WO2018003435A1 - Pompe d'alimentation en carburant haute pression - Google Patents

Pompe d'alimentation en carburant haute pression Download PDF

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Publication number
WO2018003435A1
WO2018003435A1 PCT/JP2017/021075 JP2017021075W WO2018003435A1 WO 2018003435 A1 WO2018003435 A1 WO 2018003435A1 JP 2017021075 W JP2017021075 W JP 2017021075W WO 2018003435 A1 WO2018003435 A1 WO 2018003435A1
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WO
WIPO (PCT)
Prior art keywords
relief valve
inner peripheral
supply pump
fuel supply
relief
Prior art date
Application number
PCT/JP2017/021075
Other languages
English (en)
Japanese (ja)
Inventor
雄太 笹生
徳尾　健一郎
悟史 臼井
菅波　正幸
淳 伯耆田
斉藤　淳治
稔 橋田
将通 谷貝
早谷　政彦
千彰 徳丸
Original Assignee
日立オートモティブシステムズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Priority to JP2018524998A priority Critical patent/JP6649483B2/ja
Publication of WO2018003435A1 publication Critical patent/WO2018003435A1/fr

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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
    • F02M59/44—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
    • F02M59/46—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded

Definitions

  • the present invention relates to a high-pressure fuel supply pump having a relief valve mechanism.
  • a high-pressure fuel supply pump for increasing the pressure of fuel is widely used in a direct injection type in which fuel is directly injected into a combustion chamber.
  • JP 2009-1114886 A As a background art of this high-pressure fuel pump, there is JP 2009-1114886 A.
  • the relief valve structure of the high-pressure fuel pump is configured to have a squeezing effect in the gap between the housing in the fuel passage and the valve body presser in the fuel passage through which fluid flows from the high-pressure side to the low-pressure side.
  • the stroke amount of the valve body presser is larger than that without the squeezing effect, and when the adjuster that regulates the stroke of the valve body presser is not provided, the valve body presser is set in the valve closing direction. It may cause the relief spring to sag. If an adjuster is provided, the relief valve may increase in size, increase in mass, increase in cost, and may impair product value.
  • An object of the present invention is to provide a high-pressure fuel supply pump that can regulate the stroke of the valve body and can greatly stroke the valve body without providing an adjuster that regulates the stroke of the valve body.
  • the present invention provides: “A discharge passage for discharging fuel pressurized in the pressurizing chamber; A relief passage connecting the discharge passage and the pressurizing chamber, or a suction passage of the pressurizing chamber; A relief valve for opening and closing the relief seat of the relief passage; A relief valve holder for holding the relief valve; A relief spring that biases the relief valve holder from the downstream side to the upstream side of the relief valve; A first inner peripheral portion that is disposed on the outer peripheral side of the relief valve holder and is formed on the relief seat side, and is formed on the downstream side of the relief valve from the first inner peripheral portion and from the first inner peripheral portion.
  • a housing having a second inner peripheral portion having a large cross-sectional area
  • the relief valve holder is formed at a position facing the first inner peripheral portion in a closed state of the throttle valve, and a throttle forming portion that forms a setting gap with the first inner peripheral portion.
  • a flow path forming portion that moves to a position facing the second inner peripheral portion in the opened state of the relief valve;
  • a high pressure fuel supply pump configured such that a gap between the flow path forming portion and the second inner peripheral portion is larger than the set gap. It is characterized by that.
  • FIG. 1 is an overall longitudinal sectional view of a high-pressure fuel supply pump according to a first embodiment in which the present invention is implemented. It is sectional drawing from another angle of the high-pressure fuel supply pump of a 1st Example.
  • FIG. 4 is a cross-sectional view of the fuel inlet shaft center and the discharge port shaft center perpendicular to the plunger shaft direction of the high-pressure fuel supply pump of the first embodiment.
  • 1 is an overall system view including a high-pressure fuel supply pump.
  • FIG. It is sectional drawing of the relief valve mechanism of 1st Example by which this invention was implemented. It is detail drawing of the relief valve mechanism of 1st Example by which this invention was implemented. It is an external view of a relief valve member. It is detail drawing of the relief valve mechanism of 2nd Example. It is an external view of the relief valve member of a 3rd Example. It is detail drawing of the relief valve mechanism of 3rd Example. It is detail drawing of the relief valve mechanism of 3rd Example. It is detail drawing of the relief valve mechanism
  • FIG. 4 is a diagram showing the overall configuration of the system including the high-pressure fuel supply pump according to the present invention.
