WO2015163243A1 - 高圧燃料供給ポンプ - Google Patents
高圧燃料供給ポンプ Download PDFInfo
- Publication number
- WO2015163243A1 WO2015163243A1 PCT/JP2015/061774 JP2015061774W WO2015163243A1 WO 2015163243 A1 WO2015163243 A1 WO 2015163243A1 JP 2015061774 W JP2015061774 W JP 2015061774W WO 2015163243 A1 WO2015163243 A1 WO 2015163243A1
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- WIPO (PCT)
- Prior art keywords
- cylinder
- pressure
- fuel
- pump
- plunger
- Prior art date
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Classifications
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- 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
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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
- F02M59/48—Assembling; Disassembling; Replacing
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- 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
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- 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
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- 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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/80—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/80—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 a cylinder structure of a high-pressure fuel supply pump for an automobile internal combustion engine.
- a cylinder outer periphery is held by a cylindrical fitting portion of a cylinder holder, while a screw threaded on the outer periphery of the cylinder holder is a screw threaded on a pump body.
- a high-pressure fuel supply pump having a structure in which one cylinder end face is brought into close contact with the pump body and the other cylinder end face is brought into close contact with and fixed to the pump body by being screwed into the pump body is described. (See Patent Document 1).
- An object of the present invention is to provide a high-pressure fuel supply pump that can fix a cylinder to a pump body with a simple structure even at high fuel pressure, and as a result, can reduce the size and cost of the pump body.
- the object of the present invention can be achieved by making the cylinder have a bottomed cylindrical shape, a structure having a large diameter portion and a small diameter portion, and surface pressing in the compression direction of the plunger at the step formed by the large diameter portion and the small diameter portion. .
- the cylinder is pressed in a direction in which the step formed by the large diameter portion and the small diameter portion is more surface-bonded. That is, it is not necessary to consider that the cylinder falls off from the pump body due to the applied pressure, and as a result, the fixing force of the cylinder can be small. That is, the cylinder can be fixed to the pump body with a simple structure, and as a result, the pump body can be reduced in size and cost.
- 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.
- FIG. 4 is an overall longitudinal sectional view at another angle of the high-pressure fuel supply pump of the first embodiment in which the present invention is implemented, and shows a sectional view at the center of the suction joint axis.
- 1 is an overall cross-sectional view of a high-pressure fuel supply pump according to a first embodiment in which the present invention is implemented, and shows a cross-sectional view at the center of a fuel intake / discharge port shaft.
- Overall system configuration diagram The detailed shape of an annular protrusion is shown. Another embodiment of an annular protrusion is shown. It is a whole longitudinal cross-sectional view of the high pressure fuel supply pump of 2nd Example by which this invention was implemented. An embodiment in which a cylinder is fixed using a ring will be described.
- the portion surrounded by a broken line indicates a main body of a high-pressure fuel supply pump (hereinafter referred to as a high-pressure pump), and the mechanisms and components shown in the broken line indicate that the high-pressure pump main body 1 is integrated.
- the fuel in the fuel tank 20 is pumped up by the feed pump 21 and sent to the suction joint 10 a of the pump body 1 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 constituting 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 suction valve 30 includes an electromagnetic coil 308.
- the suction valve body 301 is biased in the valve opening direction due to the difference between the biasing force of the anchor spring 303 and the biasing force of the valve spring 304.
- the suction port 30d is open.
- the urging force of the anchor spring 303 and the urging force of the valve spring 304 are Energizing force of anchor spring 303> Energizing force of valve spring 304 It is set to become.
- the anchor spring 303 In a state in which the electromagnetic coil 308 is energized, the anchor spring 303 is maintained in a compressed state while the anchor 305 is moved leftward in FIG.
- the suction valve body 301 attached so that the tip of the electromagnetic plunger 305 contacts coaxially closes the suction port 30d connected to the pressurizing chamber 11 of the high-pressure pump by the biasing force of the valve spring 304.
- the valve remains open by the biasing force of the intake valve body 301 anchor spring 303.
