WO2003095824A1 - Structure de montage de pompe de carburant pour moteur a injection de carburant - Google Patents

Structure de montage de pompe de carburant pour moteur a injection de carburant Download PDF

Info

Publication number
WO2003095824A1
WO2003095824A1 PCT/JP2003/005800 JP0305800W WO03095824A1 WO 2003095824 A1 WO2003095824 A1 WO 2003095824A1 JP 0305800 W JP0305800 W JP 0305800W WO 03095824 A1 WO03095824 A1 WO 03095824A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel pump
fuel
cam
intake
fuel injection
Prior art date
Application number
PCT/JP2003/005800
Other languages
English (en)
Japanese (ja)
Inventor
Shinichi Kurosawa
Original Assignee
Yamaha Hatsudoki Kabushi Kikaisha
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 Yamaha Hatsudoki Kabushi Kikaisha filed Critical Yamaha Hatsudoki Kabushi Kikaisha
Publication of WO2003095824A1 publication Critical patent/WO2003095824A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]

Definitions

  • the present invention relates to a fuel pump mounting structure for a fuel injection engine in which a fuel pump for supplying fuel to a fuel injection valve is cam-driven by a cam shaft.
  • a fuel pump that supplies high-pressure fuel to a fuel injection valve may be driven by a camshaft.
  • a mounting structure of such a fuel pump conventionally, for example, a mounting hole is formed in a portion facing a cam shaft of a head cover, a driving portion of the fuel pump is inserted into the mounting hole, and a flange portion of the fuel pump is mounted on the head cover. Some are fixed.
  • the wall thickness of the pump mounting portion of the head cover is increased in order to increase the mounting strength of the fuel pump.
  • An object of the present invention is to provide a fuel injection engine mounting structure for a fuel injection engine, which can prevent the occurrence of the occurrence and can easily perform alignment with a camshaft. Disclosure of the invention
  • the fuel pump in a fuel pump mounting structure for a fuel injection engine in which a fuel pump for supplying fuel to a fuel injection valve is driven by a camshaft, the fuel pump is formed on a head cover. It is characterized by being fixed to the cylinder head through the through hole.
  • the invention according to claim 2 is the invention according to claim 1, wherein the fuel pump is fixed to a cylinder head via a bracket, and the bracket has a through hole through which a driving unit of the fuel pump is attached. And a base portion formed so as to straddle a cam cap adjacent in the axial direction of the cam shaft. The base portion is shared with the cam carrier of the cylinder head together with the cam cap. It is characterized by being fastened and fixed.
  • the invention according to claim 3 is the invention according to claim 2, wherein the main body of the bracket is exposed to the outside from the through hole of the head cover, and a gap between the peripheral portion of the through hole and the main body is provided. Is provided with a seal member made of an elastic body.
  • the fuel pump is disposed so as to be inclined outward with respect to the cylinder axis.
  • FIG. 1 is a plan view of a cylinder head of an engine according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of the cylinder head (a cross-sectional view taken along line 11 in FIG. 1).
  • Fig. 3 is a cross-sectional view of the above-mentioned cylinder head (a cross-sectional view taken along line II-III in Fig. 1).
  • FIG. 4 is a sectional view showing the operation of the variable valve lift mechanism of the engine.
  • FIG. 5 is a cross-sectional view (a cross-sectional view taken along the line V-V in FIG. 1) of a mounting portion of the fuel pump of the engine.
  • FIG. 6 is a side view of the fuel pump mounting portion.
  • FIG. 7 is a plan view of a bracket for mounting the fuel pump.
  • FIG. 8 is a side view of the bracket.
  • FIG. 9 is a cross-sectional view (a cross-sectional view taken along line IX-IX in FIG. 7) of the bracket of the bracket.
  • FIG. 10 is a cross-sectional view (cross-sectional view taken along line X-X) of the bracket.
  • FIG. 11 is a cross-sectional view of a valve spring supporting portion of the cylinder head.
  • FIG. 12 is a diagram of the rocker arm of the engine. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 is a plan view of a cylinder head of the engine
  • FIGS. Fig. 3 is a cross-sectional view of the cylinder head (cross-sectional view taken along the line ⁇ - ⁇ , in Fig. 1;
  • Fig. 4 is a cross-sectional view showing the operation of the variable valve lift mechanism).
  • 5 is a cross-sectional view of the fuel pump mounting part (cross-sectional view taken along the line VV in FIG. 1)
  • FIG. 6 is a side view of the fuel pump mounting part
  • FIGS. 7 and 8 are plan, side, and figure views of the bracket. 9, Fig.
  • FIG. 10 is a cross-sectional view of the bracket (cross-sectional view taken along line IX-IX and XX in Fig. 7), Fig. 11 is a cross-sectional view of the intake port of the cylinder head, and Fig. 12 is a rocker arm.
  • FIG. 10 is a cross-sectional view of the bracket (cross-sectional view taken along line IX-IX and XX in Fig. 7)
  • Fig. 11 is a cross-sectional view of the intake port of the cylinder head
  • Fig. 12 is a rocker arm.
  • reference numeral 1 denotes a water-cooled 4-cycle multi-cylinder engine.