  • a portion surrounded by a broken line indicates a main body 1A of a high-pressure fuel supply pump (hereinafter referred to as a high-pressure pump) 1 (see FIG. 1).
  • the mechanisms and components shown in the broken line are integrated with the high-pressure pump main body 1A. Indicates that it is incorporated.
  • the fuel in the fuel tank 20 is pumped up by the feed pump 21 and sent to the suction joint 10a of the pump body (pump body) 1A through the suction pipe 28.
  • the fuel that has passed through the suction joint 10a reaches the suction port 30a of the electromagnetic suction valve 30 that constitutes the variable capacity mechanism via the pressure pulsation reducing mechanism 9 and the suction passage 10b.
  • the pulsation prevention mechanism 9 will be described later.
  • the electromagnetic intake valve 30 includes an electromagnetic coil 308.
  • the anchor (electromagnetic plunger) 305 and the suction valve body 301 are urged by the urging force that is the difference between the urging force of the anchor spring 303 and the urging force of the valve spring 304.
  • the suction valve body 301 is biased in the valve opening direction, and the suction port 30d is open.
  • the urging force of the anchor spring 303 and the urging force of the valve spring 304 are:
  • the biasing force of the anchor spring 303 is set to be the biasing force of the valve spring 304.
  • the suction valve body 301 attached to the tip of the anchor 305 so that the tip of the anchor 305 contacts coaxially closes the suction port 30d by the biasing force of the valve spring 304.
  • the suction port 30d is a fuel passage (fuel passage) that connects the pressurization chamber 11 of the high-pressure pump 1 and the suction port 30a.
  • the operation of the high-pressure pump 1 will be described.
  • the plunger 2 is displaced downward in FIG. 4 due to the rotation of the cam, which will be described later, and in the suction stroke state, the volume of the pressurizing chamber 11 increases and the fuel pressure in the pressurizing chamber 11 decreases. If the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure in the suction passage 10b (suction port 30a) in this process, the fuel flows into the pressurizing chamber 11 through the suction port 30d in the open state.
  • the plunger 2 When the plunger 2 completes the suction stroke and shifts to the compression stroke, the plunger 2 moves to the compression stroke (a state of moving upward in FIG. 1).
  • the electromagnetic coil 308 remains in a non-energized state, and no magnetic biasing force acts on the anchor 305. Therefore, the suction valve body 301 remains open due to the biasing force of the anchor spring 303.
  • the compression stroke of the plunger 2 (the ascending stroke from the lower starting point to the upper starting point) consists of a return stroke and a discharge stroke. Then, by controlling the energization timing of the electromagnetic coil 308 of the electromagnetic intake valve 30, the amount of high-pressure fuel that is discharged can be controlled. If the timing of energizing the electromagnetic coil 308 is advanced, the rate of the return stroke during the compression stroke is reduced and the rate of the discharge stroke is increased. That is, the amount of fuel returned to the suction passage 10b (suction port 30a) decreases, and the amount of fuel discharged at high pressure increases.
  • the ratio of the return stroke during the compression stroke increases and the ratio of the discharge stroke decreases. That is, more fuel is returned to the suction passage 10b, and less fuel is discharged at high pressure.
  • the timing of energizing the electromagnetic coil 308 is controlled by a command from the ECU 27.
  • the amount of fuel discharged at high pressure can be controlled to the amount required by the internal combustion engine by controlling the energization timing to the electromagnetic coil 308.
  • a discharge valve mechanism 8 is provided at the outlet of the pressurizing chamber 11.
  • the discharge valve mechanism 8 includes a discharge valve seat surface (discharge valve seat portion) 8a, a discharge valve 8b, and a discharge valve spring 8c.
  • the discharge valve 8b In a state where there is no fuel differential pressure between the pressurizing chamber 11 and the fuel discharge port 12, the discharge valve 8b is pressed against the discharge valve seat surface 8a by the urging force of the discharge valve spring 8c and is in a closed state.
  • the discharge valve 8b is opened against the discharge valve spring 8c only when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure on the discharge joint side constituting the discharge port 12. By opening the discharge valve 8b, the fuel in the pressurizing chamber 11 is discharged at a high pressure to the common rail 23 through the fuel discharge port 12.