- the volume of the pressurizing chamber 11 decreases as the plunger 2 compresses, in this state, the fuel once sucked into the pressurizing chamber 11 passes through the suction valve body 301 in the valve-opened state once again to the suction passage 10b (suction). Since the pressure is returned to the port 30a), the pressure in the pressurizing chamber does not increase. This process is called a return process.
- the compression process of the plunger 2 includes a return process and a discharge process. 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 ratio of the return process in the compression process is small and the ratio of the discharge process is large. That is, the amount of fuel returned to the suction passage 10b (suction port 30a) is small, and the amount of fuel discharged at high pressure is large.
- the timing of energization is delayed, the ratio of the return process in the compression process is large and the ratio of the discharge process is small. That is, the amount of fuel returned to the suction passage 10b is large, and the amount of fuel discharged at high pressure is small.
- the timing of energizing the electromagnetic coil 308 is controlled by a command from the ECU.
- the amount of fuel discharged at a high pressure can be controlled to an 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 8a, a discharge valve 8b, and a discharge valve spring 8c.
- the discharge valve 8b When there is no fuel differential pressure in the pressurizing chamber 11 and the fuel discharge port 12, the discharge valve 8b is biased by the discharge valve spring 8c. Is pressed against the discharge valve seat 8a and is in a closed state. Only when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the fuel discharge port 12, the discharge valve 8 b opens against the discharge valve spring 8 c, and the fuel in the pressurization chamber 11 is discharged from the fuel discharge port. 12 is discharged to the common rail 23 through a high pressure.
- the fuel guided to the suction joint 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.
- 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 according to 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.
- ECU engine control unit
- the pump body 1 is further provided with a discharge passage 110 communicating with the downstream side of the discharge valve 8b and the pressurizing chamber 11 by bypassing the discharge valve separately from the discharge passage.
- the discharge passage 110 is provided with a relief valve 102 that restricts the flow of fuel in only one direction from the discharge passage to the pressurizing chamber 11.
- the relief valve 102 is pressed against the relief valve seat 101 by a relief spring 104 that generates a pressing force. When the pressure difference between the pressurizing chamber and the relief passage exceeds a specified pressure, the relief valve 102 is The valve is set to be opened away from the seat 101.
- the relief valve 102 When an abnormally high pressure is generated in the common rail 23 or the like due to a failure of the direct injection injector 24 or the like, the relief valve 102 is opened when the differential pressure between the discharge passage 110 and the pressurizing chamber 11 exceeds the opening pressure of the relief valve 102. Then, the discharge flow path having an abnormally high pressure is returned from the discharge flow path 110 to the pressurizing chamber 11, and the high-pressure section piping such as the common rail 23 is protected.
- FIG. 1 is an overall longitudinal sectional view of a high-pressure fuel supply pump in which the present invention is implemented, and shows a sectional view at the center of a discharge joint axis.
- FIG. 2 is an overall longitudinal sectional view at another angle and shows a sectional view at the center of the suction joint axis.
- FIG. 3 is an overall transverse cross-sectional view showing a cross-sectional view at the center of the fuel-absorption discharge port axis.
- FIG. 4 shows an overall configuration diagram of the fuel supply system.
- 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 provided in the pump body 1.
- An O-ring 61 is fitted into the pump main body 1 to keep the cylinder head and the pump main body airtight.
- the pump body 1 is provided with a cylinder 6 that guides the forward and backward movement of the plunger 2 and has an end formed in a bottomed cylindrical shape so as to form a pressurizing chamber 11 therein. Further, the pressurizing chamber 11 is provided with a plurality of communication holes 11a so as to communicate with an electromagnetic suction valve 30 for supplying fuel and a discharge valve mechanism 8 for discharging fuel from the pressurizing chamber 11 to the discharge passage. .
- 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.
- the plunger seal 13 held at the lower end of the inner periphery of the seal holder 7 is installed in a slidable contact with 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 the pump.
- 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 is sent to the pump body 1 through the suction joint 10a coupled to the suction pipe 28.
- the damper cover 14 is combined with the pump body 1 to form a low-pressure fuel chamber 10, and the fuel that has passed through the inlet joint 10a flows in.
- a fuel filter 102 is attached upstream of the low-pressure fuel chamber 10 by, for example, being press-fitted into the pump body 1 in order to remove foreign matters such as metal powder contained in the fuel.
