EP3135899B1 - Hochdruckbrennstoffpumpe - Google Patents

Hochdruckbrennstoffpumpe Download PDF

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Publication number
EP3135899B1
EP3135899B1 EP15782715.5A EP15782715A EP3135899B1 EP 3135899 B1 EP3135899 B1 EP 3135899B1 EP 15782715 A EP15782715 A EP 15782715A EP 3135899 B1 EP3135899 B1 EP 3135899B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
pressure
fuel
pump body
plunger
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP15782715.5A
Other languages
English (en)
French (fr)
Other versions
EP3135899A4 (de
EP3135899A1 (de
Inventor
Masayuki Suganami
Hiroyuki Yamada
Satoshi Usui
Kenichirou TOKUO
Atsuji Saito
Masamichi Yagai
Yuta SASO
Masayuki Kobayashi
Kenichi Gunji
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Astemo Ltd
Original Assignee
Hitachi Automotive Systems Ltd
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 Hitachi Automotive Systems Ltd filed Critical Hitachi Automotive Systems Ltd
Publication of EP3135899A1 publication Critical patent/EP3135899A1/de
Publication of EP3135899A4 publication Critical patent/EP3135899A4/de
Application granted granted Critical
Publication of EP3135899B1 publication Critical patent/EP3135899B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0421—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/48—Assembling; Disassembling; Replacing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8053—Fuel injection apparatus manufacture, repair or assembly involving mechanical deformation of the apparatus or parts thereof
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8061—Fuel injection apparatus manufacture, repair or assembly involving press-fit, i.e. interference or friction fit