  • the fuel guided to the suction joint 10a is pressurized to a high pressure by the reciprocating motion of the plunger 2 in the pressurizing chamber 11 of the pump body 1A, and a required amount of fuel is pumped from the fuel discharge port 12 to the common rail 23. .
  • the common rail 23 is equipped with a direct injection injector 24 (so-called direct injection injector) and a pressure sensor 26.
  • the direct injection injectors 24 are mounted in accordance with the number of cylinders of the internal combustion engine, and are opened and closed according to a control signal from an engine control unit (ECU) 27 to inject fuel into the cylinders (combustion chambers) of the internal combustion engine. .
  • ECU engine control unit
  • the relief valve mechanism 100 is further provided in the pump body 1A.
  • a relief passage (return passage) 101 that communicates the downstream side of the discharge valve 8b and the pressurizing chamber 11 is provided separately from the discharge passage 110 to bypass the discharge valve mechanism 8.
  • the discharge passage 110 discharges the fuel pressurized in the pressurizing chamber 11.
  • the relief passage (return passage) 101 is configured to connect the discharge passage 110 and the pressurizing chamber 11, but not the pressurizing chamber 11 but connects the discharge passage 110 and the suction passages (10 a, 10 b). You may comprise as follows.
  • a relief valve 103 is provided in the relief passage 101. The relief valve 103 restricts the flow of fuel in only one direction from the discharge passage 110 to the pressurizing chamber 11.
  • the relief valve 103 is pressed against the relief valve seat 104 by a relief spring 102 that generates a pressing force (biasing force).
  • a pressing force biasing force
  • FIG. 1 is an overall cross-sectional view showing a high-pressure fuel supply pump according to a first embodiment of the present invention cut in the axial direction of a plunger.
  • FIG. 2 is an overall cross-sectional view at another angle of the high-pressure fuel supply pump according to the first embodiment of the present invention, and a cross-sectional view at the center of the suction joint axis.
  • FIG. 3 is an overall cross-sectional view showing the high-pressure fuel supply pump according to the first embodiment of the present invention, cut in a direction perpendicular to the axial direction of the plunger, and at the fuel inlet shaft center and discharge port shaft center. It is sectional drawing.
  • the high-pressure pump is fixed in close contact with the plane of the cylinder head 41 of the internal combustion engine using a flange 1e (see FIG. 3) provided in the pump body 1A.
  • An O-ring 61 is fitted into the pump body 1A in order to maintain airtightness between the cylinder head 41 and the pump body 1A.
  • a cylinder 6 having an end formed in a cylindrical shape is attached to the pump main body 1A so as to guide the forward / backward movement of the plunger 2 and to form the pressurizing chamber 11 therein. Further, the pressurizing chamber 11 communicates with an electromagnetic suction valve 30 for supplying fuel and a discharge valve mechanism 8 (see FIG. 3) for discharging fuel from the pressurizing chamber 11 to the discharge passage.
  • a passage 11a (see FIG. 3) is provided.
  • a tappet 3 that converts the rotational motion of the cam 5 attached to the camshaft of the internal combustion engine into a vertical motion and transmits it to the plunger 2.
  • the plunger 2 is pressure-bonded to the tappet 3 by a spring 4 through a retainer 15. Thereby, the plunger 2 can be moved back and forth (reciprocated) up and down with the rotational movement of the cam 5.
  • a plunger seal 13 (see FIG. 1) held at the inner peripheral lower end portion of the seal holder 7 is installed in a slidable contact with the outer periphery of the plunger 2 at the lower end portion of the cylinder 6 in the drawing. .
  • lubricating oil (including engine oil) for lubricating the sliding portion in the internal combustion engine is prevented from flowing into the pump body 1 through the blow-by gap.
  • the fuel pumped up by the feed pump 21 (see FIG. 4) is sent to the pump body 1A through the suction joint 10a coupled to the suction pipe 28.
  • the damper cover 14 is coupled to the pump body 1A to form low-pressure fuel chambers 10b and 10c, and the fuel that has passed through the suction joint 10a flows in.
  • a fuel filter 120 is attached upstream of the low-pressure fuel chambers 10b and 10c, for example, by being press-fitted into the pump body 1A in order to remove foreign matters such as metal powder contained in the fuel.
  • the suction joint 10a and the low-pressure fuel chambers 10b and 10c constitute a low-pressure fuel passage portion 10 through which low-pressure fuel flows.
