WO2014083979A1 - Pompe d'alimentation en carburant à haute pression - Google Patents

Pompe d'alimentation en carburant à haute pression Download PDF

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Publication number
WO2014083979A1
WO2014083979A1 PCT/JP2013/078893 JP2013078893W WO2014083979A1 WO 2014083979 A1 WO2014083979 A1 WO 2014083979A1 JP 2013078893 W JP2013078893 W JP 2013078893W WO 2014083979 A1 WO2014083979 A1 WO 2014083979A1
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WIPO (PCT)
Prior art keywords
fuel
valve
pressure
relief valve
relief
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PCT/JP2013/078893
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English (en)
Japanese (ja)
Inventor
勝巳 宮崎
山田　裕之
悟史 臼井
稔 橋田
Original Assignee
日立オートモティブシステムズ株式会社
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Publication of WO2014083979A1 publication Critical patent/WO2014083979A1/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
    • 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

Definitions

  • the present invention relates to a high-pressure fuel supply pump that pumps high-pressure fuel to a fuel injection valve of an internal combustion engine.
  • the present invention relates to a high-pressure fuel supply pump incorporating a relief valve as a safety valve for avoiding an abnormally high fuel pressure.
  • Patent Document 1 discloses a high-pressure fuel supply pump in which a sole relief valve as a safety valve is incorporated in a high-pressure fuel supply pump, and an outlet of the relief valve is connected to a low-pressure side upstream from an intake valve of the high-pressure fuel supply pump. ing. Specifically, the suction passage and the discharge passage of the high-pressure fuel supply pump are arranged close to each other, a communication passage is provided in these, and a relief valve is provided in the communication passage. The relief valve opening pressure is set higher than the system fuel pressure during normal operation.
  • the relief valve is opened, and the fuel in the pressure accumulating chamber is discharged to the suction passage.
  • the failure of the fuel injection valve that supplies fuel to the engine, the engine control unit (ENGINE CONTROL UNIT: hereinafter referred to as ECU) that controls the fuel injection valve and the high-pressure fuel supply pump, etc. fail, and high-pressure piping such as common rails. If an abnormally high pressure occurs, the pressure in the high-pressure pipe cannot be released sufficiently to the low-pressure side due to insufficient fuel capacity that opens from the relief valve to the low-pressure side, and the fuel pressure exceeds the allowable pressure value of the high-pressure pipe. There is a problem of end.
  • the relief is provided within the circumference surrounded by the outside of the outer diameter of the plunger and the cylinder and the inside of the outer diameter of the pump housing.
  • a valve must be placed. Therefore, in order to increase the size of the relief valve and to provide a plurality of relief valves, it is necessary to increase the outer diameter shape of the housing. As a result, the high-pressure fuel supply pump becomes large.
  • a high-pressure fuel pump that pressurizes fuel sucked into a pressurizing chamber and discharges pressurized fuel by opening a discharge valve, and includes a relief passage that connects the downstream side and the upstream side of the discharge valve.
  • the relief passage has a relief valve mechanism having a check valve that stops the flow of fuel from the downstream side to the upstream side of the discharge valve.
  • the relief valve mechanism attaches a relief valve, a valve seat, and a relief valve to the valve seat.
  • a high pressure fuel pump comprising a damper mechanism for restricting a spring to be energized and a valve opening operation of a relief valve.
  • the suction passage has a suction passage for sucking fuel into the pressurizing chamber and a discharge passage for discharging fuel from the pressurization chamber, and the fuel is sucked and discharged by a plunger that reciprocates in the pressurization chamber.
  • a relief passage that communicates the upstream side (low pressure side) of the suction valve of the suction passage and the downstream side (high pressure side) of the discharge valve of the discharge passage.
  • the relief passage has a relief valve that restricts the flow of fuel in only one direction from the discharge passage to the suction passage, and the relief valve has a valve and a valve seat, and the contact / non-contact between the valve and the valve seat
  • the contact switches between low pressure side and high pressure side communication, and when the pressure difference between the high pressure side and the low pressure side exceeds the specified valve opening pressure, the valve separates from the valve seat, and the low pressure side and the high pressure side Communicate with the high pressure fuel In those open to the low pressure side, the valve being in contact with the valve seat, after separated from the valve seat, a high-pressure fuel supply pump, characterized in that it comprises a mechanism for limiting the valve opening operation speed.