Definitions

  • the present invention relates to the structure of a cylinder of a high-pressure fuel supply pump for an internal-combustion engine of a vehicle.
  • High-pressure fuel supply pumps that increase the pressure of the fuel are widely used for direct-injection internal-combustion engines in which the fuel is directly injected to the inside of the combustion chamber among internal-combustion engines, for example, of vehicles.
  • JP 5178676 B2 describes a high-pressure fuel supply pump having a structure in which the outer periphery of a cylinder is held by a cylindrical fitting part of a cylinder holder, a screw thread put around the outer periphery of the cylinder holder is screwed in a thread put around the pump body so that an end surface of the cylinder is adhered to the pump body and the other end surface of the cylinder is adhered to the pump body, and the cylinder is fixed to the pump body (see PTL 1).
  • PTL 2 relates to a high pressure pump, in which a cylinder is configured into a bottomed tubular form and includes an inner peripheral wall, an inner bottom wall, an outer peripheral wall, an intake hole, and a discharge hole.
  • US2012195780 A1 discloses another high-pressure fuel supply pump.
  • the cylinder is screwed and fastened to the pump body through the cylinder A holder.
  • the screw thread needs to have the tightening axial torque that withstands the fuel pressure required for the internal-combustion engine.
  • the production cost is increased.
  • the restrictions on attachment of the pump body to the internal-combustion engine are increased. These may decrease the marketability of the pump.
  • An objective of the invention is to provide a high-pressure fuel supply pump in which the cylinder can be fixed to the pump body with a simple structure even when the fuel pressure is high. As a result, the size and cost of the pump body can be reduced.
  • the objective of the present invention can be achieved by a structure in which the cylinder is formed in a cylindrical shape with a bottom, and the cylinder includes a large-diameter part and a small-diameter part so that the surface of the width difference formed between the large-diameter part and the small-diameter part is press-fitted to the pump body in the pressurizing direction in which the plunger is pressurized.
  • the width difference formed between the large-diameter part and small-diameter part of the cylinder is more strongly pressed in a direction in which the surface of the width difference is press-fitted to the pump body in a pressurizing process in which the maximum force acts on the cylinder.
  • the cylinder drops from the pump body due to the pressurizing force.
  • less fixing force is required in order to fix the cylinder to the pump body.
  • the cylinder can be fixed to the pump body with a simply structure. As a result, the size and cost of the pump body can be reduced.
  • a part surrounded by a dashed line is the body of a high-pressure fuel supply pump (hereinafter, referred to as a high-pressure pump) .
  • the mechanism and parts in the dashed line are integrally embedded in a high-pressure pump body 1.
  • the fuel in a fuel tank 20 is pumped up by a feed pump 21, and fed via an intake pipe 28 to an intake joint 10a of the pump body 1.
  • the fuel After passing through the intake joint 10a, the fuel passes through a pressure pulsation reducing mechanism 9, and an intake path 10b, and reaches an intake port 30a of an electromagnetic inlet valve 30 included in a flow rate control mechanism.
  • the pulsation preventing mechanism 9 will be described below.
  • the electromagnetic inlet valve 30 includes an electromagnetic coil 308.
  • the electromagnetic coil 308 does not conduct electricity, the difference between the biasing force of an anchor spring 303 and the biasing force of a valve spring 304 biases an inlet valve body 301 in a valve-opening direction in which the inlet valve body 301 is opened, and this opens the intake opening 30d.
  • the biasing force of the anchor spring 303 and the biasing force of the valve spring 304 are set so that the biasing force of the anchor spring 303 > the biasing force of the valve spring 304 holds.
  • the inlet valve body 301 is still opened by the biasing force of the anchor spring 303.
  • the volume of the pressurizing chamber 11 decreases with the compressing motion of the plunger 2.
  • the fuel sucked in the pressurizing chamber 11 is returned through the opened inlet valve body 301 to the intake path 10b (the intake port 30a).
  • the pressure in the pressurizing chamber is not increased. This process is referred to as a return process.
  • ECU engine control unit 27
  • a current flows through the electromagnetic coil 308 of the electromagnetic inlet valve 30.
  • the magnetic biasing force moves the electromagnetic plunger 305 to the left side of FIG. 4 and a state in which the anchor spring 303 is compressed is maintained.
  • the biasing force of the anchor spring 303 does not act on the inlet valve body 301.
  • the fluid force due to the biasing force of the valve spring 304 and the flow of the fuel into the intake path 10b (the intake port 30a) acts. This closes the inlet valve 301 and thus closes the intake opening 30d.
