WO2019012976A1 - Pompe à carburant haute-pression - Google Patents

Pompe à carburant haute-pression Download PDF

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Publication number
WO2019012976A1
WO2019012976A1 PCT/JP2018/024091 JP2018024091W WO2019012976A1 WO 2019012976 A1 WO2019012976 A1 WO 2019012976A1 JP 2018024091 W JP2018024091 W JP 2018024091W WO 2019012976 A1 WO2019012976 A1 WO 2019012976A1
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WO
WIPO (PCT)
Prior art keywords
suction valve
fuel pump
pressure fuel
high pressure
valve
Prior art date
Application number
PCT/JP2018/024091
Other languages
English (en)
Japanese (ja)
Inventor
幸平 松下
谷江　尚史
康雄 溝渕
徳尾　健一郎
Original Assignee
日立オートモティブシステムズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立オートモティブシステムズ株式会社 filed Critical 日立オートモティブシステムズ株式会社
Publication of WO2019012976A1 publication Critical patent/WO2019012976A1/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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • 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

Definitions

  • the present invention relates to a high pressure fuel pump for supplying fuel to an internal combustion engine at high pressure.
  • FIG. 1 provides a high pressure pump capable of reducing the weight of a suction valve for opening and closing a supply passage for supplying fuel to a pressurizing chamber.
  • the suction valve 40 closes the supply passage 100 by being seated on the valve seat 34 and opens the supply passage 100 by leaving the valve seat 34.
  • a stopper 50 is provided on the pressure chamber side of the suction valve 40 to limit movement of the suction valve 40 to the pressure chamber side.
  • the needle 60 configured separately from the suction valve 40 can abut on the end face of the suction valve 40 on the valve seat 34 side.
  • the first spring 21 is accommodated in the accommodation chamber 52 provided in the stopper 50, and urges the suction valve 40 toward the valve seat 34.
  • the guide portion 41 extending from the end face on the stopper 50 side of the suction valve 40 is formed such that the axial length B is longer than the movement distance A between the fully closed and fully opened suction valve 40. Restrict movement. It is disclosed that this makes it possible to reduce the outer diameter of the suction valve 40 and reduce the axial thickness thereof (see the summary).
  • Patent Document 1 describes that the weight of the suction valve can be reduced by reducing the outer diameter of the suction valve and reducing the thickness in the axial direction.
  • the thickness is made too thin for the purpose of weight reduction, the strength reliability of the valve body is reduced, and there is a concern that fatigue failure may occur.
  • the axial thickness may be increased, and the noise reduction effect may not be sufficiently obtained.
  • An object of the present invention is to provide a high-pressure fuel pump equipped with a suction valve that reduces noise while maintaining strength reliability.
  • the high-pressure fuel pump includes a suction valve for opening and closing a flow path, a seat portion on which the suction valve is seated, and a movement of the suction valve toward the opposite side of the seat portion when opened.
  • a high pressure fuel pump comprising a stopper portion for restricting the pressure, and a rod which is formed separately from the suction valve and which biases the suction valve toward the stopper portion, the suction valve includes a central portion, and The radial outer side of the central portion is formed from the downstream surface of the central portion toward the upstream, and is formed with an outer peripheral portion whose axial thickness is thinner than the central portion.
  • FIG. 1 is a diagram showing an overall configuration of a high pressure fuel pump system to which an embodiment of the present invention is applied. It is a figure which shows the cross section of the electromagnetic suction valve mechanism 50 with which the Example of this invention is applied. It is a figure showing the section of electromagnetic induction valve mechanism 50 concerning Example 1 of the present invention. It is a figure explaining the case where concentration load F acts on the end of cantilever with length R 1 -R 0 and width x ⁇ . It is a figure explaining about the case where the fuel pressure p acts on the end of the cantilever of length R-R 0 and width x ⁇ . It is a figure which shows the cross section of the electromagnetic suction valve mechanism 50 which concerns on Example 2 of this invention.
  • Example 1 will be described with reference to FIGS. 1 and 2.
  • FIG. 1 shows the overall configuration of a high pressure fuel pump system to which the embodiments of the present invention (Embodiments 1 to 6) are applied. For this reason, first, the entire configuration will be described using FIG. 2, and then each embodiment of the suction valve structure will be described.