  • the relief valve opening at the time of sudden (instantaneous) increase in fuel pressure due to fuel pressure pulsation is suppressed, and the fuel pressure due to abnormality of the high-pressure fuel system in which the fuel pressure increases over a long time compared to the fuel pressure pulsation When rising, the relief valve can be opened, and an increase in fuel pressure due to an abnormality in the high-pressure piping system including the control device can be avoided without impairing the efficiency of the high-pressure fuel supply pump.
  • FIG. 5 is an overall cross-sectional view of a high-pressure fuel supply pump according to first, second to third and fourth embodiments in which the present invention is implemented. It is the figure which showed the structure of the discharge valve mechanism of the high pressure fuel supply pump by 1st, 2nd thru
  • a mechanism for suppressing the amount of fuel leaking from the high-pressure side to the low-pressure side by restricting the valve operating speed when the relief valve opens during normal operation makes the valve difficult to open. Will be described.
  • a high pressure fuel supply pump having a discharge valve in each of the valve and the discharge passage has a relief passage that communicates the upstream side (low pressure side) of the suction valve of the suction passage and the downstream side (high pressure side) of the discharge valve of the discharge passage.
  • the relief passage is provided with a relief valve that restricts the flow of fuel in only one direction from the discharge passage to the suction passage.
  • the relief valve has a valve and a valve seat.
  • the contact / non-contact between the valve and the valve seat switches between communication between the low pressure side and the high pressure side, and the pressure difference between the pressure on the high pressure side and the pressure on the low pressure side changes.
  • the valve opening pressure exceeds a specified value
  • the valve is detached from the valve seat, the low pressure side and the high pressure side are communicated, and the high pressure fuel is opened to the low pressure side.
  • the valve in contact with the valve seat is provided with a mechanism for limiting the valve opening operation speed after being detached from the valve seat.
  • This mechanism can also suppress the fuel pressure in the high-pressure pipe within a specified value when an abnormal high pressure occurs due to a failure of the fuel injection valve.
  • This mechanism has a configuration that includes a mechanism that limits the valve opening operation speed after the relief valve that is in contact (sitting) with the valve seat is separated (opened) from the valve seat.
  • the relief valve has a fuel chamber filled with fuel that changes in volume with the movement of another valve provided on the side opposite to the valve seat, and the fuel chamber has a fuel that changes in volume. This is a mechanism that restricts the movement of the relief valve by restricting the movement of the valve.
  • the fuel chamber is connected to the low pressure side only by a minute gap, and the amount of fuel moving between the fuel chamber and the low pressure side is limited to adjust the rate of volume change of the fuel chamber.
  • the fuel chamber is provided with a check valve that restricts the movement of fuel from the low pressure side only to the fuel chamber in a part different from the minute gap and the relief valve, and the check valve is set only when the volume of the fuel chamber increases.
  • a mechanism that enables movement of fuel between the low pressure side and the fuel chamber.
  • the amount of high-pressure fuel that leaks from the high-pressure side to the low-pressure side can be reduced compared to a relief valve mechanism that does not have a simple mechanism. That is, since the valve opening due to the fuel pressure pulsation is suppressed, the amount of fuel leaking from the high pressure side to the low pressure side is small, and a high-pressure fuel supply pump with high energy efficiency can be obtained. Further, during the valve closing operation, the relief valve moves in the direction of seating on the valve seat side, so that the volume of the fuel chamber increases, and fuel flows from the low pressure side to the fuel chamber via the check valve. This speeds up the valve closing speed of the valve.
  • the relief valve can be seated (closed) earlier in the valve seat, so the amount of high-pressure fuel that leaks from the high-pressure side to the low-pressure side can be reduced, and an energy-efficient high-pressure fuel supply pump is obtained. be able to.
  • a first embodiment of the present invention will be described with reference to FIGS. First, the configuration and operation of the system will be described using the overall configuration diagram of the system shown in FIG. A portion surrounded by a broken line indicates the pump housing 1 of the high-pressure pump, and the mechanisms and components shown in the broken line indicate that they are integrated into the pump housing 1 of the high-pressure pump.
  • the fuel in the fuel tank 20 is pumped up by the feed pump 21 based on a signal from the engine control unit 27 (hereinafter referred to as ECU), pressurized to an appropriate feed pressure, and passed through the suction pipe 28 to the suction inlet 10a of the high-pressure fuel supply pump. Sent to.
  • ECU engine control unit 27
  • the fuel that has passed through the suction inlet 10a reaches the suction port 30a of the electromagnetic suction valve mechanism 30 constituting the variable capacity mechanism via the pressure pulsation reducing mechanism 9 and the suction passages 10b and 10c.