  • the compression process of the plunger 2 includes the return process and the discharge process.
  • Controlling the timing at which the electromagnetic coil 308 of the electromagnetic inlet valve 30 conducts electricity can control the amount of the high-pressure fuel to be discharged.
  • the timing at which the electromagnetic coil 308 conducts electricity is hastened, the proportion of the return process is low and the proportion of the discharge process is high to the compression process.
  • the amount of fuel to be returned to the intake path 10b (the intake port 30a) is decreased and the amount of fuel to be discharged at high pressure is increased.
  • the proportion of the return process is high and the proportion of the discharge process is low to the compression process. In other words, the amount of fuel to be returned to the intake path 10b is increased and the amount of fuel to be discharged at high pressure is decreased.
  • the timing at which the electromagnetic coil 308 conducts electricity is controlled by the instructions from the ECU.
  • the configuration described above controls the timing at which the electromagnetic coil 308 conducts electricity. This can control the amount of fuel to be discharged at high pressure in accordance with the amount of fuel that the internal-combustion engine requires.
  • the outlet of the pressurizing chamber 11 is provided with a discharge valve mechanism 8.
  • the discharge valve mechanism 8 includes a discharge valve seat 8a, a discharge valve 8b, and a discharge valve spring 8c.
  • the discharge valve 8b When there is no fuel differential pressure between the pressurizing chamber 11 and the fuel discharge outlet 12, the discharge valve 8b is pressed and fixed to the discharge valve seat 8a and closed by the biasing force of the discharge valve spring 8c.
  • the discharge valve 8b is opened against the discharge valve spring 8c and the fuel in the pressurizing chamber 11 is discharged at high pressure through the fuel discharge outlet 12 to the common rail 23.
  • the fuel guided to the intake joint 10a is pressurized at high pressure by the reciprocation of the plunger 2 in the pressurizing chamber 11 of the pump body 1 as much as necessary, and fed from the fuel discharge outlet 12 to the common rail 23 by the pressure.
  • Injectors 24 for direct injection namely, a direct-injection injectors
  • a pressure sensor 26 are attached to the common rail 23.
  • the number of the attached direct-injection injectors 24 corresponds to the number of cylinder engines of the internal-combustion engine.
  • the direct-injection injectors 24 open and close in accordance with the control signal from the engine control unit (ECU) 27 so as to inject the fuel in the cylinder.
  • ECU engine control unit
  • the pump body 1 is further provided with a discharge flow path 110 communicating the downstream part of the discharge valve 8b with the pressurizing chamber 11 and bypassing the discharge valve, separately from the discharge flow path.
  • the discharge flow path 110 is provided with a pressure relief valve 102 that limits the flow of the fuel only to a direction from the discharge flow path to the pressurizing chamber 11.
  • the pressure relief valve 102 is pressed to the pressure relief valve seat 101 by the relief spring 104 that generates pressing force.
  • the pressure relief valve 102 moves away from the pressure relief valve seat 101 and opens.
  • the pressure relief valve 102 opens and the discharge flow path at the excessive high pressure is returned from the discharge flow path 110 to the pressurizing chamber 11. This protects a high-pressure pipe such as the common rail 23.
  • FIG. 1 is a vertical cross-sectional view of the whole of a high-pressure fuel supply pump in which the present invention is implemented, and is a cross-sectional view taken along the axis of a discharge joint.
  • FIG. 2 is a vertical cross-sectional view, viewed from an angle different from FIG. 1 , and a cross-sectional view taken along the axis of an intake joint.
  • FIG. 3 is a horizontal cross-sectional view, and a cross-sectional view taken along the axis of a fuel discharge outlet.
  • FIG. 4 illustrates the whole configuration of a fuel supply system.
  • a general high-pressure pump is air-tightly sealed and fixed to the flat surface of a cylinder head 41 of the internal-combustion engine with a flange 1e provided to the pump body 1.
  • An O-ring 61 is fitted to the pump body 1 so that the airtightness between the cylinder head and the pump body is retained.
  • a cylinder 6 is attached to the pump body 1.
  • the cylinder 6 is formed in a cylinder with a bottom on an end so that the cylinder 6 guides the back-and-forth movement of the plunger 2 and the pressurizing chamber 11 is formed in the cylinder 6.
  • the pressurizing chamber 11 is provided with a plurality of communication holes 11a so that the pressurizing chamber 11 communicates with the electromagnetic inlet valve 30 configured to feed the fuel and the discharge valve mechanism 8 configured to discharge the fuel from the pressurizing chamber 11 to the discharge path.