  • the high-pressure fuel pump system shown in FIG. 1 can be roughly divided into a fuel tank 101 on the left side, a high-pressure fuel pump 300 on the center side, a fuel injection system 200 (common rail 53, injector 54, etc.) on the right side. 40, an internal combustion engine 400 (not shown) below the center of the drawing (below the high pressure fuel pump 1).
  • the high pressure fuel pump 300 integrally incorporates a plurality of parts and mechanisms in the body 1 and is attached to the cylinder head 20 of the internal combustion engine 400.
  • a suction passage 9, a pressure chamber 11, a discharge passage 12, and a relief passage 15 are formed in the body 1.
  • An electromagnetic suction valve mechanism 5 is provided in the suction passage 9, a discharge valve 8 in the discharge passage 12, and a relief valve mechanism 30 in the relief passage 15. Further, the volume of the pressure chamber 11 in the body 1 is changed by the plunger 2 moved up and down by the rotation of the cam 7 of the internal combustion engine, and the pump operation becomes possible.
  • the electromagnetic suction valve mechanism 50 is a control valve that determines the amount of fuel to be pressurized.
  • the discharge valve 8 is a check valve that restricts the flow direction of the fuel.
  • the relief valve mechanism 30 functions as a safety valve that opens the inside of the common rail 53 when the pressure in the common rail 53 exceeds a predetermined pressure.
  • the fuel from the fuel tank 101 is introduced to the high pressure fuel pump 300 and passes through the electromagnetic suction valve mechanism 50 of the suction passage 9, the pressure chamber 11 and the discharge valve 8 of the discharge passage 12. Is supplied to the fuel injection system 200.
  • the high pressure fuel pump is connected to the common rail 53 of the fuel injection system 200, and the pressurized fuel is pumped, and the high pressure fuel is injected from the injector 54 into the combustion chamber of the internal combustion engine.
  • the pressure in the common rail 53 is measured by a pressure sensor 56, and the signal is sent to an engine control unit (ECU) 40.
  • the injectors 54 are mounted in accordance with the number of cylinders of the engine, and inject fuel in response to a signal from the engine control unit (ECU) 40.
  • the engine control unit (ECU) 40 also controls an electromagnetic suction valve mechanism 50 in the high pressure fuel pump.
  • the plunger 2 at the lower part of the pressure chamber 11 is slidably inserted into the cylinder 120, and a retainer 3 is attached to the lower end.
  • the biasing force of the plunger return spring 4 acts on the retainer 3 downward in FIG.
  • the tappet 6 reciprocates in the vertical direction of FIG. 1 by the rotation of the cam 7 of the internal combustion engine.
  • the plunger 2 is displaced following the tappet 6, whereby the volume of the pressure chamber 11 changes and the pump operation becomes possible.
  • the electromagnetic suction valve mechanism 50 is held in a hole formed in the body 1 by press-fitting and welding.
  • the electromagnetic suction valve mechanism 50 is provided with an electromagnetic coil 500, a mover 503, an anchor spring 502, and a valve body spring 504.
  • the movable portion 503 is formed of one member, but the movable portion 503 is driven in the valve closing direction (left direction in FIG. 1) by the anchor forming the magnetic attraction surface attracted to the magnetic core and the anchor. It may be formed from two parts of the rod.
  • FIG. 1 shows an engine system using a normally open type electromagnetic suction valve mechanism 50, but the present invention is not limited thereto. That is, the present invention is also applicable to the case where a normally closed electromagnetic suction valve mechanism is provided.
  • the electromagnetic intake valve mechanism which is in the valve open state when the electromagnetic coil 500 is off and the valve closed state when the electromagnetic coil 500 is on is referred to as a normally open type electromagnetic intake valve mechanism.
  • the biasing force of the anchor spring 502 acts on the suction valve 501 in the valve opening direction via the movable portion 503, while the biasing force of the valve body spring 504 acts on the valve closing direction.
  • the biasing force of the anchor spring 502 is larger than the biasing force of the valve body spring 504. Therefore, when the electromagnetic coil 500 is OFF, ie, when no current is supplied, the suction valve 501 overcomes the biasing force of the valve spring 504 by the mover 503 biased by the anchor spring 502, so the suction valve 501 is opened. It has become.
  • a normally closed system in which the suction valve 501 is closed when the operation is reversed, that is, when the electromagnetic coil 500 is OFF (no current). It is possible to practice the present invention.
  • the plunger 2 starts moving upward again after reaching the BDC (Bottom Dead Center).
  • the electromagnetic coil 500 is in the OFF state.
  • the movable portion 503 maintains the open state of the suction valve 501 even if the plunger 2 moves upward.
  • the pressure in the pressure chamber 11 is in a low pressure state substantially equal to that of the suction passage 9, the discharge valve 8 can not be opened, and the fuel corresponding to the volume reduction of the pressure chamber 11 is the suction valve 501.
