WO2012147173A1 - 高圧ポンプの調量装置 - Google Patents
高圧ポンプの調量装置 Download PDFInfo
- Publication number
- WO2012147173A1 WO2012147173A1 PCT/JP2011/060224 JP2011060224W WO2012147173A1 WO 2012147173 A1 WO2012147173 A1 WO 2012147173A1 JP 2011060224 W JP2011060224 W JP 2011060224W WO 2012147173 A1 WO2012147173 A1 WO 2012147173A1
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- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- feed
- pump
- metering device
- spring member
- Prior art date
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Classifications
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- 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
- F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
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- 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
- F02M59/368—Pump inlet valves being closed when actuated
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/22—Safety or indicating devices for abnormal conditions
- F02D41/221—Safety or indicating devices for abnormal conditions relating to the failure of actuators or electrically driven elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/3809—Common rail control systems
- F02D41/3836—Controlling the fuel pressure
- F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/22—Safety or indicating devices for abnormal conditions
- F02D2041/224—Diagnosis of the fuel system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0602—Fuel pressure
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- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/18—Fuel-injection apparatus having means for maintaining safety not otherwise provided for
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
Definitions
- the present invention relates to a metering device for a high-pressure pump.
- FIG. 1 According to the fuel injection device disclosed in Patent Document 1, it is possible to maintain high controllability of the fuel pressure even when abnormality occurs in some of the pumping systems. Specifically, if it is determined that there is an abnormality in one of the fuel pumping systems of each of the two plungers, the pumping start angle of the fuel pump is forced so that the pumping amount of the pumping system that does not correspond to the abnormality increases. Has been changed.
- the metering device of the high-pressure pump disclosed in this specification has an object to maintain and continue fuel discharge when a malfunction occurs in the metering valve.
- a metering device for a high-pressure pump disclosed in the present specification is a metering device for a high-pressure pump that pressurizes and feeds fuel supplied from a feed pump, the cylinder included in the high-pressure pump, A suction valve that adjusts the communication state with the feed pump communication path through which the fuel supplied by the feed pump flows, adjusts the discharge amount of the high-pressure pump, and a spring member that biases the suction valve toward the valve closing side, A valve closing means for allowing the spring member to move in the valve closing direction by energization, and a compression amount adjusting member for changing a compression amount of the spring member in accordance with a feed pressure of the feed pump.
- a suction valve that adjusts the communication state with the feed pump communication path through which the fuel supplied by the feed pump flows, adjusts the discharge amount of the high-pressure pump
- a spring member that biases the suction valve toward the valve closing side
- a valve closing means for allowing the spring member to move in the valve closing direction by ener
- the valve closing means When the valve closing means is activated and the suction valve is closed by the biasing force of the spring member, the high pressure pump is in a state where the fuel in the cylinder can be pumped. Therefore, if an abnormality occurs in the valve closing means and the intake valve cannot be closed, there is a possibility that the fuel pressure cannot be continued.
- the suction valve is urged by a spring member mounted in a compressed state and moves in the valve closing direction. For this reason, if the compression amount of the spring member is increased, the intake valve can be easily closed.
- the compression amount adjusting member adjusts the ease of opening and closing the intake valve by changing the compression amount of the spring member according to the feed pressure.
- Such a compression amount adjusting member can be a plate member having a first surface and a second surface which is the back surface of the first surface.
- the plate member holds the spring member between a first surface and a hooking flange provided on the suction valve, and the pressure receiving area of the feed pressure on the first surface is the second surface.
- the structure is larger than the pressure receiving area of the feed pressure.
- the compression amount of the spring member can be changed according to the feed pressure. Specifically, when the feed pressure is reduced, the amount of decrease in the force acting on the first surface having a large pressure receiving area is larger than the amount of decrease in the force acting on the second surface having a small pressure receiving area. As a result, the force pushed from the second surface side increases, and the plate member moves to the first surface side. Then, the compression amount of the spring member supported on the first surface side increases. As a result, the preload of the spring member is increased, and the intake valve is easily moved in the valve closing direction.
- the metering device of the high-pressure fuel pump includes a failure determining means for the valve closing means when the feed pump is electrically operated, and when the failure determining means determines that the valve closing means has failed.