  • the lower end of the plunger 2 is provided with a tappet 3 that converts the rotation movement of a cam 5 attached to a camshaft of the internal-combustion engine into up-and-down movement, and transmits the up-and-down movement to the plunger 2.
  • the plunger 2 is pressed and fixed to the tappet 3 through a retainer 15 with a spring 4. This can move (reciprocate) the plunger 2 up and down with the rotation movement of the cam 5.
  • a plunger seal 13 held on the lower end of the inner periphery of the seal holder 7 has slidably contact with the outer periphery of the plunger 2 on the lower end of the cylinder 6 in the drawing. This seals the blow-by gap between the plunger 2 and the cylinder 6 and prevents the fuel from leaking to the outside of the pump. Meanwhile, this prevents the lubricant (including engine oil) that smoothly moves a sliding part of the internal-combustion engine from leaking through the blow-by gap into the pump body 1.
  • the fuel sucked by the feed pump 21 is fed through the intake joint 10a coupled with the intake pipe 28 to the pump body 1.
  • a damper cover 14 is coupled with the pump body 1 and forms a low-pressure fuel chamber 10.
  • the fuel passing through the inlet joint 10a flows into the low-pressure fuel chamber 10.
  • a fuel filter 102 is attached to the upstream part of the low-pressure fuel chamber 10, for example, while being pressed and inserted in the pump body 1.
  • a pressure pulsation reducing mechanism 9 is installed in the low-pressure fuel chamber 10 so that the pressure pulsation reducing mechanism 9 reduces the spread of the pressure pulsation generated in the high-pressure pump to a fuel pipe 28.
  • the fuel sucked in the pressurizing chamber 11 is returned through the opened inlet valve body 301 to the intake path 10b (the intake port 30a) under a state in which the flow rate of the fuel is controlled, the fuel returned to the intake path 10b (the intake port 30a) generates the pressure pulsation in the low-pressure fuel chamber 10.
  • the pressure pulsation is absorbed and reduced by the expansion and contraction of a metal damper 9a forming the pressure pulsation reducing mechanism 9 provided to the low-pressure fuel chamber 10.
  • the metal damper 9a is formed of two corrugated metal disks of which outer peripheries are bonded together. Inert gas such as argon is injected in the metal damper 9a.
  • Mounting hardware 9b is configured to fix the metal damper 9a on the inner periphery of the pump body 1.
  • the electromagnetic inlet valve 30 is a variable control mechanism that includes the electromagnetic coil 308.
  • the electromagnetic inlet valve 30 is connected to the ECU through the terminal 307 and repeats conduction and non-conduction of electricity so as to open and close the inlet valve and control the flow rate of the fuel.
  • the biasing force of the anchor spring 303 is transmitted to the inlet valve body 301 through the anchor 305 and the anchor rod 302 integrally formed with the anchor 305.
  • the biasing force of the valve spring 304 installed in the inlet valve body is set so that the biasing force of the anchor spring 303 > the biasing force of the valve spring 304 holds.
  • the inlet valve body 301 is biased in a valve-opening direction in which the inlet valve body 301 is opened.
  • the intake opening 30d is opened.
  • the anchor rod 302 has contact with the inlet valve body 301 at a part 302b (in a state illustrated FIG. 1 ).
  • the setting for the magnetic biasing force generated by the electricity conduction through the coil 308 is configured to enable the anchor 305 to overcome the biasing force of the anchor spring 303 and be sucked into a stator 306.
  • the anchor 303 moves toward the stator 306 (the left side of the drawing) and a stopper 302a formed on an end of the anchor rod 302 has contact with an anchor rod bearing 309 and is seized.
  • the clearance is set so that the travel distance of the anchor 301 > the travel distance of the inlet valve body 301 holds.
  • the contact part 302b opens between the anchor rod 302 and the inlet valve body 301. As a result, the inlet valve body 301 is biased by the valve spring 304 and the intake opening 30d is closed.
  • the electromagnetic inlet valve 30 is fixed to the pump body 1 while an inlet valve seat 310 is hermetically inserted in a tubular boss 1b so that the inlet valve body 301 can seal the intake opening 30d to the pressurizing chamber.
  • the intake port 30a is connected to the intake path 10b.
  • the discharge valve mechanism 8 is provided with a plurality of discharge paths radially drilled around the sliding axis of the discharge valve body 8b.
  • the discharge valve mechanism 8 includes a discharge valve seat member 8a and a discharge valve member 8b.
  • the discharge valve seat member 8a is provided with a bearing that can sustain the sliding reciprocation of the discharge valve body 8b at the center of the discharge valve seat member 8a.