- the low-pressure fuel chamber 10 is provided with a pressure pulsation reduction mechanism 9 that reduces and reduces the pressure pulsation generated in the high-pressure pump from spreading to the fuel pipe 28.
- the pressure pulsation reducing mechanism 9 provided in the low-pressure fuel chamber 10 is formed by a metal damper 9a in which two corrugated disk-shaped metal plates are bonded together on the outer periphery and an inert gas such as argon is injected therein. The pressure pulsation is absorbed and reduced as the metal damper 9a expands and contracts.
- Reference numeral 9 b denotes a mounting bracket for fixing the metal damper 9 a to the inner peripheral portion of the pump body 1.
- the electromagnetic intake valve 30 includes an electromagnetic coil 308 and is a variable control mechanism that is connected to the ECU via a terminal 307 and controls the flow rate of the fuel by controlling the opening and closing of the intake valve by repeating energization and non-energization.
- 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.
- the biasing force of the valve spring 304 installed inside the suction valve body is Biasing Force of Anchor Spring 303>
- the biasing force of the valve spring 304 is set.
- the suction valve body 301 is biased 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 urging force generated by energizing the coil 308 is set so that the anchor 305 has a force that can be attracted by overcoming the urging force of the anchor spring 303 on the stator 306 side.
- the anchor 303 moves to the stator 306 side (left side in the figure), and a stopper 302 a formed at the end of the anchor rod 302 abuts on and is locked to the anchor rod bearing 309.
- the movement amount of the anchor 301 and the movement amount of the suction valve body 301 are as follows: The clearance is set so that the amount of movement of the anchor 301> and the amount of movement of the suction valve body 301, and the contact portion 302b between the anchor rod 302 and the suction valve body 301 is opened. As a result, the suction valve body 301 has a valve spring 304. And the suction port 30d is closed.
- a suction valve seat 310 is inserted into the cylindrical boss 1b in a secret manner so that the suction valve body 301 can block the suction port 30d to the pressurizing chamber, and is fixed to the pump body 1.
- the discharge valve mechanism 8 is a discharge valve seat member provided with a plurality of discharge passages radially provided with respect to the center of the slide shaft of the discharge valve body 8b, and provided with a bearing so as to hold reciprocal sliding at the center. 8a and a discharge valve member 8b having an annular contact surface that can be kept airtight by providing a central shaft so as to be slidable with respect to the bearing of the discharge valve seat member 8a and contacting the discharge valve sheet member 8a on the outer periphery. . Further, a discharge valve spring 33 composed of a string spring for urging the discharge valve member 8b in the valve closing direction is inserted and held.
- the discharge valve seat member is held in the pump body 1 by, for example, press-fitting, and the discharge valve member 8 b and the discharge valve spring 33 are inserted and sealed in the pump body 1 by the sealing plug 17 to constitute the discharge valve mechanism 8. Yes.
- the discharge valve mechanism 8 functions as a check valve that restricts the direction of fuel flow.
- the relief valve mechanism 100 includes a relief valve stopper 101, a relief valve 102, a relief seat 103, a relief spring stopper 104, and a relief spring 105.
- the relief valve seat 103 has a bearing provided so that the relief valve 102 can slide. After the relief valve 102 having an integral sliding shaft is inserted into the relief valve seat 103, the position of the relief spring stopper 104 is specified so that the relief spring 105 has a desired load, and the relief valve 102 is press-fitted into the relief valve 102. Fix it.
- the valve opening pressure of the relief valve 102 is defined by the pressing force by the relief spring 104.
- the relief valve stopper 101 is inserted between the pump body 1 and the relief valve seat 103 and functions as a stopper that limits the opening amount of the relief valve 102.
- the unitized relief valve mechanism 100 is fixed by press-fitting the relief valve seat 103 into the inner peripheral wall of the cylindrical through-hole 1 ⁇ / b> C provided in the pump body 1.
- the fuel discharge outlet 12 is fixed so as to close the cylindrical through-hole 1C of the pump body 1, and the fuel is prevented from leaking from the high-pressure pump to the outside, and at the same time the connection with the common rail is made possible.