  • the engine 1 opens and closes intake and exhaust valves 4 and 5 via rocker arms 7 and 9 by intake and exhaust camshafts 6 and 8 described later.
  • the upper mating surface 1a of the cylinder head 2 of the engine 1 is connected to the lower mating surface 3a of the head cover 3, and the lower mating surface 1b is connected to a cylinder block (not shown).
  • a crankcase (not shown) for accommodating a crankshaft is connected to the cylinder block.
  • Reference numeral 12 denotes a head bolt hole for fixing the cylinder head 2 to the cylinder block, and two holes are formed between the cylinders.
  • a combustion recess 2c is formed in the lower mating surface 2b of the cylinder head 2, and the combustion recess 2c, the cylinder bore of the cylinder block, and the top surface of the piston inserted into the cylinder bore are formed. (Not shown) A space surrounded by and is a combustion chamber.
  • the combustion recess 2c has two intake openings 2d, 2d and two exhaust openings 2e, 2e.
  • the intake opening 2d, the exhaust opening 2e have an intake valve 4, an exhaust valve 2e, respectively.
  • Valve 5 is provided so as to be openable and closable.
  • Each intake valve 4 is driven to open and close by an intake force arm 7 by an intake force shaft 6 constituting the valve operating mechanism, and each exhaust valve 5 is driven by an exhaust cam shaft 8 via an exhaust port arm 9. It is driven to open and close.
  • the intake and exhaust camshafts 6, 8 are rotationally driven by a crankshaft via a timing chain (not shown).
  • An intake port 1 f communicating with each intake opening 2 d is formed in the cylinder head 1, and each intake port 1 f joins on the way and leads to the right wall surface 2 f ′ of the cylinder head 2.
  • An exhaust port 1 g communicating with each exhaust opening 2 e is formed in the cylinder head 2, and each exhaust port 1 g joins on the way and is led out to the left wall surface 2 g ′.
  • the intake port 2 f is formed upright so that the port axis f forms an angle of about 50 degrees with respect to the cylinder axis A, while the exhaust port 2 g has the port axis g with respect to the cylinder axis A. And is formed so as to form a substantially right angle.
  • the intake and exhaust camshafts 6 and 8 are provided with the variable valve lift mechanism.
  • FIG. 4 shows the intake side of the variable valve lift mechanism, and since the exhaust side has substantially the same structure, only the intake side will be described.
  • the variable valve lift mechanism includes a low-speed cam nose 6a and a high-speed cam nose 6b formed on the intake camshaft 6, an independently rotatable low-speed rocker arm 7a and a high-speed rocker arm 7b, And the high-speed rocker arm 7b can be idled or interlocked with the low-speed rocker arm 7a.
  • a hydraulic cylinder 21 having pistons 21a and 21a for driving the engaging pins 20 forward and backward.
  • the rotation of the camshaft 6 is transmitted only to the low-speed rocker arm 7a, and the lift amount of the intake valve 4 is small (see the right side of the cylinder axis A in FIG. 4).
  • the engagement pin 20 is engaged with the high-speed rocker arm 7 b by the hydraulic pressure supplied to the oil chamber 21 b of the cylinder section 21, and the rotation of the cam shaft 6 is transmitted to the high-speed rocker arm 7 b. This increases the lift of the intake valve 4 (see the left side of the cylinder axis A in FIG. 4).
  • the in-cylinder fuel injection device includes a fuel injection valve 40 for injecting fuel into each cylinder, and a fuel pump 41 for supplying high-pressure fuel to each fuel injection valve 40.
  • the fuel injection valve 40 is positioned vertically below the two intake boats 2 f of the cylinder head 2 and is inclined so as to be substantially parallel to the port axis f of the intake port 2 f.
  • the injection port 40a of the fuel injection valve 40 faces the center of the combustion chamber.
  • the cylinder head 2 includes a head body 10 in which the intake and exhaust ports 2 f and 2 g are formed, and a cam in which the intake and exhaust cam shafts 6 and 8 and the rocker arms 7 and 9 are arranged.
  • the carrier 11 is divided into a carrier 11 and a lower surface 11 f of the force carrier 11 is placed on the receiving surface 10 f of the head body 10.
  • the cam carrier 11 is a cam port described later.
  • the bolts 43 are connected to the head body 10 together with the cam caps 15 and 16 by bolts.
  • An outer peripheral wall 10a is formed on the head main body 10 so as to surround the outer peripheral portion of the cam carrier 11. This head is attached to the upper mating surface 2a of this outer peripheral wall 10a.
  • the lower mating surface 3a of the cover 3 is mounted and fixed with an oil seal 13 interposed therebetween, whereby an oil-tight cam chamber 14 is formed.
  • the cam carrier 11 extends in the direction perpendicular to the camshaft so as to cross the cylinder axis A, and one journal receiving portion 11a per cylinder and a lateral wall portion 11c extending between the cylinders and extending in the direction perpendicular to the camshaft. And a vertical wall portion 11b that extends in the cam axis direction and connects the adjacent journal receiving portion 11a and the horizontal wall portion 11c.