  • This process is called a return process.
  • a metal damper composed of a two-piece metal diaphragm for reducing pulsation of fuel pressure is disposed.
  • the mover 503 When the electromagnetic coil 500 is energized in the return step, the mover 503 is attracted to the magnetic core 5 by the magnetic attraction force, and the magnetic attraction force overcomes the biasing force of the anchor spring 502 to move the movable portion 503 in the valve closing direction. . Then, the valve body 501 is closed by the biasing force of the valve body spring 504 and the fluid pressure difference of the return fuel. Immediately after the suction valve 501 is closed, the fuel pressure in the pressure chamber 11 rises with the rise of the plunger 2. Thus, the discharge valve 8 is automatically opened, and the fuel is pressure fed to the common rail 53.
  • the relief valve mechanism 30 includes a relief valve 151 seated on the relief valve seat 150 and a relief spring 155 biasing the relief valve 151 in the valve closing direction.
  • FIG. 1 An enlarged view A of the lower drawing of FIG. 1 shows an enlarged sectional view of the suction valve although the shape is different from the suction valve 501 shown in the upper drawing of FIG.
  • the electromagnetic suction valve mechanism 50 includes a suction valve 501, a valve body spring 504 for biasing the suction valve 501 in a valve closing direction, a seat portion 505 on which the suction valve 501 is seated, and the suction valve 501.
  • a stopper portion 506 for restricting the movement in the valve opening direction and a rod portion 507 for urging the suction valve 501 in the valve opening direction are provided.
  • the stopper member forming the stopper portion 506 is press-fitted to the inner peripheral surface of the sheet member forming the sheet portion 505.
  • the high-pressure fuel pump of this embodiment includes a suction valve 501 for opening and closing a flow path, a seat portion 505 on which the suction valve 501 is seated, and a stopper for regulating the movement of the suction valve 501 toward the opposite side to the seat portion 501 when opening. And a rod configured separately from the suction valve 501 and urging the suction valve 501 toward the stopper portion 506.
  • the suction valve 501 has a central portion 509, an outer peripheral portion 511 which is formed radially outward of the central portion 509 from the downstream surface of the central portion 509 toward the upstream and has a thinner axial thickness than the central portion 509. It is formed by
  • the electromagnetic suction valve mechanism 50 has a suction valve 501 that opens and closes the flow path at the valve body upstream portion 508, a seat portion 505 that holds the suction valve 501 when closing the valve, and a stopper portion that holds the suction valve 501 when opening the valve. And a rod 507 configured separately from the suction valve 501 to bias the suction valve 501, and a valve spring 504 biasing the suction valve 501 toward the rod 507. Further, as shown in FIG. 2, it is desirable that the central portion 509 is configured to become thinner as the axial thickness goes radially outward.
  • the suction valve 501 is configured such that the plate thickness (axial direction thickness) becomes thinner toward the outermost peripheral portion 510, and a curved surface portion 511 recessed on the upstream side is formed.
  • One end of the valve body spring 504 contacts the spring contact portion 512 on the inner diameter side of the central portion 509 of the suction valve 501 to bias the suction valve 501 in the valve closing direction.
  • the spring contact portion 512 is configured to be formed on the same plane at the same inclination as the central portion 509.
  • the outer peripheral portion 511 is formed to be connected to the central portion 509, and the downstream surface of the outer peripheral portion 511 is configured to have a curved surface portion recessed on the upstream side.
  • all of the outer peripheral portion 511 be configured to be located upstream with respect to all of the downstream surfaces of the central portion 509.
  • the downstream surface of the central portion 509 be configured to collide with the stopper portion 506 that restricts the movement of the suction valve 501 in the valve opening direction.
  • the curved surface portion of the downstream surface of the outer peripheral portion 511 be formed on the outermost peripheral portion of the suction valve 501.
  • the mass of the suction valve 501 becomes lighter. Noise can be reduced.
  • the axial thickness t of the suction valve 501 extends from the outermost peripheral portion 510 (radius R) to the root portion 514 (radius R 0 ) of the central portion 509 It is formed so as to be equal to or greater than the axial thickness indicated by (Equation 1) and (Equation 2) of In the present embodiment, the suction valve 501 has the largest axial thickness at the radial center and has a guide portion guided by the inner peripheral portion of the valve body spring 504. That is, the central portion 509 is formed radially outward with respect to the guide portion.