- the relief spring 105 on the fuel discharge port 12 side of 102, the volume of the pressurizing chamber 11 does not increase even if the outlet of the relief valve 102 of the relief valve mechanism 100 is opened to the pressurizing chamber 11.
- 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 overshoots to an extremely high pressure. This high pressure is also propagated in the discharge channel, and the pressure in the discharge channel also overshoots at the same timing.
- the pressure difference between the inlet and outlet of the relief valve 102 may cause the relief valve mechanism 100 to open due to pressure overshoot in the discharge flow path.
- the pressure becomes larger than the valve pressure, and the relief valve malfunctions.
- the pressure in the pressurizing chamber acts on the outlet of the relief valve mechanism 100, and the outlet of the relief valve mechanism 11
- the pressure in the discharge channel 110 acts.
- pressure overshoot occurs at the same timing in the pressurizing chamber and in the discharge flow path, the pressure difference between the inlet and outlet of the relief valve does not exceed the valve opening pressure of the relief valve. That is, the relief valve does not malfunction.
- the direct injection injector fails, that is, when the injection function is stopped and the fuel sent to the common rail 23 cannot be supplied into the combustion chamber of the internal combustion engine, the fuel accumulates between the discharge valve mechanism 8 and the common rail 23 and the fuel pressure becomes abnormal. Become high pressure. In this case, if the pressure rises gradually, an abnormality is detected by the pressure sensor 26 provided on the common rail 23, and the electromagnetic suction valve 30 serving as a capacity control mechanism provided on the suction passage suction passage 10b (suction port 30a) is fed back. Although the safety function to control and reduce the discharge amount operates, instantaneous abnormal high pressure cannot be dealt with by feedback control using this pressure sensor.
- 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 the embodiment functions as a safety valve.
- the cylinder 6 has a large-diameter portion 6b and a small-diameter portion 6c at the outer diameter, and the small-diameter portion is press-fitted into the pump body 1, and the pressure in the suction passage 10b and the pressurizing chamber 11a is controlled by the circumferential surface pressure acting on the small-diameter portion.
- the pressure in the suction passage 10b is the low-pressure fuel pressure supplied to the high-pressure pump by the feed pump, and is about 0.4 MPa.
- the pressure generated in the pressurizing chamber 11 is a pressure pressurized by a high-pressure pump, and the instantaneous pressure is about 30 to 50 MPa.
- the pressurized fuel is supplied from the pressurizing chamber 11 to the common rail 23 through the plurality of communication holes 11 a opened on the cylinder side surface, through the discharge valve mechanism 8 and through the fuel discharge port 12.
- the press-fitting allowance of the small diameter portion is set so that the fuel does not leak into the suction passage 10b due to the pressurizing pressure.
- the gap between the inner diameter of the large-diameter portion 6b and the pump body 1 may be zero or may be light press-fitting.
- the fuel is pressurized in the pressurizing chamber 11, and the applied pressure acts on the bottom surface of the inner diameter of the cylinder 6, so that the large diameter portion 6b and the small diameter are reduced.
- the step 6a of the portion 6c is pressure-bonded to the pump body 1, and the pressurized fuel is sealed so that there is no leakage in the space formed by the seal holder 7 and the cylinder lower end (hereinafter referred to as a sub pressure chamber).
- the auxiliary pressure chamber communicates with the suction passage 10b, and its pressure is equal to the value of the low-pressure side fuel pressure.
- the fuel pressure pressurized during the compression process of the plunger 2 acts on the surface crimping portion. At this time, the bottomed portion of the cylinder 6 receives the applied pressure, and the force is in a direction to avoid leakage that makes the surface crimping portion more closely contact. Act on.
- the pressure is applied in the direction in which the cylinder 6 is in close contact with the pump body 1 during the compression step, which is advantageous in this respect.
- the force due to the low-pressure fuel pressure in the suction passage 10b acts on the cylinder 6 to release the cylinder 6 from the pump body 1.
- the low-pressure side pressure is about 0.4 MPa. If the diameter of the small diameter portion 6c is 13 mm, for example, the detachment force acting on the cylinder 6 is about 53 N, and the pressure input between the small diameter portion 6c and the pump body 1 is performed. It is a value that can be held by.