  • a pressure pulsation reducing mechanism 9 for reducing the pressure pulsation generated in the high pressure pump 1 from spreading to the fuel pipe 28 is installed.
  • the fuel once sucked into the pressurizing chamber 11 is returned to the suction passage 10b (suction port 30a) through the opened suction valve body 301 again for capacity control, it returns to the suction passage 10b (suction port 30a).
  • Pressure pulsation occurs in the low-pressure fuel chambers 10b and 10c due to the fuel thus produced.
  • the pressure pulsation is absorbed and reduced by the pressure pulsation reducing mechanism 9.
  • the pressure pulsation reducing mechanism 9 is formed of a metal damper 9a in which two corrugated disk-shaped metal plates are bonded together at the outer periphery and an inert gas such as argon is injected therein. The pressure pulsation is reduced by absorption and expansion of the metal damper 9a.
  • Reference numeral 9b denotes a mounting bracket for fixing the metal damper 9a to the inner peripheral portion of the pump body 1A.
  • the electromagnetic coil 308 of the electromagnetic intake valve 30 is connected to the ECU 27 via a terminal 307. By repeatedly energizing and de-energizing the electromagnetic coil 308, the opening and closing of the intake valve body 301 is controlled.
  • the electromagnetic intake valve 30 is a variable control mechanism that controls the flow rate of fuel by opening and closing the intake valve body 301. When the electromagnetic coil 308 is not energized, the biasing force of the anchor spring 303 is transmitted to the suction valve body 301 via the anchor 305 and the anchor rod 302 formed integrally with the anchor 305.
  • a valve spring 304 is provided so as to face the urging force of the anchor spring 303.
  • the valve spring 304 is installed inside the intake valve body 301.
  • the biasing force of the anchor spring 303 and the biasing force of the valve spring 304 are set as described above.
  • the suction valve body 301 is urged in the valve opening direction, and the suction port 30d is opened.
  • the anchor rod 302 and the suction valve body 301 are in contact with each other at a portion indicated by 302b (state shown in FIG. 1).
  • the magnetic biasing force generated by energization of the electromagnetic coil 308 is set so that the anchor 305 has a force that can be attracted by overcoming the biasing force of the anchor spring 303 on the stator 306 side.
  • the electromagnetic coil 308 is energized, the anchor 305 moves to the stator 306 side (left side in the figure), and the stopper 302a formed at the end of the anchor rod 302 abuts on the anchor rod bearing 309 and is locked.
  • the movement amount of the anchor 305 and the movement amount of the suction valve body 301 are: The amount of movement of the anchor 301> The clearance is set so as to be the amount of movement of the intake valve body 301.
  • a suction valve seat member 310 is provided so that the suction valve body 301 can block the suction port 30d to the pressurizing chamber 11.
  • the suction valve seat member 310 is formed with a suction valve seat 310a.
  • the intake valve seat member 310 is inserted in the cylindrical boss 1b with security, and is fixed to the pump body 1A.
  • the discharge valve mechanism 8 has a discharge valve seat surface 8a provided in the pump body 1, a discharge valve member 8b provided with a bearing 8e so that reciprocal sliding can be held at the center, and a bearing of the discharge valve member 8b. It has a discharge valve guide member 8d provided with a slidable central shaft 8f.
  • the discharge valve member 8b forms an annular contact surface 8f that can be kept oil-tight by contacting the discharge valve seat surface 8a.
  • the discharge valve spring 8c is provided to urge the discharge valve member 8b in the valve closing direction.
  • the inclination of the discharge valve member 8b can be suppressed, and the discharge valve member 8b can be restrained so as to be slidable in the axial direction. It is possible to abut on the (discharge valve seat surface 8a).
  • the discharge valve mechanism 8 is configured by sealing the discharge valve guide member 8d to the pump body 1 by press-fitting, for example.
  • the discharge valve mechanism 8 acts as a check valve that restricts the fuel flow direction.
  • the relief valve mechanism 100 is accommodated in an accommodation hole (accommodation recess) 1C formed in the pump body 1A.
  • the accommodation hole 1C communicates with the pressurizing chamber 11 through the communication hole 11b. That is, the relief passage (return passage) 101 communicates with the pressurizing chamber 11 via the relief valve mechanism 100 through the communication hole 11b.