  • the axial thickness t (x) of the suction valve 501 is set to satisfy the following (Equation 1).
  • R 1 is a radius to the stopper contact portion 513
  • t 0 is an axial thickness of the root portion 514.
  • the plate thickness t (x) where the relationship between ⁇ (x) and ⁇ s always satisfies ⁇ (x) ⁇ ⁇ s is as shown in (Equation 1). Accordingly, the stress applied from the outermost periphery 510 to the root portion 514 of the suction valve 501, which is applied when the suction valve 501 and the stopper portion 506 contact, can be made equal to or less than the stress applied to the root portion 514.
  • the axial thickness t (x) of the suction valve 501 be set to satisfy the above (Equation 2).
  • Equation 7 The moment M (x) acting on each cross section of the beam can be expressed by (Equation 7), and the bending stress ⁇ (x) can be expressed by (Equation 3). If the equation (7) is rearranged by the equation (3), the bending stress ⁇ (x) can be expressed by the equation (8). As shown in the enlarged view A of FIG.
  • the suction valve 501 has a spring contact portion 512 with the valve body spring 504 on the inner diameter side of the central portion 509.
  • the downstream surface of the central portion 509 is provided with a spring contact portion 512 with the valve body spring 504, and the spring contact portion 512 is a direction orthogonal to the axial direction (left and right direction in FIG. 6) of the valve body spring 504. It is formed flat (in the vertical direction in FIG. 6).
  • valve body spring 504 and the spring contact part 512 contact uniformly, the biasing force which the suction valve 501 receives from the valve body spring 504 can be stabilized. Therefore, it is possible to suppress the asymmetry of the suction valve 501 and provide the electromagnetic suction valve mechanism 50 with high reliability.
  • the suction valve 501 is configured such that the stopper contact portion 513 with the stopper portion 506 is a flat portion. That is, the downstream surface of the central portion 509 includes the stopper contact portion 513 with the stopper portion 506, and the stopper contact portion 513 is formed flat in the direction orthogonal to the valve body spring 504.
  • the valve body 501 when the contact portion 513 with the stopper portion 506 is flat, the valve body 501 does not locally contact the stopper portion 506, and the wear of the suction valve 501 can be prevented.
  • the outermost peripheral portion 510 of the suction valve 501 has a sharp shape, the outermost peripheral portion 510 can not be fixed when manufacturing the suction valve 501 by lathe processing, and the workability is reduced. According to the above configuration, this is suppressed, and the processing of the suction valve 501 is facilitated.
  • the electromagnetic suction valve mechanism 50 includes a suction valve 501, a valve body spring 504, a seat portion 505, a stopper portion 506, a rod portion 507, an outermost peripheral portion 510, a stopper contact portion 513, and a suction valve 501. And a root portion 514 of the central portion 509.
  • a curved surface portion 511 which is configured such that the thickness in the axial direction decreases from the outermost peripheral portion 510 toward the stopper contact portion 513 and is recessed on the upstream side is formed, and the central portion root portion from the stopper contact portion 513 The axial thickness is made constant over 514.
  • the central portion 509 of the suction valve 501 is formed in a flat plate shape having a constant axial thickness.
  • a curved outer peripheral portion 511 is formed from the stopper contact portion 513 with the stopper portion 506 toward the outermost peripheral portion 510, and the radial direction inward from the stopper contact portion 513 is in the axial direction
  • a central portion 509 having a constant thickness is formed.
  • the downstream surface of the outer peripheral portion 511 is formed to have a curved surface portion recessed toward the upstream side.
  • the axial thickness of the suction valve 501 be configured to satisfy the relationship shown in (Equation 1) and (Equation 2) shown in the first embodiment.
  • a sixth embodiment of the present invention will be described with reference to FIG.
  • the basic configuration is the same as that of the first embodiment or the fifth embodiment, so only the difference will be described here.
  • the outermost peripheral portion 510 of the suction valve 501 has a curved surface or a constant thickness.
  • the outermost periphery 510 of the suction valve 501 has a sharp shape, it can not be fixed when manufacturing the suction valve 501 by lathe processing, which makes processing difficult. According to the above configuration, this is suppressed, and the processing of the suction valve 501 is facilitated.
  • the present invention is widely applicable not only to high pressure fuel pumps for internal combustion engines but also to various high pressure pumps.