  • the electromagnetic intake valve mechanism 30 includes an electromagnetic coil 30b. When the electromagnetic coil 30b is energized, the electromagnetic plunger 30c is moved rightward in FIG. 1, and the compressed state of the spring 33 is maintained. At this time, the suction valve 31 attached to the tip of the electromagnetic plunger 30c opens the suction port 32 connected to the pressurizing chamber 11 of the high-pressure pump.
  • the suction valve 31 By the valve opening force due to the fluid differential pressure, the suction valve 31 is set to open over the biasing force of the spring 33 and open the suction port 32. In this state, when a control signal from the ECU 27 is applied to the electromagnetic intake valve 30, an electric current flows through the electromagnetic coil 30b of the electromagnetic intake valve 30, and the electromagnetic plunger 30c is moved to the right in FIG. The spring 33 is maintained in a compressed state. As a result, the state in which the suction valve 31 opens the suction port 32 is maintained. When the plunger 2 finishes the suction stroke while the application state of the input voltage is maintained in the electromagnetic suction valve 30, and the plunger 2 moves to the compression stroke that is displaced upward in FIG. 1, the magnetic biasing force remains maintained.
  • the suction valve 31 remains open.
  • the volume of the pressurizing chamber 11 decreases with the compression motion of the plunger 2.
  • the fuel once sucked into the pressurizing chamber 11 passes through the suction valve 31 in the valve opening state again and the suction passage 10 c (suction port). 30a), the pressure in the pressurizing chamber does not increase. This process is called a return process.
  • the control signal from the ECU 27 is canceled and the electromagnetic coil 30b is de-energized, the magnetic biasing force acting on the electromagnetic plunger 30c is after a certain time (after the magnetic or mechanical delay time). Erased.
  • the suction valve 31 closes the suction port 32 by the biasing force by the spring 33 when the electromagnetic force acting on the electromagnetic plunger 30 c disappears.
  • the suction port 32 is closed, the fuel pressure in the pressurizing chamber 11 increases with the upward movement of the plunger 2 from this time.
  • the pressure in the fuel discharge port 12 or higher is reached, high pressure discharge of the fuel remaining in the pressurizing chamber 11 is performed via the discharge valve unit 8 and supplied to the common rail 23.
  • This stroke is referred to as a discharge stroke. That is, the compression stroke of the plunger 2 (the upward stroke from the lower starting point to the upper starting point) includes a return stroke and a discharge stroke.
  • the quantity of the high pressure fuel discharged can be controlled by controlling the timing which cancels
  • FIG. If the timing for releasing the energization of the electromagnetic coil 30c is advanced, the ratio of the return stroke is small during the compression stroke, and the ratio of the discharge stroke is large. That is, the amount of fuel returned to the suction passage 10c (suction port 30a) is small, and the amount of fuel discharged at high pressure is large. On the other hand, if the timing of releasing the input voltage is delayed, the ratio of the return stroke during the compression stroke is large and the ratio of the discharge stroke is small.
  • the amount of fuel returned to the suction passage 10c is large, and the amount of fuel discharged at high pressure is small.
  • the timing for releasing the energization of the electromagnetic coil 30c is controlled by a command from the ECU.
  • the amount of fuel discharged at high pressure can be controlled to an amount required by the internal combustion engine by controlling the timing of releasing the energization of the electromagnetic coil 30c.
  • the fuel guided to the fuel suction port 10 a is pressurized to a high pressure by the reciprocating motion of the plunger 2 in the pressurizing chamber 11 of the pump body 1, and is pumped from the fuel discharge port 12 to the common rail 23.
  • An injector 24 and a pressure sensor 26 are attached to the common rail 23.
  • the injectors 24 are mounted in accordance with the number of cylinders of the internal combustion engine, open and close according to a control signal from an engine control unit (ECU) 27, and inject fuel into the cylinders.
  • ECU engine control unit
  • a convex portion 1A as a pressurizing chamber 11 is formed at the center of the pump housing 1, and a recess 11A for mounting the discharge valve mechanism 8 is formed between the inner peripheral wall of the pressurizing chamber 11 and the discharge port 12. ing. Further, a hole 30A for mounting an electromagnetic suction valve mechanism 30 for supplying fuel to the pressurizing chamber 11 is provided on the outer wall of the pump housing on the same axis as the recess 11A for mounting the discharge valve mechanism 8. .
  • the recess 11A for mounting the discharge valve mechanism 8 and the axis of the hole for attaching the electromagnetic suction valve mechanism 30 are formed in a direction intersecting, A discharge valve mechanism 8 for discharging fuel from the chamber 11 to the discharge passage is provided.