  • the relief valve mechanism 100 includes a relief valve housing 105, a relief valve 103, a relief valve holder 107, a relief spring 102, and a relief spring adjuster 106 that are integral with the relief valve seat 104.
  • the relief valve mechanism 100 is assembled outside the pump housing 1 as a subassembly.
  • the relief valve 103, the relief valve retainer 107, and the relief spring 102 are sequentially inserted into the relief valve housing 105 in this order, and the relief spring adjuster 106 is press-fitted and fixed to the relief valve housing 105.
  • the set load of the relief spring 102 is determined by the fixed position of the relief spring adjuster 106.
  • the valve opening pressure of the relief valve 103 is determined by the set load of the relief spring 102.
  • the relief valve holder 107 (relief valve holder) is urged from the downstream side to the upstream side of the relief valve 103 by the relief spring 102 to hold the relief valve 103.
  • the relief valve housing 105 is arranged on the outer peripheral side of the relief valve presser 107 (relief valve holder), and the relief valve 103 is formed on the relief valve seat 104 side rather than the first inner peripheral portion 15a and the first inner peripheral portion 15a.
  • a second inner peripheral portion 15b which is formed on the downstream side of the first inner peripheral portion 15a and has a larger cross-sectional area than the first inner peripheral portion 15a.
  • a setting gap 20 a is formed between the first inner peripheral portion 15 a of the relief valve housing 105 and the throttle forming portion 17 a of the relief valve presser 107.
  • a stroke in which the set gap 20a does not change and the relief valve presser 107 can be opened is defined as an initial stroke (St1).
  • a stroke in which the relief valve retainer 107 moves beyond the initial stroke is defined as a secondary stroke (St2).
  • a gap 20b is formed between the second inner peripheral portion 15b of the relief valve housing 105 and the flow path forming portion 17b on the relief valve seat 104 side of the throttle forming portion 17a.
  • the relationship between the setting gap 20a and the gap 20b is The setting gap 20a ⁇ gap 20b is set.
  • the relief valve holder 107 (relief valve holder) is formed at a position facing the first inner peripheral portion 15a when the relief valve 103 is closed, and the second inner peripheral portion 15b when the relief valve 103 is opened. And a flow path forming portion 17b that moves to a position facing the.
  • the gap 20b between the flow path forming portion 17b of the relief valve presser 107 (relief valve holder) and the second inner peripheral portion 15b is configured to be larger than the set gap 20a.
  • the relief valve holder 107 (relief valve holder) and the relief valve housing 105 arranged on the outer peripheral side of the relief valve holder 107 (relief valve holder) when the relief valve 103 is closed.
  • the gap 20a is formed as the maximum flow path.
  • a passage having a gap 20b larger than the set gap 20a is formed between the relief valve holder 107 (relief valve holder) and the relief valve housing 105 as a maximum passage.
  • the aperture effect by the setting gap 20a is obtained within the initial stroke (St1).
  • the differential pressure between the upstream side and the downstream side of the relief valve retainer 107 generated by the throttle effect is higher on the upstream side of the relief valve retainer 107 and lower on the downstream side, so that the relief valve retainer 107 does not force in the valve opening direction of the relief valve 103.
  • the relief valve holder 107 can be stroked greatly in the valve opening direction. That is, the clearance between the relief valve housing 105 and the relief valve retainer 107 increases with the stroke of the relief valve retainer 107.
  • the gap is enlarged, the squeezing effect is reduced, and the force generated in the valve opening direction of the relief valve presser 107 is reduced.
  • the stroke of the relief valve presser 107 can be regulated without providing an adjuster.
  • the outer cylindrical surface 17c of the relief valve retainer 107 has a plurality of (for example, three) notch portions 17d so as to form a throttle forming portion 17a and a flow path forming portion 17b. Is provided.
  • the length of the surface where the notch 17d is not provided is set so that it can always slide even in the secondary stroke (St2). That is, the throttle forming portion 17a of the relief valve holder 107 (relief valve holder) is formed at a position facing the first inner peripheral portion 15a even when the relief valve 103 is open, and is located between the first inner peripheral portion 15a. A setting gap 20a is formed. Accordingly, it is possible to prevent a malfunction that the relief valve retainer 107 comes out of the first inner peripheral portion 15a during the secondary stroke (St2) and the relief valve retainer 107 is not accommodated again in the first inner peripheral portion 15a.
