can be set. Even when the sub port 36a is manufactured with the same standard, it is possible to set an appropriate fuel injection timing and injection amount depending on the applied engine. In other words, while the fuel injection pump 1 maintains the characteristics when the CSD 30 is not operating (at normal temperature (when warm)), the fuel injection when the CSD 30 is operating (when the cold start (cold)) is performed.
- the amount of change in the timing and the injection amount with respect to the non-operation of the CSD 30 can be reduced as compared with the conventional case, so that the performance at the time of the warm state can be secured and the start at the low temperature can be optimized. As a result, emission of NOx and black smoke during low-temperature start-up and noise can be reduced, the start-up time can be shortened, and overall engine performance can be improved.
- the present invention is widely applicable to a diesel engine having a fuel injection pump provided with a low temperature start advance mechanism.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- High-Pressure Fuel Injection Pump Control (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE602004018644T DE602004018644D1 (de) | 2003-06-12 | 2004-04-28 | Kraftstoffeinspritzpumpe mit kaltstartversteller |
EP04730097A EP1645750B1 (en) | 2003-06-12 | 2004-04-28 | Fuel injection pump with cold start advancer mechanism |
US11/295,443 US7152585B2 (en) | 2003-06-12 | 2005-12-07 | Fuel injection pump with cold start device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003167945A JP3993841B2 (ja) | 2003-06-12 | 2003-06-12 | 低温始動進角機構を備える燃料噴射ポンプ |
JP2003-167945 | 2003-06-12 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/295,443 Continuation US7152585B2 (en) | 2003-06-12 | 2005-12-07 | Fuel injection pump with cold start device |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004111436A1 true WO2004111436A1 (ja) | 2004-12-23 |
Family
ID=33549320
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/006221 WO2004111436A1 (ja) | 2003-06-12 | 2004-04-28 | 低温始動進角機構を備える燃料噴射ポンプ |
Country Status (7)
Country | Link |
---|---|
US (1) | US7152585B2 (ja) |
EP (1) | EP1645750B1 (ja) |
JP (1) | JP3993841B2 (ja) |
KR (1) | KR101031395B1 (ja) |
CN (1) | CN100393998C (ja) |
DE (1) | DE602004018644D1 (ja) |
WO (1) | WO2004111436A1 (ja) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3814245B2 (ja) * | 2002-11-21 | 2006-08-23 | ヤンマー株式会社 | 燃料噴射ポンプ |
JP4427523B2 (ja) * | 2006-05-09 | 2010-03-10 | ヤンマー株式会社 | 燃料噴射ポンプ |
DE102008020221B4 (de) * | 2008-04-22 | 2018-10-25 | Thomas Koch | Verfahren zum Starten einer selbstzündenden Brennkraftmaschine bei niedrigen Temperaturen |
DE102010020578A1 (de) * | 2010-05-14 | 2011-11-17 | Bayerische Motoren Werke Aktiengesellschaft | Vorrichtung zum Antrieb eines Nebenaggregates |
DE102011079673A1 (de) * | 2011-07-22 | 2013-01-24 | Robert Bosch Gmbh | Hochdruckeinspritzsystem |
US9551631B2 (en) | 2013-02-08 | 2017-01-24 | Cummins Inc. | System and method for adapting to a variable fuel delivery cutout delay in a fuel system of an internal combustion engine |
US9903306B2 (en) | 2013-02-08 | 2018-02-27 | Cummins Inc. | System and method for acquiring pressure data from a fuel accumulator of an internal combustion engine |