  • a cylinder 6 that guides the reciprocating motion of the plunger 2 is attached so as to face the pressurizing chamber.
  • the outer periphery of the cylinder 6 is held by a cylinder holder 7, and the cylinder holder 7 is held inside the housing 1.
  • the cylinder 6 is fixed to the pump housing 1 via the cylinder holder 7 by screwing a screw threaded on the outer periphery of the cylinder holder 7 into a screw threaded on the pump housing 1.
  • the cylinder 6 holds the plunger 2 that moves forward and backward in the pressurizing chamber 11 so as to be slidable along the forward and backward movement direction.
  • the lower end of the plunger 2 is provided with a tappet 3 that converts the rotational motion of the cam 5 attached to the camshaft of the 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. Accordingly, the plunger 2 can be moved up and down (reciprocated) in accordance with the rotational movement of the cam 5.
  • the plunger seal 13 held at the lower end of the inner periphery of the cylinder holder 7 is installed in a state of slidably contacting the outer periphery of the plunger 2 at the lower end of the cylinder 6 in the figure.
  • the blow-by gap between 6 and 6 is sealed to prevent fuel from leaking outside.
  • lubricating oil including engine oil
  • that lubricates the sliding portion in the engine room is prevented from flowing into the pump body 1 through the blow-by gap.
  • the damper cover 14 is provided with a pressure pulsation reduction mechanism 9 that reduces the pressure pulsation generated by the vertical movement of the plunger 2 from spreading to the fuel pipe 28.
  • the damper cover 14 is fixed to the pump housing 1 by press fitting and welding, and the suction passage 10 as a low pressure passage is composed of 10a, 10b, 10c, 10d.
  • a pressure pulsation reducing mechanism 9 that reduces the pulsation of the pressure pulsation generated in the pump housing 1 generated in the pump with the reciprocating motion of the plunger 2 to the fuel pipe 28 is a metal diaphragm set formed of two metal diaphragms. It consists of a body 9A. In the metal diaphragm assembly 9A, two metal diaphragms are welded together at the outer periphery thereof, and an inert gas is injected therein.
  • the peripheral part of the metal diaphragm assembly 9A is supported by the support member 10A1 and the support member 10A2 from above and below, and is unitized in this state to form a damper unit 118.
  • the damper unit 118 configured as described above is housed in a recess formed in the pump housing 1. At that time, positioning in the radial direction is performed between the outer peripheral portion 10A3 of the support member 10A2 and the inner peripheral portion 1C of the pump housing 1, but not a press fit but a gap. In this state, the damper cover 14 is further assembled from above.
  • the damper cover 14 is formed in a cup shape, and an annular end surface on the open side thereof is fixed to the pump housing 1 by welding. By sealing by welding, the damper chamber is sealed against the outside air. As a result, a damper chamber is defined in the suction passage 10 and a pressure pulsation mechanism 9 is formed.
  • damper unit 118 is fixed in such a manner that the support member 10A2 is sandwiched by the damper cover 14 from above and the support member 10A1 is sandwiched from below. This is fixed in a direction that promotes the press-fitting of the support member 10A2 and the support member 10A1.
  • the passage 10d is formed on the inner peripheral surface of the damper cover 14, and the intake fuel is guided between the damper cover 14 and the metal diaphragm assembly 9A by the passage 10d.
  • the damper cover 14 has a gap in a part of the surface in contact with the support member 10A2, the fuel is distributed to both surfaces of the metal diaphragm assembly 9A through the passage 10d.
  • a discharge port (discharge side pipe connecting portion) 12 is formed in the pump housing 1, and a pressurizing chamber 11 for pressurizing fuel is formed in the middle of a fuel passage from the suction port 10 a to the outlet 12.
  • An electromagnetic suction valve mechanism 30 is provided at the entrance of the pressurizing chamber 11.
  • the suction valve 31 is biased in a direction to close the suction port by a suction valve spring 33 provided in the electromagnetic suction valve mechanism 30.
  • the electromagnetic intake valve mechanism 30 becomes a check valve that restricts the flow direction of fuel. This is as described above.
  • a discharge valve mechanism 8 is provided at the outlet of the pressurizing chamber 11.
  • the discharge valve mechanism 8 includes a sheet member (sheet member) 8a, a discharge valve 8b, a discharge valve spring 8c, and a discharge valve spring holder 8d as a discharge valve stopper.
  • the discharge valve unit (discharge valve mechanism) 8 is press-fitted into the pump housing 1 from the left side in the figure. And fixed by the press-fitting portion 8a1.