  • the second inner peripheral portion 15b of the relief valve housing 105 and the flow path forming portion 17b of the relief valve retainer 107 are both inclined.
  • the relief valve holder 107 (relief valve holder) includes a cylindrical portion (throttle forming portion 17a) and an inclined portion (flow path formation) that is inclined from the cylindrical portion (throttle forming portion 17a) toward the relief valve seat 104 toward the inner peripheral side. Part 17b).
  • the cylindrical portion forms the diaphragm forming portion 17a, and the inclined portion forms the flow path forming portion 17b.
  • the inner peripheral portion of the relief valve housing 105 is formed with a recess (second inner peripheral portion 15b) that is recessed from the first inner peripheral portion 15a to the outer peripheral side, and the relief valve 103 is opened to open the relief valve.
  • the presser 107 (relief valve holder) moves in the set opening degree and valve opening direction
  • the upstream side and the recessed part (second inner peripheral part 15b) from the upstream outer peripheral end 17e of the relief valve presser 107 (relief valve holder). Are communicated to form the flow path.
  • FIG. 7 shows an external view of the relief valve presser 107.
  • a cutout portion 17 d was formed in the third inner peripheral portion 17 c of the relief valve retainer 107.
  • Relief valve holder 107 by notch 17d In the (relief valve holder), a plurality of inclined portions (flow path forming portions 17b) are formed on the outer peripheral side. It is desirable in production that there are three inclined portions (flow path forming portions 17b). Similarly, three aperture forming portions 17a are formed between two adjacent inclined portions (second inner peripheral portions 15b). In other words, a plurality of flow path forming portions 17b are formed in the relief valve presser 107 (relief valve holder), and a throttle forming portion 17a is formed between two adjacent flow path forming portions 17b.
  • the relief valve holder 107 (relief valve holder) is viewed from the axial direction of the relief valve 103, it is formed such that the outer periphery of the throttle forming portion 17a is larger than the outer periphery of the flow path forming portion 17b.
  • the throttle forming portion 17 a is formed in a predetermined region of the relief valve presser 107 (relief valve holder) in the axial direction of the relief valve 103.
  • the flow path forming portion 17b is formed in a region smaller than the predetermined region of the relief valve presser 107 (relief valve holder) in the axial direction of the relief valve 103.
  • the flow path forming portion 17b of the relief valve holder 107 is configured by an inclined portion that is inclined toward the inner peripheral side from the throttle forming portion 17a that forms the setting gap 20a with the first inner peripheral portion 15a.
  • the boundary between the throttle forming portion 17a and the flow path forming portion 17b is disposed at a position overlapping the first inner peripheral portion 15a in the closed state of the relief valve 103, and is disposed closer to the inner peripheral side than the first inner peripheral portion 15a. Is done.
  • the relief valve holder 107 has a convex portion that is convex on the downstream side in the relief flow path, and the relief spring 102 is wound and held on the outer peripheral side of the convex portion.
  • the outer cylindrical surface 17c on the upstream side with respect to the convex portion is guided to face the first inner peripheral portion 15a.
  • the axial length of the convex portion is configured to be slightly larger than the outer cylindrical surface 17c is shown, this configuration is not necessarily required depending on the length of the spring end winding.
  • the relief spring 102 is wound around and supported by the relief spring stopper 106, and the number of end turns of the relief spring 102 at this time is set to be greater than one.
  • the natural frequency of the relief spring 102 can be adjusted by setting the number of end turns, and damage due to surging can be prevented.
  • the number of end turns of the spring is large, the seat of the spring is stabilized, so that the lateral force acting on the relief valve presser 107 is reduced, and the friction between the outer cylindrical surface 17c and the first inner peripheral portion 15a of the relief valve housing 105 is reduced. Since the force can be reduced, the wear resistance of the relief valve holder 107 can be ensured.
  • the unitized relief valve mechanism 100 is fixed by press-fitting the relief valve housing 105 into the inner peripheral wall of the accommodation hole (cylindrical through-hole) 1C provided in the pump body 1A.
  • the discharge joint 12a that forms the fuel discharge port 12 is fixed so as to block the accommodation hole 1C of the pump body 1, and the fuel can be prevented from leaking from the high-pressure pump 1 and at the same time can be connected to the common rail 23. To do.
  • the accommodation hole 1C and the accommodation hole 1D are connected by a discharge passage 110 as shown in FIG.