- FIG. 5 is an enlarged view of the annular protrusion
- FIG. 6 shows another modification of the annular protrusion.
- the step 6a between the large diameter portion 6b and the small diameter portion 6c of the cylinder 6 is provided with an annular protrusion 6d having a triangular cross section.
- the annular protrusion 6d When the cylinder 6 is assembled into the pump body 1, the annular protrusion 6d first contacts the pump body 1 at the step 6a, and the surface pressure increases locally.
- the material of the cylinder 6 is selected to be equal to or higher than the material of the pump body 1 in order to support the reciprocating motion of the plunger 2. Therefore, the pump main body 1 is first plastically deformed, and the annular protrusion 6d bites into the pump main body 1 so that the sealing function of the step 6a can be further enhanced.
- annular protrusion 6d can be configured not to protrude from the plane of the step 6a.
- the step 6a contacts the pump body 1 first, and after the pump body side of the contact surface is slightly plastically deformed, the annular protrusion 6d bites into the pump body, thereby increasing the local surface pressure. Increase the sealing function.
- the projection of the cylinder 6 is not exposed in the state of the parts before assembling the high-pressure pump, there is an advantage that it is easy to handle without having to worry about breakage of the projection.
- the annular protrusion 6d has a triangular shape, but the same effect can be expected for a convex shape, a curved surface shape, and the like.
- this object can be achieved by configuring the pump body 1 with a similar annular protrusion.
- FIG. 7 is an overall longitudinal sectional view of a high-pressure pump in which a cylinder is fixed using a ring 16.
- the end surface of the cylinder large-diameter portion 6 b is pressed by a ring 16 for the purpose of applying a preload to the surface crimping portion 6 a of the cylinder 6.
- the ring 16 is press-fitted into the pump body 1 or fixed by a metal flow (plastic flow coupling) 1d shown in FIG. 8A and a caulking 1f shown in FIG. 8B.
- the ring 16 is pressed into the pump body 1 while being pressurized so as to obtain a desired pressing load when the cylinder 6 is assembled in the pump body 1, and then the ring 16 is fixed to the pump body 1 by metal flow. .
- FIG. 8 shows an embodiment in which a cylinder is fixed using a ring.
- a gap 17 is provided between the large diameter portion 6 b of the cylinder 6 and the pump body 1. According to the cylinder structure described so far, the cylinder 6 is held by press-fitting the small-diameter portion 6C into the pump body 1 and pressing the surface crimping portion 6a onto the pump body 1. Therefore, even if a gap is provided between the cylinder outer diameter portion 6b and the pump body 1, there is no problem in holding the cylinder.
- the gap between the outer diameter of the plunger 2 and the inner diameter of the cylinder 6 greatly affects the pump pressurization performance. That is, if this gap is large, the compression efficiency of the fuel is lower than that of the pressurizing chamber 11 during the compression process. Therefore, this gap needs to be about 5 to 10 ⁇ m when the plunger diameter is 8 to 10 mm, and the outer diameter of the plunger 2 and the inner diameter of the cylinder 6 must be processed with high accuracy.
- the cylinder inner diameter is slightly deformed in the contraction direction.
- the press-fitting allowance is 10 to 20 ⁇ m
- the amount of deformation contracts by about 1 to 2 ⁇ m, which is a tenth. Since the gap between the outer diameter of the plunger 2 and the inner diameter of the cylinder 6 is 5 to 10 ⁇ m, in the worst case, this contraction may cause plunger seizure during high-pressure pump operation. Therefore, the cylinder inner diameter needs to be corrected again after the cylinder 6 is press-fitted.
- the gap between the outer diameter of the plunger 2 and the inner diameter of the cylinder 6 is defined between the cylinder end surfaces protruding into the auxiliary pressure chamber from the step 6a of the cylinder large diameter portion.
- the air gap 17 is provided between the cylinder large-diameter portion 6b and the pump main body 1, even if the cylinder 6 is incorporated into the pump main body 1, no force is exerted in the direction in which the inner diameter contracts and deforms.
- the cylinder inner diameter is increased to avoid plunger seizure due to a decrease in the gap due to the press fitting of the small diameter portion.