  • the outer peripheral portion of the press-fit portion 8a1 functions as a metal pressure contact seal with the inner peripheral surface of the pump body, and also has a function of hydraulically blocking the pressurizing chamber 11 and the discharge port 12.
  • the discharge valve 8b In a state where there is no fuel differential pressure between the pressurizing chamber 11 and the discharge port 12, the discharge valve 8b is pressed against the seat member 8a by the urging force of the discharge valve spring 8c and is in a closed state. Only when the fuel pressure in the pressurizing chamber 11 becomes larger than the fuel pressure in the discharge port 12 by a predetermined value, the discharge valve 8b is opened against the discharge valve spring 8c, and the pressure in the pressurizing chamber 11 is increased. The fuel is discharged to the common rail 23 through the discharge port 12. During the discharge stroke, as shown in FIG. 4, the fuel pressurized in the pressurizing chamber 11 passes through the gap between the passage 8 d 1 processed on the side surface of the discharge valve spring holder 8 d and the pump housing 1 to the discharge passage 12. It is discharged.
  • the discharge valve 8b When the discharge valve 8b is opened, the discharge valve 8b comes into contact with the discharge valve spring holder 8d and its operation is restricted. Therefore, the stroke of the discharge valve 8b is appropriately determined by the discharge valve spring holder 8d. If the stroke is too large, the fuel discharged to the fuel discharge port 12 will flow back into the pressurizing chamber 11 again due to the delay in closing the discharge valve 8b, and the efficiency of the high-pressure pump will decrease. . Further, when the discharge valve 8b repeats opening and closing movements, the discharge valve spring holder 8d guides the discharge valve 8b so as to move only in the stroke direction. By configuring as described above, the discharge valve mechanism 8 becomes a check valve that restricts the flow direction of fuel.
  • the high-pressure fuel supply pump is fixed to the engine by the flange 41, the bolt 42, and the bush 40.
  • the flange 41 is welded to the pump housing 1 by an annular fixing portion 41a. In this embodiment, a welding beam is used.
  • the flange 41 fixes the pump housing 1 to the engine by two bolts 42.
  • the two bushes 40 are attached to the flange 41, and are attached to the opposite side of the engine.
  • the two bolts 42 are screwed into respective screws formed on the engine side, and the two bushes 40 and the flange 41 are pressed against the engine, thereby fixing the high-pressure fuel supply pump to the engine.
  • the pump housing 1 is further provided with a relief passage 210 and a relief passage 211 that communicate the downstream side of the discharge valve 8b with the suction passage 10b.
  • the relief passage 210 and the relief passage 211 are provided with a relief valve B202 that restricts the flow of fuel in only one direction from the discharge passage to the suction passage 10b.
  • the relief valve B202 is pressed against the relief valve seat B201 by a relief spring B204 that generates a pressing force.
  • the relief valve B202 is pressed to the relief valve seat.
  • the set valve opening pressure is set so that the valve opens away from B201.
  • the pressure when the relief valve B202 starts to open is defined as the set valve opening pressure.
  • the set valve opening pressure of the relief valve B202 is set to 17.5 MPa.
  • the pressure applied to the relief valve B202 by the pressure overshoot is about 22 MPa at the maximum. Therefore, the pressure becomes higher than the set valve opening pressure of the relief valve B202, the relief valve B202 opens unintentionally, and a part of the high-pressure fuel leaks into the low-pressure passage 10b (malfunction of the relief valve). This means a reduction in the high-pressure fuel discharged from the high-pressure fuel supply pump to the common rail 23, leading to a reduction in efficiency as the high-pressure fuel supply pump.
  • the set valve opening pressure of the relief valve B202 is set to be equal to or higher than the pressure overshoot pressure, the pump discharge efficiency will not be lowered. It cannot be suppressed to the following.
  • the pressure overshoot caused by the fuel pressure pulsation occurs in a shorter time than the fuel pressure abnormality of the high pressure fuel system.
  • a mechanism that suppresses valve opening when a pressure overshoot due to fuel pressure pulsation occurs and opens when a fuel pressure abnormality occurs in the high-pressure fuel system will be described below.
  • the relief valve mechanism B200 is integrated with a relief valve housing B206, a relief valve B202, a relief valve presser B203, a relief spring B204, a relief valve presser guide B208, a back pressure valve B209, and a back pressure valve seat B212 that are integral with the relief valve seat B201. It consists of a spring holder B205.