  • the discharge passage 110 communicates with the fuel discharge port 12 through the accommodation hole 1C.
  • the pressure in the pressurizing chamber 11 increases as the volume decreases.
  • the discharge valve mechanism 8 is opened, and fuel is discharged from the pressurization chamber 11 to the discharge passage 110. From the moment when the discharge valve mechanism 8 is opened to the moment, the pressure in the pressurizing chamber 11 overshoots and becomes a very high pressure. This high pressure is also propagated in the discharge flow path 110, and the pressure in the discharge flow path 110 also overshoots at the same timing.
  • the outlet of the relief valve mechanism 100 is connected to the pressurizing chamber 11, so that the pressure in the pressurizing chamber 11 acts on the outlet of the relief valve mechanism 100, and the relief valve mechanism 11
  • the pressure in the discharge channel 110 acts on the inlet.
  • the pressure difference between the inlet and the outlet of the relief valve 103 is equal to or higher than the valve opening pressure of the relief valve 103.
  • the relief valve 103 does not malfunction.
  • the discharge pressure becomes abnormally high in an operation state where not much fuel is required.
  • the pressure sensor 26 of the common rail 23 detects an abnormally high pressure, the capacity control mechanism itself is broken, so that the abnormally high pressure cannot be eliminated.
  • the relief valve mechanism 100 of this embodiment functions as a safety valve.
  • the pressure in the pressurizing chamber 11 decreases as the volume increases.
  • the pressure of the inlet of the relief valve mechanism 100 that is, the pressure of the discharge passage 110 becomes higher than the outlet pressure of the relief valve 103, that is, the pressure of the pressurizing chamber 11
  • the relief valve mechanism 100 becomes higher than the valve opening pressure. Will open.
  • the fuel having an abnormally high pressure in the common rail 23 is returned to the pressurizing chamber 11.
  • the high-pressure piping system such as the common rail 23 does not exceed a specified pressure, and the high-pressure piping system such as the common rail 23 is protected.
  • the relief valve housing 105 has a third inner peripheral portion 15c having a smaller cross-sectional area than the second inner peripheral portion 15b.
  • a relief spring stopper 106 is press-fitted into the inner peripheral portion of the third inner peripheral portion 15c. That is, the relief valve housing 105 has a third inner peripheral portion 15c formed on the downstream side of the relief valve 103 with respect to the second inner peripheral portion 15b.
  • the cross-sectional area of the 3rd inner peripheral part 15c is comprised so that it may become smaller than the largest cross-sectional area of the 2nd inner peripheral part 15b.
  • the relief valve housing 105 is fixed by pressing the outer peripheral side of the third inner peripheral portion 15 c into a hole formed in the pump body 11 forming the pressurizing chamber 11 in the horizontal direction.
  • the relief valve housing 105 has a third inner peripheral portion 15c that is formed closer to the pressurizing chamber 11 or the suction passages (10a, 10b) than the second inner peripheral portion 15b.
  • the third inner peripheral portion 15c is formed so that the cross-sectional area is smaller than the maximum cross-sectional area of the second inner peripheral portion 15b.
  • the relief valve 103, the relief valve holder 107, the relief spring 102, and the relief valve housing 105 are integrated to form a relief valve unit 100.
  • the relief valve unit 100 is fixed by press-fitting the outer peripheral side of the third inner peripheral portion 15 c into the hole of the pump body that forms the pressurizing chamber 11.
  • the flow path forming portion of the relief valve holder is a high pressure fuel supply pump configured by an inclined portion that is inclined toward an inner peripheral side from a throttle forming portion that forms a set gap with the first inner peripheral portion.
  • the third embodiment will be described below with reference to FIGS. A description of the same contents as those in the first and second embodiments is omitted.
  • the inner cylindrical surface 15e of the relief valve housing 105 can always guide the throttle forming portion 17a of the relief valve retainer 107 even in the secondary stroke (St2).
  • St2 secondary stroke
  • four counterbore holes 15d are provided as an example, but theoretically one or more counterbore holes may be provided.
  • the shape of the spot facing hole may be a square shape instead of a round hole.
  • a set gap 20a is formed between the first inner peripheral portion 15a of the relief valve housing 105 and the throttle forming portion 17a of the relief valve presser 107, and the secondary stroke.
  • a gap 20b is formed between the second inner peripheral portion 15b of the relief valve housing 105 and the inner cylindrical surface 15f of the counterbore hole 15d.