- this embodiment can also be defined as follows. That is, a high-pressure fuel pump having a plunger that reciprocates, a cylinder having a portion that guides the reciprocating movement of the plunger, and a pump body that holds the cylinder, the cylinder having a bottomed cylindrical shape, a large diameter portion, and a small diameter
- a high-pressure fuel pump having a cylinder and a cylinder surface-compressed in the reciprocating direction of the pump body and the plunger.
- a high-pressure fuel pump having a reciprocating plunger, a cylinder having a portion for guiding the reciprocating movement of the plunger, and a pump body holding the cylinder, the cylinder having a bottomed cylindrical shape, a large diameter portion, and a small diameter
- a high pressure fuel pump having a portion and having a cylinder surface-compressed in a reciprocating direction of the pump body and the plunger and in a portion not overlapping the guiding portion and the axial direction.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
アンカーばね303の付勢力 > 弁ばね304の付勢力
となるよう設定されている。
低圧燃料室10には高圧ポンプ内で発生した圧力脈動が燃料配管28へ波及するのを低減減させる圧力脈動低減機構9が設置されている。一度加圧室11に吸入された燃料が、容量制御状態のため再び開弁状態の吸入弁体301を通して吸入通路10b(吸入ポート30a)へと戻される場合、吸入通路10b(吸入ポート30a)へ戻された燃料により低圧燃料室10には圧力脈動が発生する。しかし、低圧燃料室10に設けた圧力脈動低減機構9は、波板状の円盤型金属板2枚をその外周で張り合わせ、内部にアルゴンのような不活性ガスを注入した金属ダンパ9aで形成されており、圧力脈動はこの金属ダンパ9aが膨張・収縮することで吸収低減される。9bは金属ダンパ9aをポンプ本体1の内周部に固定するための取り付け金具である。
アンカーばね303の付勢力 > 弁ばね304の付勢力
となるよう設定されており、結果、吸入弁体301は開弁方向に付勢され吸入口30dは開けられた状態となっている。この時アンカーロッド302と吸入弁体301は302bに示す部位で接触している(図1に示す状態)。
アンカー301の移動量>と吸入弁体301の移動量
となる様にクリアランスが設定されておりアンカーロッド302と吸入弁体301の接触部302bは開放され、結果吸入弁体301は、弁ばね304により付勢され吸入口30dは閉じられた状態となる。
このように、リリーフ弁102の燃料吐出口12側にリリーフばね105を設けることで、リリーフ弁機構100のリリーフ弁102の出口を加圧室11に開口しても加圧室11の容積が増加することはない。
図7において、シリンダ6の面圧着部6aに予圧力を付加することを目的としてシリンダ大径部6bの端面をリング16により押し付けている。リング16はポンプ本体1に圧入もしくは、図8(a)に示すメタルフロー(塑性流動結合)1dおよび図8(b)に示すかしめ1f等で固定されるものとする。ポンプ本体1にシリンダ6を組み込み時に所望の押し付け荷重を得る様にリング16を与圧しつつポンプ本体1に組み込んだ後にリングをかしめ、もしくはメタルフローでリング16をポンプ本体1に固定するものである。
2 プランジャ
6 シリンダ
8 吐出弁機構
9 圧力脈動低減機構
30 電磁吸入弁
100 リリーフ弁機構
Claims (5)
- 往復運動するプランジャと、
前記プランジャの往復運動をガイドする部分を有するシリンダと、
前記シリンダを保持するポンプボディと、
を有する高圧燃料ポンプであって、
前記シリンダは有底筒型形状かつ大径部と小径部を有し、前記シリンダは前記ポンプボディと前記プランジャの往復運動方向に面圧着される、
高圧燃料ポンプ - 請求項1記載の高圧燃料供給ポンプであって、
前記シリンダは環状突起を有し、該環状突起が前記ポンプと面圧着する、高圧燃料供給ポンプ。 - 前記シリンダの面圧着部に予圧力を付加するよう前記シリンダ大径部をリング形状などの別部材を介し、この別部材はかしめ等の塑性加工もしくは圧入によりポンプボディに固定されている請求項1に記載の高圧燃料供給ポンプ
- 前記シリンダの大径部外径は前記ポンプ本体の内径に対し空隙を有する様に構成された請求項1に記載の高圧燃料供給ポンプ
- 往復運動するプランジャと、
前記プランジャの往復運動をガイドする部分を有するシリンダと、
前記シリンダを保持するポンプボディと、
を有する高圧燃料ポンプであって、
前記シリンダは有底筒型形状かつ大径部と小径部を有し、前記シリンダは前記ポンプボディと前記プランジャの往復運動方向であって、かつ前記ガイドする部分と軸方向に重ならない部分で面圧着される、
高圧燃料ポンプ。
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EP15782715.5A EP3135899B1 (en) | 2014-04-25 | 2015-04-17 | High-pressure fuel pump |