  • the relief valve mechanism B200 is assembled outside the pump housing 1 as a subassembly, and then fixed to the pump housing 1 by press fitting. First, the relief valve B202, the relief valve presser B203, and the relief spring B204 are sequentially inserted into the relief valve housing B206 in this order.
  • the back pressure valve B209 and the relief valve pressing guide B208 are sequentially inserted into the spring holder B205 in this order, and the relief valve pressing guide B208 is press-fitted and fixed to the spring holder B205.
  • the shape of the relief valve pressing guide B208 is a bottomed cylinder, and a hole B214 through which fuel can flow is formed at the bottom.
  • the spring holder B205 is inserted into the relief valve housing B206 and is press-fitted and fixed.
  • the relief spring B204 is supported at one end by a relief valve pressing guide B208 and at the other end by a relief valve pressing B203. Further, the set load of the relief spring B204 is determined by the fixing position of the spring holder B205.
  • the valve opening pressure of the relief valve B202 is determined by the set load of the relief spring B204.
  • the subassembly relief valve B200 thus formed is press-fitted and fixed to the pump housing 1.
  • the pressure overshoot generated in the pressurizing chamber 11 propagates from the discharge passage 12 to the relief passage 210 and the relief passage 211, passes through the relief passage port B207, and reaches the relief valve B202.
  • the relief valve B202 leaves the relief valve seat B201, and the high pressure relief passage 211 and the low pressure suction passage 10b are in communication.
  • the fuel that has passed between the relief valve B202 and the relief valve seat B201 flows through the relief passage 206a opened in the relief valve housing B206 to the suction passage 10b that is the low pressure portion.
  • a fuel chamber B211 filled with fuel is formed.
  • the fuel chamber B211 is connected to the low pressure side only by a minute clearance B210 that is a minute gap.
  • the minute clearance B210 is formed between the outer peripheral surface of the relief valve presser B203 and the inner peripheral surface of the relief valve presser guide B208.
  • the outer peripheral surface of the relief valve presser B203 and the inner peripheral surface of the relief valve presser guide B208 are slidably supported.
  • the minute clearance B210 is set to such an extent that it has a small cross-sectional area and has an effect as an orifice.
  • the relief valve B202 When the pressure of the high-pressure fuel pushing the relief valve B202 overcomes the urging force of the relief spring B204, the relief valve B202 is separated from the relief valve seat B201, and the relief valve mechanism B200 is opened.
  • the relief valve presser B203 moves upward in the drawing.
  • the fuel receives a pressure toward the upper side of the figure, and the pressure acts on the back pressure valve B209 through the hole B214.
  • a fluid force (pressure) that is moved upward in the drawing acts on the back pressure valve B209, and is seated (closed) on a back pressure valve seat B212 formed on the fuel chamber B211 side of the spring holder B205.
  • the fuel chamber B211 has a function as a check valve that blocks the movement of fuel from the fuel chamber B211 to the low pressure side, in addition to the minute clearance B210.
  • the amount of fuel moving between the fuel chamber B211 and the low pressure side can be limited by the minute clearance B210, and the rate of volume change of the fuel chamber B211 can be limited.
  • the minute clearance B210 is large, the volume change speed of the fuel chamber B211 is slow, and when the minute clearance B210 is small, the volume change speed of the fuel chamber is fast. That is, the movement speed of the relief valve B202 is determined by adjusting the cross-sectional area of the minute clearance B210.
  • the movement speed of the relief valve B202 is more limited as the cross-sectional area is smaller.
  • the volume in the fuel chamber B211 decreases and the pressure in the fuel chamber B211 increases with the movement of the relief valve B202.
  • a force acting in the direction opposite to the opening direction is generated in the relief valve B202 and the relief valve presser B203, so that the movement speed of the relief valve B202 is limited.
  • the valve opening operation speed is limited.
  • the amount of high-pressure fuel that leaks from the high-pressure side to the low-pressure side can be reduced, and a high-pressure fuel supply pump that is less energy-efficient and less energy-efficient can be obtained.
  • the relief valve B202 moves in the direction in which the relief valve B202 is seated on the relief valve seat B202 side. Accordingly, the volume of the fuel chamber B211 increases, and the spring holder passage B205a and the back pressure valve that is a check valve.
  • the valve closing operation speed of the relief valve B202 is increased.
  • the relief valve B202 can be seated (closed) earlier by the relief valve seat B201, so that the amount of high-pressure fuel that leaks from the high-pressure side to the low-pressure side can be reduced, and high-pressure fuel supply that is energy efficient.
  • a pump can be obtained.