  • the discharge valve member 8b has the central axis so as to slide with respect to the bearing of the discharge valve seat member 8a, and has a circular contact surface on the outer periphery. The circular contact surface can retain the airtightness by having contact with the discharge valve seat member 8a.
  • a discharge valve spring 33 is inserted and held in the discharge valve mechanism 8.
  • the discharge valve spring 33 is a coil spring that biases the discharge valve member 8b in a valve-closing direction in which the discharge valve member 8b is closed.
  • the discharge valve seat member for example, is pressed, inserted and held in the pump body 1.
  • the discharge valve member 8b and the discharge valve spring 33 are further inserted in the pump body 1.
  • a sealing plug 17 seals the pump body 1.
  • the discharge valve mechanism 8 is formed as described above. The formation causes the discharge valve mechanism 8 to function as a check valve that controls the direction in which the fuel flows.
  • a pressure relief valve mechanism 100 includes a pressure relief valve stopper 101, a pressure relief valve 102, a relief seat 103, a relief spring stopper 104, and a relief spring 105 as illustrated.
  • the pressure relief valve seat 103 includes a bearing that enables the pressure relief valve 102 to slide.
  • the pressure relief valve 102 integrally including a sliding shaft is inserted in the pressure relief valve seat 103. After that the position of the relief spring stopper 104 is determined so that the relief spring 105 has a desired load, and the relief spring stopper 104 is fixed to the pressure relief valve 102, for example, by press-insertion.
  • the valve-opening pressure at which the pressure relief valve 102 is opened is determined depending on the pressing force of the relief spring 104.
  • the pressure relief valve stopper 101 is inserted between the pump body 1 and the pressure relief valve seat 103 so as to function as a stopper that controls how much the pressure relief valve 102 is opened.
  • the pressure relief valve mechanism 100 unitized as described above is fixed to the pump body 1 by the press-insertion of the pressure relief valve seat 103 to the inner peripheral wall of a cylindrical pass-through slot 1C provided to the pump body 1. Subsequently, the fuel discharge outlet 12 is fixed so that the fuel discharge outlet 12 blocks the cylindrical pass-through slot 1C of the pump body 1. This prevents the fuel from leaking from the high-pressure pump to the outside and to enable the pressure relief valve mechanism 100 to be connected to a common rail.
  • the relief spring 105 is provided to a side of the pressure relief valve 102 facing the fuel discharge outlet 12 as described above. This prevents the volume of the pressurizing chamber 11 from increasing even when the outlet of the pressure relief valve 102 of the pressure relief valve mechanism 100 is opened to the pressurizing chamber 11.
  • the pressure in the pressurizing chamber increases with the decrease in volume.
  • the discharge valve mechanism 8 is opened and the fuel is discharged from the pressurizing chamber 11 to the discharge flow path 110. From the moment the discharge valve mechanism 8 is opened to the time immediately after the opening, the pressure in the pressurizing chamber overshoots and becomes very high. The very high pressure propagates in the discharge flow path and the pressure in the discharge flow path simultaneously overshoots.
  • the overshoot of the pressure in the discharge flow path causes the pressure difference between the inlet and outlet of the pressure relief valve 102 to exceed the valve-opining pressure at which the pressure relief valve mechanism 100 is opened. This causes an error in the pressure relief valve.
  • the outlet of the pressure relief valve mechanism 100 of the embodiment is connected to the pressurizing chamber 11, and thus the pressure in the pressurizing chamber acts on the outlet of the pressure relief valve mechanism 100 and the pressure in the discharge flow path 110 acts on the inlet of the pressure relief valve mechanism 11.
  • the pressure overshoot occurs simultaneously in the pressurizing chamber and the discharge flow path.
  • the pressures difference between the inlet and outlet of the pressure relief valve does not exceed the valve-opining pressure at which the pressure relief valve is opened. In other words, an error in the pressure relief valve does not occur.
  • the direct-injection injector In the event of failure of the direct-injection injector, in other words, when the injection function of the direct-injection injector stops and the direct-injection injector does not feed the fuel fed in the common rail 23 into the combustion chamber of the internal-combustion engine, the fuel accumulates between the discharge valve mechanism 8 and the common rail 23. This causes an excessive high pressure of the fuel. When the fuel pressure moderately increases to the excessive high pressure, the pressure sensor 26 provided to the common rail 23 detects the abnormal pressure. Then, the electromagnetic inlet valve 30 that is a flow rate control mechanism provided in the intake path the intake path 10b (the intake port 30a) is controlled by feedback control. The feedback control operates as a safety function to decrease the amount of the fuel to be discharged.