CN201580022013.1A CN106255822B (zh) | 2014-04-25 | 2015-04-17 | 高压燃料供给泵 |
JP2016514896A JP6268279B2 (ja) | 2014-04-25 | 2015-04-17 | 高圧燃料供給ポンプ |
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Cited By (3)
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WO2017207150A1 (de) * | 2016-06-02 | 2017-12-07 | Robert Bosch Gmbh | Hochdruckpumpe für ein kraftstoffeinspritzsystem |
CN110184734A (zh) * | 2019-06-27 | 2019-08-30 | 李鸣 | 常开式机头三角气缸 |
CN113123907A (zh) * | 2020-01-15 | 2021-07-16 | 株式会社电装 | 制造组件的方法、零件组、燃料喷射泵及制造其的方法 |
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JP2001295729A (ja) * | 2000-04-18 | 2001-10-26 | Toyota Motor Corp | 高圧ポンプ |
JP2009185613A (ja) * | 2008-02-04 | 2009-08-20 | Hitachi Ltd | 高圧燃料ポンプ |
JP2012211558A (ja) * | 2011-03-31 | 2012-11-01 | Denso Corp | 高圧ポンプ |
WO2013080253A1 (ja) * | 2011-11-30 | 2013-06-06 | 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 |
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EP2122168B1 (en) * | 2007-01-10 | 2015-12-09 | Stanadyne Corporation | Load ring mounting of pumping plunger |
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 |
CN102619660B (zh) * | 2011-01-28 | 2015-06-24 | 株式会社电装 | 高压泵 |
JP5768723B2 (ja) * | 2012-01-10 | 2015-08-26 | 株式会社デンソー | 高圧ポンプ |
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2015
- 2015-04-17 CN CN201580022013.1A patent/CN106255822B/zh active Active
- 2015-04-17 WO PCT/JP2015/061774 patent/WO2015163243A1/ja active Application Filing
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Patent Citations (5)
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JPH06249133A (ja) * | 1993-02-12 | 1994-09-06 | Elasis Sistema Ric Fiat Nel Mezzogiorno Soc Consortile Per Azioni | ポンプ装置 |
JP2001295729A (ja) * | 2000-04-18 | 2001-10-26 | Toyota Motor Corp | 高圧ポンプ |
JP2009185613A (ja) * | 2008-02-04 | 2009-08-20 | Hitachi Ltd | 高圧燃料ポンプ |
JP2012211558A (ja) * | 2011-03-31 | 2012-11-01 | Denso Corp | 高圧ポンプ |
WO2013080253A1 (ja) * | 2011-11-30 | 2013-06-06 | 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 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017207150A1 (de) * | 2016-06-02 | 2017-12-07 | Robert Bosch Gmbh | Hochdruckpumpe für ein kraftstoffeinspritzsystem |
CN110184734A (zh) * | 2019-06-27 | 2019-08-30 | 李鸣 | 常开式机头三角气缸 |
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 |
CN113123907A (zh) * | 2020-01-15 | 2021-07-16 | 株式会社电装 | 制造组件的方法、零件组、燃料喷射泵及制造其的方法 |
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EP3135899B1 (en) | 2020-10-28 |
CN106255822B (zh) | 2018-12-07 |
EP3135899A1 (en) | 2017-03-01 |
JP6268279B2 (ja) | 2018-01-24 |
CN106255822A (zh) | 2016-12-21 |
EP3135899A4 (en) | 2017-12-27 |
JPWO2015163243A1 (ja) | 2017-04-13 |
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