  • the high-pressure fuel that leaks from the relief valve B202 to the suction passage 10b is limited. The reduction of the high-pressure fuel discharged to the fuel is suppressed, and the energy efficiency as the high-pressure fuel supply pump is improved.
  • the relief operation in the first embodiment will be described.
  • the abnormally high pressure generated in the high-pressure pipe passes through the relief passage 210 and the relief passage port B207 and reaches the relief valve B202.
  • the relief valve B202 leaves the valve seat B201, and the high-pressure side relief passage 211 and the low-pressure side suction passage 10b are in communication.
  • the fuel that has passed through the relief valve B202 leaks through the relief passage 206a opened in the relief valve housing B206 to the suction passage 10b that is the low pressure portion.
  • the relief valve B202 leaves the relief valve seat B201 and starts to open, the volume in the fuel chamber B211 decreases and the pressure in the fuel chamber B211 increases with the movement of the relief valve B202. .
  • a force acting in the direction opposite to the opening direction is generated in the relief valve B202 and the relief valve presser B203, so that the movement speed of the relief valve B202 is limited.
  • the fuel chamber B211 has a minute clearance B210 and the minute clearance B211 is connected to the low pressure side, the compressed fuel in the fuel chamber B211 passes through the minute clearance B211 as time passes. Released. As a result, the force in the direction opposite to the operation direction for opening the valve acting on the relief valve B202 and the relief valve presser B203 is attenuated. Therefore, the restriction on the opening operation of the relief valve B202 is released, and the relief valve B202 can secure a lift amount sufficient to sufficiently open the abnormal high pressure, so that the abnormal high pressure in the high pressure pipe is attenuated, The high-pressure fuel system such as the common rail 23 is protected.
  • the sectional area of the spring holder passage B205a provided in the spring holder B205 is small, for example, the hole diameter is about 50 ⁇ m in diameter. That is, the hole diameter is reduced to such an extent that the spring holder passage B205a has an effect as an orifice.
  • the relief valve presser B203 moves upward in the drawing as the relief valve B202 opens. Therefore, in the fuel chamber B211, the fuel flows through the spring holder passage B205a as the fuel moves upward in the drawing. Therefore, the pressure difference increases due to the orifice effect at the inlet and outlet of the spring holder passage B205a, so that the movement of fuel from the fuel chamber B211 to the low pressure side is restricted. That is, the same effect as that of the check valve can be obtained.
  • the pressure loss can be adjusted by the cross-sectional area of the spring holder passage B205a.
  • the volume in the fuel chamber B211 decreases with the movement of the relief valve B202.
  • the pressure in the chamber B211 increases.
  • a force acting in the direction opposite to the opening direction is generated in the relief valve B202 and the relief valve presser B203, so that the movement speed of the relief valve B202 is limited.
  • the valve B209 in the first embodiment is not required, the number of parts can be reduced, and the cost can be reduced.
  • the valve seat B212 is also unnecessary, it is not necessary to perform sheet processing that requires finishing accuracy.
  • the orifice passage only the hole diameter needs to be adjusted, so that processing becomes very easy, the overall length of the relief valve can be shortened, and the degree of freedom in layout increases.
  • the relief spring B204 is arranged outside the space of the fuel chamber B211. All the symbols and numbers described are the same as those in the first embodiment.
  • the relief spring B204 is disposed outside the fuel chamber B211, and the relief spring B204 is supported by the relief valve pressing guide B208 at one end and supported by the spring holder B205 at the other end.
  • the set load of the relief spring B204 is determined by the fixing position of the spring holder B205. That is, the valve opening pressure of the relief valve B202 is determined by the set load of the relief spring B204.
  • the sub-assembly relief valve B200 thus formed is press-fitted and fixed to the pump housing 1.
  • the set valve opening pressure when the set valve opening pressure is set to a higher value in order to further increase the pressure, it is necessary to increase the set load of the relief spring B204, which inevitably increases the wire diameter and the total length, and increases the relief spring B204. It must be converted. That is, the space volume in the fuel chamber B211 is increased, and the rate of volume reduction in the fuel chamber B211 accompanying the movement of the relief valve B202 is reduced. That is, the effect of limiting the valve opening operation speed of the relief valve B202 is reduced. Therefore, as shown in the embodiment of FIG. 9, by adopting a configuration in which the relief spring B204 is disposed outside the fuel chamber B211, the volume of the fuel chamber B211 is increased even when the relief spring B204 is enlarged. There is no need. In addition, since the volume of the fuel chamber B211 can be further reduced, the speed of volume change in the fuel chamber B211 can be increased, so that the valve opening operation speed of the relief valve B202 can be further limited. Become.