  • the feedback control with the pressure sensor is not effective in dealing with an instantaneous excessive high pressure.
  • the electromagnetic inlet valve 30 is out of order and keeps the maximum flow rate in an operation state in which the fuel is not required so much, the pressure at which the fuel is discharged excessively increases. In such a case, the excessive high pressure is not dissolved because of the failure of the flow rate control mechanism even when the pressure sensor 26 of the common rail 23 detects the excessive high pressure.
  • the pressure relief valve mechanism 100 of the embodiment functions as a safety valve.
  • the pressure in the pressurizing chamber decreases with the increase in volume.
  • the pressure in the inlet of the pressure relief valve mechanism 100 namely, in the discharge flow path is higher than or equal to the pressure in the outlet of the pressure relief valve, namely, in the pressurizing chamber 11 by the valve-opening pressure at which the pressure relief valve mechanism 100 is opened
  • the pressure relief valve mechanism 100 is opened and returns the fuel at an excessive high pressure in the common rail to the pressurizing chamber. This return prevents the fuel pressure from being higher than or equal to a predetermined pressure even when an excessive high pressure occurs. This prevention protects the high-pressure pipe system including the common rail 23.
  • a cylinder 6 includes a large-diameter part 6b and a small-diameter part 6c on the outer diameter of the cylinder 6.
  • the small-diameter part is pressed and inserted into the pump body 1 so that the circumferential surface pressure acting on the small-diameter part maintains the pressure in the intake path 10b and the pressurizing chamber 11a.
  • the pressure in the intake path 10b is a lower fuel pressure fed to the high-pressure pump by a feed pump, and is about 0.4 MPa.
  • the pressure generated in the pressurizing chamber 11 is a pressure pressurized by the high-pressure pump and the instantaneous pressure reaches about 30 to 50 MPa.
  • the pressurized fuel is fed from the pressurizing chamber 11 through a plurality of communication holes 11a drilled in a side of the cylinder and through the discharge valve mechanism 8 and the fuel discharge outlet 12 to the common rail 23.
  • the setting for the press fit allowance of the small-diameter part is configured to prevent the fuel from leaking to the intake path 10b due to the pressure pressurizing the fuel.
  • the void between the large-diameter part 6b and the inner diameter of the pump body 1 is zero, the cylinder only needs to be slightly pressed and inserted into the pump body.
  • the fuel is pressurized in the pressurizing chamber 11 and the pressure pressuring the fuel acts on the bottom surface of the inner diameter of the cylinder 6.
  • the surface of the width difference 6a between the large-diameter part 6b and the small-diameter part 6c is press-fitted to the pump body 1, and seals the pressurizing chamber 11 so as to prevent the pressurized fuel from leaking to the space formed between the seal holder 7 and the lower end of the cylinder (hereinafter, referred to as an auxiliary pressurizing chamber).
  • the auxiliary pressurizing chamber communicates with the intake path 10b and the pressure in the auxiliary pressurizing chamber is equal to the value of the lower fuel pressure.
  • the fuel pressure generated in the compression process of the plunger 2 acts on the press-fitted surface.
  • the bottom of the cylinder 6 receives the pressure pressuring the fuel and the pressure acts in a direction in which the press-fitted surface is more tightly adhered and the leakage of fuel is prevented.
  • the structure in which the cylinder 6 does not drop from the pump body 1 in the compression process in which the maximum pressure acts on the high-pressure pump among the operation processes is important to ensure the high quality of the high-pressure pump.
  • the cylinder 6 receives the pressure to adhere the cylinder 6 to the pump body 1 in the compression process. This is also advantageous for preventing the cylinder 6 from dropping from the pump body 1.
  • the lower fuel pressure in the intake path 10b acts on the cylinder 6 so as to disconnect the cylinder 6 from the pump body 1.
  • the lower pressure is about 0.4 MPa.
  • the disconnecting force acting on the cylinder 6 is about 53 N. The value of the disconnecting force is small enough to hold the cylinder 6 with the press-inserting force between the small-diameter part 6c and the pump body 1.
  • a seal part will be described in detail with reference to FIGS. 5 and 6 .
  • FIG. 5 is an enlarged view of a part including a circular protrusion.
  • FIG. 6 illustrates another exemplary variation of the part including a circular protrusion.
  • the width difference 6a between the large-diameter part 6b and small-diameter part 6c of the cylinder 6 is provided with a circular protrusion 6d with a triangular cross-sectional surface.
  • the circular protrusion 6d comes into contact with the pump body 1 first in the width difference 6a and this contact locally increases the surface pressure.