- the control part which reduces the feed pressure of the feed pump can be provided.
- the compression amount adjusting member changes the compression amount of the spring member according to the feed pressure. Specifically, when the feed pressure decreases, the compression amount of the spring member is increased. For this reason, when a failure of the valve closing means is detected, the feed pressure is forcibly reduced. Thereby, the compression amount of the spring member is increased, the self-closing phenomenon of the intake valve is promoted, and the fuel discharge is maintained and continued.
- the failure determination means can determine the failure of the valve closing means according to the rail pressure of the common rail to which high pressure fuel is supplied from the high pressure pump.
- a conventional rail pressure sensor can be used without additional equipment.
- FIG. 1 is an explanatory diagram showing a schematic configuration of a metering device incorporated in the high-pressure pump of the embodiment.
- 2A is a plan view of a plate member incorporated in the metering device
- FIG. 2B is a bottom view
- FIG. 2C is a cross-sectional view taken along line AA.
- FIG. 3A is an explanatory diagram showing a state in which the intake valve is opened in the metering device in the normal state
- FIG. 3B is an explanatory diagram showing a state in which the suction valve is closed in the metering device in the normal state.
- FIGS. 4A to 4D are explanatory views showing the state of fuel discharge by the high-pressure pump in the normal state.
- FIG. 5A is an explanatory view showing a state in which the intake valve is opened in the metering device in the solenoid failure state
- FIG. 5B is a state in which the suction valve is closed in the metering device in the solenoid failure state. It is explanatory drawing shown.
- FIGS. 6A to 6D are explanatory views showing the state of fuel discharge by the high-pressure pump in a solenoid failure state.
- FIG. 7 is a graph showing the relationship between the feed pressure of the feed pump and the engine speed.
- the metering device (hereinafter simply referred to as “metering device”) 20 of the high-pressure pump of the embodiment is assembled to the high-pressure pump 100.
- the metering device 20 has a discharge amount adjustment valve (PCV: Control Valve).
- the high-pressure pump 100 pressurizes and feeds the fuel supplied from the electric feed pump 1.
- the high-pressure pump 100 includes a plunger 102 that is slidably disposed in the cylinder 101.
- the high-pressure pump 100 is a single cylinder pump including one cylinder 101 and one plunger 102.
- the metering device 20 is provided between the feed pump 1 and the high-pressure pump 100.
- the metering device 20 changes the communication state between the cylinder 101 provided in the high-pressure pump 100 and the feed pump communication passage 2 through which the fuel supplied by the feed pump 1 flows, and adjusts the discharge amount of the high-pressure pump 100. It has.
- the suction valve 3 is arranged so that the tip side provided with a tapered seat surface 3 a is located in the cylinder 101. That is, it is arranged in a state of penetrating a fuel introduction hole 101 a formed in the upper part of the cylinder 101. When the seat surface 3a of the suction valve 3 is seated on the tapered seat portion 101a1 formed in the introduction hole 101a, the cylinder 101 is closed.
- the high-pressure pump 100 pumps fuel to the common rail 14 when the plunger 102 driven by the cam 103 moves up and down.
- the suction valve 3 is opened when the fuel supplied from the feed pump 1 is sucked into the cylinder 101. Further, when the fuel is discharged by the plunger 102, the discharge amount is controlled by adjusting the closing / adjustment.
- a one-way valve 15 is provided between the high-pressure pump 100 and the common rail 14.
- the suction valve 3 is slidably supported by the main body 4.
- the main body 4 includes an air release passage 4a.
- the main body portion 4 is provided with a cylindrical portion 5.
- a gasket 6 is mounted between the main body portion 4 and the tubular portion 5, and the inside of the tubular portion 5 and the atmosphere opening passage 4 a are partitioned.
- the inside of the cylindrical portion 5 communicates with the feed pump communication path 2 so that feed pressure is applied to the inside.
- the metering device 20 includes a spring member 12 that biases the suction valve 3 on the valve closing side, that is, in this embodiment, upward in FIG.
- the metering device 20 includes valve closing means that allows the spring member 12 to move the suction valve 3 in the valve closing direction when energized.