Abstract

L'invention concerne une pompe à carburant haute pression dans laquelle est montée une soupape d'aspiration qui réduit le bruit tout en maintenant la fiabilité de la résistance. Cette pompe à carburant haute pression est pourvue: d'une soupape d'aspiration pour ouvrir et fermer un passage d'écoulement; d'un siège sur lequel repose la soupape d'aspiration; d'un bouchon qui, au moment de l'ouverture de la soupape, empêche la soupape d'aspiration de s'éloigner du siège; et d'une tige formée en tant que corps séparé à partir de la soupape d'aspiration et sollicitant la soupape d'aspiration vers la butée. La soupape d'aspiration comprend une section centrale et une section périphérique externe qui est formée radialement à l'extérieur de la section centrale de façon à s'étendre en amont à partir de la surface aval de la section centrale, et qui a une épaisseur axiale plus petite que celle de la section centrale.
PCT/JP2018/024091 2017-07-14 2018-06-26 Pompe à carburant haute-pression WO2019012976A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-137639 2017-07-14
JP2017137639A JP6855343B2 (ja) 2017-07-14 2017-07-14 高圧燃料ポンプ

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WO2019012976A1 true WO2019012976A1 (fr) 2019-01-17

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004218633A (ja) * 2002-12-27 2004-08-05 Bosch Automotive Systems Corp 高圧燃料ポンプ
US20100206252A1 (en) * 2007-07-20 2010-08-19 Bernd Schroeder High-pressure pump for a fuel system of an internal combustion engine
JP2015127545A (ja) * 2015-03-26 2015-07-09 株式会社デンソー 高圧ポンプ
JP2016133010A (ja) * 2015-01-16 2016-07-25 株式会社デンソー 高圧ポンプ

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5126605B2 (ja) * 2008-12-26 2013-01-23 株式会社デンソー 高圧ポンプ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004218633A (ja) * 2002-12-27 2004-08-05 Bosch Automotive Systems Corp 高圧燃料ポンプ
US20100206252A1 (en) * 2007-07-20 2010-08-19 Bernd Schroeder High-pressure pump for a fuel system of an internal combustion engine
JP2016133010A (ja) * 2015-01-16 2016-07-25 株式会社デンソー 高圧ポンプ
JP2015127545A (ja) * 2015-03-26 2015-07-09 株式会社デンソー 高圧ポンプ

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JP6855343B2 (ja) 2021-04-07
JP2019019728A (ja) 2019-02-07

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