  • the material of the cylinder 6 has hardness higher than or equal to the hardness of the material of the pump body 1 in order to support the reciprocation of the plunger 2. This causes earlier plastic deformation of the pump body 1 than the cylinder 6.
  • the circular protrusion 6d is engaged in the pump body 1. This engagement can further increase the sealing function of the width difference 6a.
  • the circular protrusion 6d can be formed into a shape that does not protrude from the flat surface of the width difference 6a as illustrated in FIG. 6 .
  • the width difference 6a comes into contact with the pump body 1 first.
  • the surface of the pump body having contact with the width difference 6a is slightly plastic deformed.
  • the circular protrusion 6d is engaged in the pump body and this engagement locally increases the surface pressure and enhances the sealing function.
  • the protrusion on the cylinder 6 does not protrude from the surface of the width difference 6a before the high-pressure pump is assembled.
  • this makes it unnecessary to pay attention to breakage of the protrusion and thus makes it easy to handle the cylinder 6.
  • the cross-sectional surface of the circular protrusion 6d has a triangular shape.
  • a convex shape or a curved surface can have the same effect.
  • the circular protrusion can similarly be formed on the pump body 1. This can also achieve the objective.
  • a ring 16 will be described in detail with reference to FIGS. 7 and 8(a) to 8(c) .
  • FIG. 7 is a vertical cross-sectional view of the whole of the high-pressure pump to which the cylinder is fixed with the ring 16.
  • FIG. 7 in order to add a pre-charge pressure to the press-fitted surface 6a of the cylinder 6, an end surface of the large-diameter part 6b of the cylinder is pressed to the pump body with the ring 16.
  • the ring 16 is fixed to the pump body 1 by press-insertion or, for example, with a metal flow part (plastic flow combination) 1d illustrated in FIG. 8(a) , or with a swaged part 1f illustrated in FIG. 8(b) .
  • the ring 16 is previously pressurized and installed in the pump body 1. Then, the ring 16 is fixed to the pump body 1 by swaging or metal flow.
  • a spring member 18 can be attached to an end surface of the large-diameter part of the cylinder in order to add a pre-charge pressure to the width difference 6a of the cylinder 6.
  • FIGS. 8 (a) to 8 (c) illustrate embodiments in which a ring is used to fix the cylinder to the pump body.
  • a void 17 is provided between the large-diameter part 6b of the cylinder 6 and the pump body 1.
  • the press-insertion of the small-diameter part 6C in the pump body 1 and press-fitting of the press-fitted surface 6a to the pump body 1 allows the pump body 1 to hold the cylinder 6.
  • the void provided between the outer diameter part 6b of the cylinder and the pump body 1 does not adversely affect the holding of the cylinder at all.
  • the void between the outer diameter of the plunger 2 and the inner diameter of the cylinder 6 greatly affects the pump pressurizing performance.
  • the inner diameter of the cylinder is slightly deformed in a direction in which the cylinder contracts.
  • the press fit allowance is 10 to 20 ⁇ m
  • the cylinder contracts by about 1 to 2 ⁇ m.
  • the amount of deformation is one tenth of the press fit allowance.
  • the void between the outer diameter of the plunger 2 and the inner diameter of the cylinder 6 is 5 to 10 ⁇ m.
  • the contraction may cause the plunger to be burned and seized during the operation of the high-pressure pump.
  • a process for correcting the inner diameter of the cylinder is required after the cylinder 6 is pressed and inserted into the pump body.
  • the void between the outer diameter of the plunger 2 and the inner diameter of the cylinder 6 exists between the width difference 6a of the large-diameter part of the cylinder and the end surface of the cylinder protruding toward the auxiliary pressurizing chamber.
  • the void 17 is provided between the large-diameter part 6b of the cylinder and the pump body 1.
  • the embodiment is a high-pressure fuel pump that includes: a plunger that reciprocates; a cylinder including a part that guides the reciprocation of the plunger; and a pump body that holds the cylinder.
  • the cylinder is formed in a cylindrical shape with a bottom, and includes a large-diameter part and a small-diameter part. The surface of cylinder is press-fitted to the pump body in a direction in which the plunger reciprocates .
  • the embodiment is a high-pressure fuel pump that includes: a plunger that reciprocates; a cylinder including a part that guides the reciprocation of the plunger; and a pump body that holds the cylinder.
  • the cylinder is formed in a cylindrical shape with a bottom, and includes a large-diameter part and a small-diameter part.
  • the surface of cylinder is press-fitted to the pump body in a direction in which the plunger reciprocates.
  • the surface of the cylinder is a part that does not axially overlap the part that guides the reciprocation of the plunger.