- the valve closing means includes a solenoid 9 and an armature 10.
- the solenoid 9 and the armature 10 are disposed inside the cylindrical portion 5.
- the solenoid 9 When the solenoid 9 is not energized, the armature 10 contacts the suction valve 3 and opens the suction valve 3 by a spring member 11 that biases the suction valve 3 to the valve opening side.
- the armature 10 is pulled toward the solenoid 9 while compressing the spring member 11 by energizing the solenoid 9. Thereby, the suction valve 3 urged toward the valve closing side by the spring member 12 moves.
- a hooking hook portion 3b is provided on the proximal end side of the intake valve 3, that is, the side on which the armature 10 abuts.
- the spring member 12 is held between the hooking flange portion 3 b and the first surface 7 a of the plate member 7.
- the plate member 7 is an example of a compression amount adjusting member that changes the compression amount of the spring member 12 according to the feed pressure of the feed pump.
- the plate member 7 is a ring-shaped member having a first surface 7a and a second surface which is the back surface of the first surface 7a. It is a member. As shown in FIG. 1, the plate member 7 is arranged so that the first surface 7 a is located in the cylindrical portion 5. Since the inside of the cylindrical portion 5 receives the feed pressure as described above, the entire surface of the first surface 7a becomes a pressure receiving surface for the feed pressure. On the other hand, a wall is provided at the edge on the second surface 7b side, and the second surface 7b is divided into a feed pressure receiving surface 7b1 and an atmospheric pressure receiving surface 7b2.
- the plate member 7 is attached to the main body 4 so that the atmospheric pressure receiving surface 7b2 is exposed to the atmosphere opening passage 4a.
- a disc spring 8 is interposed between the atmospheric pressure receiving surface 7 b 2 and the atmosphere opening passage 4 a, and the plate member 7 is supported by the main body 4 via the disc spring 8.
- the pressure receiving area of the feed pressure on the first surface 7a that is, the area of the first surface 7a is larger than the pressure receiving area of the feed pressure on the second surface 7b, that is, the area of the feed pressure receiving surface 7b1.
- the position of the plate member can be changed with the change of the feed pressure. Specifically, when the feed pressure is increased, the plate member 7 is lowered in the cylindrical portion 5, and when the feed pressure is reduced, the plate member 7 is raised in the cylindrical portion 5.
- the plate member 7 holds the spring member 12 between the first surface 7a and the hooking flange portion 3b. For this reason, when the plate member 7 rises, the spring member 12 is compressed.
- the compression amount of the spring member 12 can be changed according to the feed pressure. Specifically, when the feed pressure is reduced and the plate member 7 is raised, the spring member 12 is compressed, the preload is increased, and the intake valve 3 is easily closed.
- the metering device 20 includes an ECU (Electronic control unit) 13 as a control unit.
- the ECU 13 is electrically connected to the rail pressure sensor 14 a mounted on the common rail 14, the solenoid 9, and the feed pump 1.
- FIG. 3A is an explanatory diagram showing a state in which the suction valve 3 is opened in the metering device 20 in the normal state
- FIG. 3B is a diagram in which the suction valve 3 is closed in the metering device 20 in the normal state. It is explanatory drawing which shows a state.
- 4A to 4D are explanatory views showing the state of fuel discharge by the high-pressure pump 100 in a normal state.
- FIG. 5A is an explanatory diagram showing a state in which the intake valve 3 is opened in the metering device 20 in a solenoid failure state
- FIG. 5B is a diagram in which the intake valve 3 is closed in the metering device 20 in a solenoid failure state. It is explanatory drawing which shows the state turned off.
- FIGS. 6A to 6D are explanatory views showing the state of fuel discharge by the high-pressure pump 100 in a solenoid failure state.
- FIG. 3 (A) and FIG. 3 (B) a high feed pressure is applied to the first surface 7a of the plate member 7 at normal times. For this reason, the plate member 7 pushes down the disc spring 8 and is positioned at the lowermost portion of the cylindrical portion 5.
- FIG. 3A when the solenoid 9 is normal and the solenoid 9 is not energized, the intake valve 3 is urged by the spring member 11 via the armature 10 and is opened. .