  • the present invention is applied to a high-pressure fuel supply pump used in a cylinder injection type internal combustion engine.
  • a so-called single-cylinder high-pressure fuel supply pump having only one pressurizing chamber has been described, but it can be used for a so-called multi-cylinder pump having a plurality of pressurizing chambers.
  • suction passage 10A1 ... support member, 10A2 ... support member, 10A3 ... outer periphery, 11 ... pressurizing chamber, 11A ... recess, 12 DESCRIPTION OF SYMBOLS ... Fuel outlet, 13 ... Plunger seal, 14 ... Damper cover, 15 ... Retainer, 20 ... Fuel tank, 21 ... Feed pump, 23 ... Common rail, 24 ... Injector, 26 ... Pressure sensor, 27 ... ECU, 28 ... Suction Pipe, 30 ... Electromagnetic suction valve mechanism, 30a ... Suction port, 30b ... Electromagnetic coil, 30c ... Electromagnetic plunger, 30A ... Hole, 31 ... Suction valve, 32 ...

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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)

Abstract

Le problème décrit par la présente invention est que lorsqu'un moteur exige davantage de carburant du fait d'une rotation élevée pendant une conduite normale, la pression d'ouverture de soupape d'une soupape de surpression est dépassée par une augmentation momentanée de la pression de carburant et une pulsation de pression dans un tuyau lorsque le carburant est évacué de la pompe à carburant, et ainsi, la soupape de surpression s'ouvre involontairement et du carburant fuit du côté haute pression du conduit d'évacuation vers le côté basse pression du conduit d'admission. Pour cette raison, il y a un problème en ce que la quantité de carburant haute pression évacuée vers la rampe commune depuis la pompe d'alimentation en carburant haute pression est réduite. La solution selon l'invention consiste en une pompe à carburant haute pression, qui met sous pression le carburant aspiré dans une chambre de mise sous pression et évacue le carburant sous pression en ouvrant une soupape d'échappement, caractérisée en ce qu'elle est équipée d'un conduit de surpression reliant le côté en amont et le côté en aval de la soupape d'échappement, le conduit de surpression ayant un mécanisme de soupape de surpression qui possède un clapet antiretour qui arrête l'écoulement de carburant allant du côté en aval au côté en amont de la soupape d'échappement, et le mécanisme de soupape de surpression étant équipé d'une soupape de surpression, d'un siège de soupape, d'un ressort qui sollicite la soupape de surpression en direction du siège de soupape, et d'un mécanisme d'amortisseur qui limite l'opération d'ouverture de la soupape de surpression.
PCT/JP2013/078893 2012-11-29 2013-10-25 Pompe d'alimentation en carburant à haute pression WO2014083979A1 (fr)

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JP2012260464A JP2014105669A (ja) 2012-11-29 2012-11-29 高圧燃料供給ポンプ

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Cited By (3)

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WO2017175539A1 (fr) * 2016-04-06 2017-10-12 日立オートモティブシステムズ株式会社 Pompe d'alimentation en carburant haute pression
JP2017198155A (ja) * 2016-04-28 2017-11-02 株式会社デンソー 高圧ポンプ
EP3296558A4 (fr) * 2015-05-12 2018-12-19 Hitachi Automotive Systems, Ltd. Pompe à carburant à haute pression

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JP2017008806A (ja) * 2015-06-22 2017-01-12 株式会社デンソー 高圧ポンプ
JP2017101622A (ja) * 2015-12-03 2017-06-08 株式会社デンソー リリーフ弁装置、及び、それを用いる高圧ポンプ

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EP3296558A4 (fr) * 2015-05-12 2018-12-19 Hitachi Automotive Systems, Ltd. Pompe à carburant à haute pression
US10253741B2 (en) 2015-05-12 2019-04-09 Hitachi Automotive Systems, Ltd High-pressure fuel pump
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US20190128229A1 (en) * 2016-04-06 2019-05-02 Hitachi Automotive Systems, Ltd. High-Pressure Fuel Supply Pump
US10788003B2 (en) 2016-04-06 2020-09-29 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump
CN109072845B (zh) * 2016-04-06 2021-07-30 日立汽车系统株式会社 高压燃料供给泵
JP2017198155A (ja) * 2016-04-28 2017-11-02 株式会社デンソー 高圧ポンプ
WO2017187876A1 (fr) * 2016-04-28 2017-11-02 株式会社デンソー Pompe à haute pression

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