Landscapes

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

Claims (6)

  1. Hochdruckkraftstoffzufuhrpumpe, die Folgendes umfasst:
    einen Kolben (2), der sich hin- und herbewegt;
    einen Zylinder (6), der einen Teil enthält, der die Hin- und Herbewegung des Kolbens (2) führt;
    eine Druckkammer (11), die im Zylinder (6) gebildet ist; und
    einen Pumpenkörper (1), der den Zylinder (6) hält, wobei
    der Zylinder (6) in einer zylindrischen Form mit einem Boden gebildet ist und einen Teil (6b) mit großem Durchmesser und einen Teil (6c) mit kleinem Durchmesser enthält, eine Oberfläche (6a) des Zylinders (6) einem Oberflächendruck ausgesetzt ist und in einer Richtung, in der der Kolben (2) sich in einem Kompressionsprozess hin- und herbewegt, zum Pumpenkörper (1) gedrückt wird, und die gedrückte Oberfläche (6a) des Zylinders (6) eine ringförmige Stufenfläche (6a) ist, die zwischen dem Teil (6b) mit großem Durchmesser und einem Zwischenteil des Zylinders (6), der einen kleineren Durchmesser als der Teil (6c) mit kleinem Durchmesser besitzt, gebildet ist, und
    die ringförmige Stufenfläche (6a) die Druckkammer (11) abdichtet, um zu verhindern, dass der mit Druck beaufschlagte Kraftstoff austritt.
  2. Hochdruckkraftstoffzufuhrpumpe nach Anspruch 1, wobei der Zylinder (6) einen kreisförmigen Vorsprung (6d) enthält und eine Oberfläche des kreisförmigen Vorsprungs (6d) zur Pumpe gedrückt wird.
  3. Hochdruckkraftstoffzufuhrpumpe nach Anspruch 1, wobei der Teil (6b) mit großem Durchmesser des Zylinders (6) mit einem verschiedenen Element (16) versehen ist, das z. B. in einer Ringform gebildet ist, um einen Vorladedruck auf die gedrückte Oberfläche (6a) des Zylinders (6) zuzugeben, und das verschiedene Element (16) am Pumpenkörper (1) durch einen Kunststoffbildungsprozess wie z. B. Verpressen oder durch Einpressen befestigt ist.
  4. Hochdruckkraftstoffzufuhrpumpe nach Anspruch 1, wobei ein Hohlraum (17) zwischen einem Außendurchmesser des Teils (6b) mit großem Durchmesser des Zylinders (6) und einem Innendurchmesser des Pumpenkörpers (1) vorgesehen ist.
  5. Hochdruckkraftstoffzufuhrpumpe nach Anspruch 1, wobei die Oberfläche (6a) des Zylinders (6) mit dem Teil, der die Hin- und Herbewegung des Kolbens (2) führt, nicht axial überlappt.
  6. Hochdruckkraftstoffzufuhrpumpe nach einem der vorhergehenden Ansprüche, wobei der Zwischenteil des Zylinders (6) eine Lücke zwischen dem Zylinder (6) und dem Pumpenkörper (1) bildet.
EP15782715.5A 2014-04-25 2015-04-17 Hochdruckbrennstoffpumpe Active EP3135899B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014090821 2014-04-25
PCT/JP2015/061774 WO2015163243A1 (ja) 2014-04-25 2015-04-17 高圧燃料供給ポンプ

Publications (3)

Publication Number Publication Date
EP3135899A1 EP3135899A1 (de) 2017-03-01
EP3135899A4 EP3135899A4 (de) 2017-12-27
EP3135899B1 true EP3135899B1 (de) 2020-10-28

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EP15782715.5A Active EP3135899B1 (de) 2014-04-25 2015-04-17 Hochdruckbrennstoffpumpe

Country Status (4)

Country Link
EP (1) EP3135899B1 (de)
JP (1) JP6268279B2 (de)
CN (1) CN106255822B (de)
WO (1) WO2015163243A1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016209726A1 (de) * 2016-06-02 2017-12-07 Robert Bosch Gmbh Hochdruckpumpe für ein Kraftstoffeinspritzsystem
CN110184734B (zh) * 2019-06-27 2024-04-05 绍兴巴鲁特智能科技有限公司 常开式机头三角气缸
JP2021110312A (ja) * 2020-01-15 2021-08-02 株式会社デンソー アッセンブリの製造方法、パーツセット、燃料噴射ポンプの製造方法、及び、燃料噴射ポンプ

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
JP3522782B2 (ja) * 1993-02-12 2004-04-26 ロバート ボッシュ ゲーエムベーハー ポンプ装置
JP3884897B2 (ja) * 2000-04-18 2007-02-21 トヨタ自動車株式会社 高圧ポンプ
EP2122168B1 (de) * 2007-01-10 2015-12-09 Stanadyne Corporation Lastenringhalterung für einen pumpstössel
JP5039507B2 (ja) * 2007-10-31 2012-10-03 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプおよびその製造方法
JP2009185613A (ja) * 2008-02-04 2009-08-20 Hitachi Ltd 高圧燃料ポンプ
JP5316969B2 (ja) * 2011-03-31 2013-10-16 株式会社デンソー 高圧ポンプ
CN102619660B (zh) * 2011-01-28 2015-06-24 株式会社电装 高压泵
DE112011105898T5 (de) * 2011-11-30 2014-08-28 Hitachi Automotive Systems, Ltd. Hochdruckkraftstoffpumpe
JP5768723B2 (ja) * 2012-01-10 2015-08-26 株式会社デンソー 高圧ポンプ

Non-Patent Citations (1)

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Title
None *

Also Published As

Publication number Publication date
WO2015163243A1 (ja) 2015-10-29
JP6268279B2 (ja) 2018-01-24
JPWO2015163243A1 (ja) 2017-04-13
CN106255822A (zh) 2016-12-21
EP3135899A4 (de) 2017-12-27
CN106255822B (zh) 2018-12-07
EP3135899A1 (de) 2017-03-01

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