- FIG. 3B when the solenoid 9 is energized, the armature 10 is attracted to the solenoid 9. Then, the suction valve 3 biased by the spring member 12 can be closed.
- the opening degree of the suction valve 3 is adjusted, and consequently, the discharge amount of the high-pressure pump 100 is adjusted.
- the state of fuel discharge will be described in more detail.
- the intake valve 3 is opened as shown in FIG. 4A, the cam 103 starts rotating, and when the plunger 102 starts to descend as shown in FIG. 4B, the feed pump 1 enters the cylinder 101. The supplied fuel flows in. Then, as shown in FIG. 4C, the plunger 102 starts to rise and starts to compress the fuel.
- the state in which the intake valve 3 is opened is continued, the fuel in the cylinder 101 is discharged again through the introduction hole 101a.
- the discharge amount is adjusted.
- the solenoid 9 is energized as shown in FIG. 4D, and the intake valve 3 is closed.
- the intake valve 3 By closing the intake valve 3, the fuel in the cylinder 101 compressed by the plunger 102 is sent to the common rail 14 side.
- a lower feed pressure is applied to the first surface 7a of the plate member 7 than in the normal state. That is, the feed pump 1 is controlled based on a command from the ECU 13, and a suppressed feed pressure is applied.
- the ECU 13 that functions as the failure determination means detects a decrease in the value of the rail pressure sensor 14a, the ECU 13 determines that this is due to the failure of the solenoid 9. Then, the feed pump 1 is controlled to lower the feed pressure. For this reason, the force which the 1st surface 7a of the plate member 7 receives becomes relatively small.
- the plate member 7 is raised in the cylindrical portion 5 due to the balance between the repulsive force of the disc spring 8 and the force received by the first surface 7a and the second surface 7b.
- the plate member 7 is raised, the amount of compression of the spring member 12 increases.
- the suction valve 3 is easily moved in the valve closing direction.
- the solenoid 9 is out of order, the intake valve 3 is urged by the spring member 11 via the armature 10 and is opened as shown in FIG.
- the solenoid 9 is out of order, as shown in FIG. 5B, when the plunger 102 rises, the intake valve 3 is pushed up by the fuel compressed in the cylinder 101, and the intake valve 3 Can be closed.
- a so-called autistic phenomenon occurs.
- fuel can be pumped to the common rail 14.
- the state of fuel discharge will be described in more detail.
- FIG. 6 (A) when the intake valve 3 is opened, the cam 103 starts to rotate, and as shown in FIG. 6 (B), when the plunger 102 starts to descend, the feed pump 1 enters the cylinder 101. The supplied fuel flows in. Then, as shown in FIG. 6C, the plunger 102 starts to rise and starts to compress the fuel. Then, the suction valve 3 is pushed by the flow of fuel discharged from the introduction hole 101a and moves in the valve closing direction.
- the spring member 12 that urges the suction valve 3 in the valve closing direction increases its preload due to the movement of the plate member 7.
- the urging force exerted by the spring member 12 can be combined with the force of the fuel flow compressed by the plunger 102 to overcome the urging force of the spring member 12, and the intake valve 3 is pushed up to be closed. be able to.
- the intake valve 3 can maintain the valve closed state. Therefore, the fuel in the cylinder 101 compressed by the plunger 102 is It is sent to the common rail 14 side.
- fuel discharge can be continued when a failure occurs in the solenoid 9 that drives the intake valve that is a metering valve. Since the fuel discharge can be continued, the retreat traveling for moving the vehicle to a safe place becomes possible.
- the ECU 13 that has detected a decrease in rail pressure by the rail pressure sensor 14a controls the feed pump 1 to decrease the feed pressure. That is, it is an example assuming that the feed pump 1 is an electric type. However, even when a so-called mechanical feed pump is used, the metering device 20 similar to that of the present embodiment can be applied. For example, if the solenoid 9 fails as in the above example, a problem occurs in the pressure-feeding of the fuel 14 to the common rail, and the engine output decreases.
- FIG. 7 is a graph showing the relationship between the engine speed and the feed pressure. If the engine output (engine speed) decreases, the output of the feed pump using the rotation of the crankshaft or camshaft as the drive source. Also decreases.