JP6411313B2 (ja) * | 2015-11-26 | 2018-10-24 | ヤンマー株式会社 | 燃料噴射ポンプ |
CN113482821B (zh) * | 2021-07-30 | 2022-08-26 | 中船动力研究院有限公司 | 一种超高压燃油喷射系统 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000234576A (ja) * | 1999-02-15 | 2000-08-29 | Yanmar Diesel Engine Co Ltd | 燃料噴射ポンプの噴射時期制御構造 |
JP2003090275A (ja) * | 2001-09-18 | 2003-03-28 | Ishikawajima Harima Heavy Ind Co Ltd | ディーゼルエンジン用燃料噴射装置 |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3004460A1 (de) * | 1980-02-07 | 1981-09-10 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
US4754737A (en) * | 1984-05-08 | 1988-07-05 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Fuel injection pump device and method for settling the same |
JPS6114743U (ja) * | 1984-06-29 | 1986-01-28 | 株式会社ボッシュオートモーティブ システム | 燃料噴射装置 |
CH671073A5 (ja) * | 1986-09-09 | 1989-07-31 | Nova Werke Ag | |
US5219280A (en) * | 1990-02-09 | 1993-06-15 | Zexel Corporation | Fuel injection pump plunger |
JPH0893595A (ja) | 1994-09-21 | 1996-04-09 | Zexel Corp | 燃料噴射ポンプ |
DE4443860B4 (de) * | 1994-12-09 | 2004-05-13 | Robert Bosch Gmbh | Kraftstoffeinspritzpumpe für Brennkraftmaschinen |
DE19630337C2 (de) * | 1996-07-26 | 1999-02-18 | Hatz Motoren | Kraftstoffeinspritzpumpe zur Einspritzung bei Brennkraftmaschinen, insbesondere Einzylinder-Dieselmotoren |
JPH10231763A (ja) * | 1997-02-18 | 1998-09-02 | Zexel Corp | 燃料噴射ポンプ |
JP3999855B2 (ja) * | 1997-09-25 | 2007-10-31 | 三菱電機株式会社 | 燃料供給装置 |
JP3762838B2 (ja) * | 1998-05-22 | 2006-04-05 | 株式会社クボタ | ディーゼルエンジンの燃料噴射装置 |
US6866025B1 (en) * | 1999-11-18 | 2005-03-15 | Siemens Vdo Automotive Corp. | High pressure fuel pump delivery control by piston deactivation |
JP2001349262A (ja) | 2000-06-08 | 2001-12-21 | Yanmar Diesel Engine Co Ltd | 燃料噴射ポンプの噴射時期制御機構 |
WO2003029631A1 (fr) * | 2001-09-28 | 2003-04-10 | Yanmar Co., Ltd. | Dispositif d'aide au demarrage d'une pompe d'injection de combustible |
-
2003
- 2003-06-12 JP JP2003167945A patent/JP3993841B2/ja not_active Expired - Fee Related
-
2004
- 2004-04-28 DE DE602004018644T patent/DE602004018644D1/de not_active Expired - Lifetime
- 2004-04-28 CN CNB2004800164345A patent/CN100393998C/zh not_active Expired - Fee Related
- 2004-04-28 KR KR1020057023499A patent/KR101031395B1/ko active IP Right Grant
- 2004-04-28 EP EP04730097A patent/EP1645750B1/en not_active Expired - Fee Related
- 2004-04-28 WO PCT/JP2004/006221 patent/WO2004111436A1/ja active Application Filing
-
2005
- 2005-12-07 US US11/295,443 patent/US7152585B2/en not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000234576A (ja) * | 1999-02-15 | 2000-08-29 | Yanmar Diesel Engine Co Ltd | 燃料噴射ポンプの噴射時期制御構造 |
JP2003090275A (ja) * | 2001-09-18 | 2003-03-28 | Ishikawajima Harima Heavy Ind Co Ltd | ディーゼルエンジン用燃料噴射装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP1645750A4 * |
Also Published As
Publication number | Publication date |
---|---|
CN1806118A (zh) | 2006-07-19 |
KR101031395B1 (ko) | 2011-04-25 |
JP3993841B2 (ja) | 2007-10-17 |
CN100393998C (zh) | 2008-06-11 |
JP2005002913A (ja) | 2005-01-06 |
US7152585B2 (en) | 2006-12-26 |
DE602004018644D1 (de) | 2009-02-05 |
EP1645750B1 (en) | 2008-12-24 |
EP1645750A1 (en) | 2006-04-12 |
US20060107929A1 (en) | 2006-05-25 |
KR20060061296A (ko) | 2006-06-07 |
EP1645750A4 (en) | 2007-09-12 |
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