  • valve body presser can be stroked greatly without providing an adjuster for regulating the stroke of the valve body presser.
  • this invention is not limited to an above-described Example, Various modifications are included.
  • the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations.
  • SYMBOLS 1A Pump main body, 2 ... Plunger, 6 ... Cylinder, 6c, 6c '... Annular protrusion, 6d ... Annular recessed part (annular groove), 8 ... Discharge valve mechanism, 9 ... Pressure pulsation reduction mechanism, 30 ... Electromagnetic suction valve, 100 ... relief valve mechanism.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Safety Valves (AREA)

Abstract

La présente invention concerne une pompe d'alimentation en carburant haute pression dans laquelle la course d'un support de corps de soupape peut être restreinte sans utiliser de dispositif de réglage pour restreindre la course du support de corps de soupape. Cette pompe d'alimentation en carburant haute pression est pourvue d'un logement disposé sur le côté périphérique externe d'un support de soupape de décharge, le logement présentant une première section périphérique interne qui est formée sur le côté d'un siège en relief, et présentant également une seconde section périphérique interne qui est formée plus loin vers le côté aval d'une soupape de décharge que la première section périphérique interne et qui présente une surface transversale supérieure à la première section périphérique interne. La pompe d'alimentation en carburant haute pression est configurée de telle sorte que : le support de soupape de décharge comporte une section de formation d'étranglement pour former un espace défini entre la section de formation d'étranglement et la première section périphérique interne, et présente également une section de formation de passage d'écoulement qui est formée à un emplacement faisant face à la première section périphérique interne lorsque la soupape de décharge est dans un état fermé, et qui se déplace vers un emplacement faisant face à la seconde section périphérique interne lorsque la soupape de décharge est dans un état ouvert ; et l'espace entre la section de formation de passage d'écoulement et la seconde section périphérique interne est réglé pour être supérieur à l'espace défini.
PCT/JP2017/021075 2016-06-29 2017-06-07 Pompe d'alimentation en carburant haute pression WO2018003435A1 (fr)

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JP2016128290 2016-06-29

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108644170A (zh) * 2018-06-04 2018-10-12 中国石油化工股份有限公司 一种安全压力可调节插装式安全溢流阀
JP2020070777A (ja) * 2018-11-01 2020-05-07 株式会社デンソー 電磁弁、および、これを用いた高圧ポンプ
WO2022091553A1 (fr) * 2020-10-28 2022-05-05 日立Astemo株式会社 Pompe à carburant

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0472454A (ja) * 1990-07-09 1992-03-06 Nippondenso Co Ltd 燃料噴射装置の安全弁
JP2004138062A (ja) * 2002-10-15 2004-05-13 Robert Bosch Gmbh 圧力制限弁及び該圧力制限弁を備えた燃料系
JP2009114868A (ja) * 2007-11-01 2009-05-28 Hitachi Ltd 高圧液体供給ポンプ
JP2012012950A (ja) * 2010-06-29 2012-01-19 Denso Corp 定残圧弁
JP2013241835A (ja) * 2012-05-17 2013-12-05 Nippon Soken Inc 高圧燃料ポンプのリリーフ弁

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0472454A (ja) * 1990-07-09 1992-03-06 Nippondenso Co Ltd 燃料噴射装置の安全弁
JP2004138062A (ja) * 2002-10-15 2004-05-13 Robert Bosch Gmbh 圧力制限弁及び該圧力制限弁を備えた燃料系
JP2009114868A (ja) * 2007-11-01 2009-05-28 Hitachi Ltd 高圧液体供給ポンプ
JP2012012950A (ja) * 2010-06-29 2012-01-19 Denso Corp 定残圧弁
JP2013241835A (ja) * 2012-05-17 2013-12-05 Nippon Soken Inc 高圧燃料ポンプのリリーフ弁

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108644170A (zh) * 2018-06-04 2018-10-12 中国石油化工股份有限公司 一种安全压力可调节插装式安全溢流阀
JP2020070777A (ja) * 2018-11-01 2020-05-07 株式会社デンソー 電磁弁、および、これを用いた高圧ポンプ
WO2022091553A1 (fr) * 2020-10-28 2022-05-05 日立Astemo株式会社 Pompe à carburant

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JP6649483B2 (ja) 2020-02-19
JPWO2018003435A1 (ja) 2018-11-15

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