- the feed pressure decreases, so that the plate member 7 can be moved as in the above example. Then, a self-closing phenomenon can be caused and the fuel pumping can be maintained.
- a mechanical feed pump it is also possible to actively induce a self-closing phenomenon by controlling the fuel pressure using the pressure reducing valve mounted on the common rail 14 and reducing the engine output. is there.
Abstract
Description
Control Valve)である。高圧ポンプ100は、電動式のフィードポンプ1から供給された燃料を昇圧して圧送する。高圧ポンプ100は、シリンダ101内に摺動自在に配置されたプランジャ102を備えている。高圧ポンプ100は、一のシリンダ101と一のプランジャ102を備えた単筒ポンプである。調量装置20は、フィードポンプ1と高圧ポンプ100との間に設けられている。調量装置20は、高圧ポンプ100が備えるシリンダ101とフィードポンプ1によって供給される燃料が流通するフィードポンプ連通路2との連通状態を変化させ、高圧ポンプ100の吐出量を調節する吸入弁3を備えている。吸入弁3は、テーパ状のシート面3aを備えた先端側がシリンダ101内に位置するように配置されている。すなわち、シリンダ101の上部に形成された燃料の導入孔101aを貫通した状態で配置されている。導入孔101aに形成されたテーパ状のシート部101a1に吸入弁3のシート面3aが着座することにより、シリンダ101は閉じた状態となる。高圧ポンプ100は、カム103によって駆動されるプランジャ102が上下動することにより燃料をコモンレール14へ圧送する。吸入弁3は、シリンダ101内にフィードポンプ1から供給された燃料を吸い込むときに開弁状態となる。また、プランジャ102によって燃料が吐出されるときに、その閉じ加減を調節することにより、吐出量を制御する。なお、高圧ポンプ100とコモンレール14との間には、一方弁15が設けられている。
2 フィードポンプ連通路
3 吸入弁
3b 掛合鍔部
4 本体部
4a 大気開放通路
5 筒状部
7 プレート部材(圧縮量調整部材)
7a 第1の面(フィード圧受圧面)
7b 第2の面
7b1 フィード圧受圧面
7b2 大気圧受圧面
9 ソレノイド
10 アーマチャ
11 バネ部材(吸入弁を開弁側に付勢)
12 バネ部材(吸入弁を閉弁側に付勢)
13 ECU(Electronic control unit;制御部)
14 コモンレール
14a レール圧センサ
20 調量装置
100 高圧ポンプ
101 シリンダ
101a 導入孔
102 プランジャ
Claims (4)
- フィードポンプから供給された燃料を昇圧して圧送する高圧ポンプの調量装置であって、
高圧ポンプが備えるシリンダと前記フィードポンプによって供給される燃料が流通するフィードポンプ連通路との連通状態を変化させ、
前記高圧ポンプの吐出量を調節する吸入弁と、
前記吸入弁を閉弁側に付勢するバネ部材と、
通電により、前記バネ部材による前記吸入弁の閉弁方向への移動を許容する閉弁手段と、
前記フィードポンプのフィード圧に応じて前記バネ部材の圧縮量を変更する圧縮量調整部材と、
を、備えた高圧ポンプの調量装置。 - 前記圧縮量調整部材は第1の面と当該第1の面の裏面となる第2の面を備えたプレート部材であって、
前記第1の面と前記吸入弁に設けられた掛合鍔部との間に前記バネ部材を保持し、
前記第1の面における前記フィード圧の受圧面積が前記第2の面における前記フィード圧の受圧面積よりも大きい請求項1記載の高圧ポンプの調量装置。 - 前記フィードポンプが電動式であるときに、
前記閉弁手段の故障判定手段を備え、
前記故障判定手段によって前記閉弁手段が故障していると判断したときに、前記フィードポンプのフィード圧を低下させる制御部を備えた請求項1又は2記載の高圧ポンプの調量装置。 - 前記故障判定手段は、前記高圧ポンプから高圧の燃料が供給されるコモンレールのレール圧に応じて前記閉弁手段の故障を判断する請求項3記載の高圧ポンプの調量装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2011800045897A CN102859149A (zh) | 2011-04-27 | 2011-04-27 | 高压泵的调量装置 |
US13/511,756 US20140034017A1 (en) | 2011-04-27 | 2011-04-27 | Adjustment device of high-pressure pump |
JP2011553200A JP5218681B2 (ja) | 2011-04-27 | 2011-04-27 | 高圧ポンプの調量装置 |
EP11822816.2A EP2703625A1 (en) | 2011-04-27 | 2011-04-27 | Metering device for high-pressure pump |
PCT/JP2011/060224 WO2012147173A1 (ja) | 2011-04-27 | 2011-04-27 | 高圧ポンプの調量装置 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2011/060224 WO2012147173A1 (ja) | 2011-04-27 | 2011-04-27 | 高圧ポンプの調量装置 |
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WO2012147173A1 true WO2012147173A1 (ja) | 2012-11-01 |
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PCT/JP2011/060224 WO2012147173A1 (ja) | 2011-04-27 | 2011-04-27 | 高圧ポンプの調量装置 |
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US (1) | US20140034017A1 (ja) |
EP (1) | EP2703625A1 (ja) |
JP (1) | JP5218681B2 (ja) |
CN (1) | CN102859149A (ja) |
WO (1) | WO2012147173A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2015090446A1 (de) * | 2013-12-20 | 2015-06-25 | Robert Bosch Gmbh | Saugventil für eine hochdruckpumpe sowie hochdruckpumpe |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
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JP5630464B2 (ja) | 2012-06-26 | 2014-11-26 | 株式会社デンソー | 燃料噴射制御装置 |
DE102014214231A1 (de) * | 2014-07-22 | 2016-01-28 | Robert Bosch Gmbh | Elektromagnetische Stelleinheit für ein Saugventil sowie Saugventil |
DE102014220975A1 (de) * | 2014-10-16 | 2016-04-21 | Robert Bosch Gmbh | Elektromagnetisch betätigbares Einlassventil und Hochdruckpumpe mit Einlassventil |
DE102015212376A1 (de) * | 2015-07-02 | 2017-01-05 | Robert Bosch Gmbh | Elektromagnetisch betätigbares Saugventil für eine Hochdruckpumpe sowie Hochdruckpumpe |
IT201700073083A1 (it) * | 2017-06-29 | 2018-12-29 | Bosch Gmbh Robert | Gruppo pompa per alimentare carburante ad un motore a combustione interna |
JP6922713B2 (ja) * | 2017-12-13 | 2021-08-18 | トヨタ自動車株式会社 | 燃料ポンプの制御装置 |
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GB0812888D0 (en) * | 2008-07-15 | 2008-08-20 | Delphi Tech Inc | Improvements relating to fuel pumps |
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- 2011-04-27 WO PCT/JP2011/060224 patent/WO2012147173A1/ja active Application Filing
- 2011-04-27 US US13/511,756 patent/US20140034017A1/en not_active Abandoned
- 2011-04-27 CN CN2011800045897A patent/CN102859149A/zh active Pending
- 2011-04-27 JP JP2011553200A patent/JP5218681B2/ja not_active Expired - Fee Related
- 2011-04-27 EP EP11822816.2A patent/EP2703625A1/en not_active Withdrawn
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WO2004001220A1 (ja) * | 2002-06-20 | 2003-12-31 | Hitachi, Ltd. | 内燃機関の高圧燃料ポンプ制御装置 |
JP2007255400A (ja) | 2006-03-27 | 2007-10-04 | Denso Corp | 燃料噴射制御装置 |
JP2010196472A (ja) * | 2009-02-23 | 2010-09-09 | Denso Corp | 内燃機関の燃料供給制御装置 |
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WO2015090446A1 (de) * | 2013-12-20 | 2015-06-25 | Robert Bosch Gmbh | Saugventil für eine hochdruckpumpe sowie hochdruckpumpe |
Also Published As
Publication number | Publication date |
---|---|
CN102859149A (zh) | 2013-01-02 |
US20140034017A1 (en) | 2014-02-06 |
JPWO2012147173A1 (ja) | 2014-07-28 |
EP2703625A1 (en) | 2014-03-05 |
JP5218681B2 (ja) | 2013-06-26 |
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