  • the intake-side and exhaust-side cam caps 15 and 16 are attached to the intake-side upper mating surface 11d and the exhaust-side upper mating surface 11e of each of the journal receiving portions 11a.
  • An intake-side cam journal receiving hole 17 is formed between each intake-side upper mating surface 11 d and a lower-side mating surface 15 a of the intake-side cam cap 15, and each cam journal receiving hole 17 is formed. Thereby, the journal portion of the suction cam shaft 6 is rotatably supported.
  • An exhaust-side cam journal receiving hole 18 is formed between the exhaust-side upper mating surface 1 1 e and the lower-side mating surface 16 a of the exhaust-side cam cap 16.
  • the journal of camshaft 8 is rotatably supported.
  • a plug hole 23 penetrating through the head body 10 and communicating with the combustion recess 2c is formed in a portion of each of the journal receiving portions 11a facing the cylinder axis A.
  • An ignition plug 24 is inserted into the plug hole 23, and the ignition plug 24 is detachably attached to the head body 10 so that an electrode portion of the ignition plug 24 is located in the combustion recess 2c. ing .
  • the plug center line B of the plug hole 23 is formed so as to be slightly deviated from the cylinder axis A toward the exhaust side.
  • a plug pipe 25 is inserted into the plug hole 23, and a lower end 25 a of the plug pipe 25 is press-fitted and fixed in a plug hole 23 a of the head body 10.
  • the upper end 25b of the plug pipe 25 projects outside through a pipe hole 3b formed in the head cover 3, and an oil-tight space is formed between the pipe hole 3b and the plug pipe 25. Sealed to.
  • the inside of the plug pipe 25 and the cam chamber 14 are defined, and the replacement of the spark plug 24 can be performed without removing the head cover 3. It is becoming possible to obtain.
  • the spark plug At the outer end of the plug pipe 25, the spark plug
  • An ignition coil 26 connected to the terminal electrode 24 is detachably mounted.
  • a concave portion 10b is formed on both sides of the journal receiving portion 11a of the receiving surface 10f of the head body 10 described above.
  • intake and exhaust side valve seat portions 10c and 10d are bulged and formed.
  • Each of the valve seat portions 10c and 10d has an intake and exhaust port.
  • Valve guide holes 10 g and 10 g communicating with 2 f and 2 g are formed.
  • the valve shafts 4a and 5a of the intake and exhaust valves 4 and 5 are slidably inserted into the valve guide member 30 press-fitted into the respective valve guide holes 10g.
  • Valve parts 4b and 5b for opening and closing the intake and exhaust openings 2d and 2e are formed at the lower ends of the valve shafts 4a and 5a, and the rockers are provided at the upper ends via valve chips 3 and 31. Rooms 7 and 9 are in contact.
  • Spring retainers 32, 33 are fixed to the upper ends of the intake and exhaust valve shafts 4a, 5a by taper fitting.
  • valve spring support structure of the present embodiment will be described.
  • An exhaust spring receiving seat 1Oh is formed on the periphery of the valve guide hole 10g of the exhaust side valve seat 10d.
  • An exhaust knob spring 35 is disposed between the spring seat 10h and the exhaust side spring retainer 33, and the exhaust valve 5 is urged in the closing direction by the valve spring 35. .
  • Inner and outer intake spring receiving seats 10j and 10k are formed at the periphery of the valve guide hole 10g of the intake side valve seat portion 10c.
  • An inner spring 36 is provided between the inner positioning portion 3 2a of the intake-side spring retainer 32 and an outer spring receiving seat 10k and the outer positioning portion 3 2b of the spring retainer 32 are provided.
  • An outer spring 37 shorter than the spring length of the inner spring 36 is coaxially disposed between the springs 36 and 36.
  • the intake valve 4 is urged in the closing direction by 3 7.
  • the inner spring seat 10 j is located lower than the outer spring seat 10 k. It is formed in the shape of a step. As a result, the spring length of the inner spring 36 is longer than the spring length of the outer spring 37, in other words, the outer spring 37 is shortened while ensuring the required set load ⁇ maximum load during lift. . Since the inner and outer spring seats 10j and 10k are simultaneously processed by the cutting tool corresponding to the step, the number of processing steps does not increase.
  • the inner spring receiving seat 10j of the intake side valve seat portion 10c is formed in a stepped shape so as to be located lower than the outer spring receiving seat 10k. Therefore, while lowering the position of the intake-side spring retainer 32, the necessary spring length of the inner spring 36 can be secured, and the cylinder axial dimension of the cylinder head 2 can be reduced.
  • the required set load and maximum load can be secured while forming the outer spring seat 10 k at a high place, so that the fuel injection valve is provided below the intake port 2 f of the cylinder head 2. Even when 40 is arranged, it is possible to suppress an increase in the height of the cylinder head 2. That is, when the fuel injection valve 40 is arranged below the intake port 1f, a bulging portion for securing a space for arranging the fuel injection valve 40 easily swells on the inner surface of the intake port, which is avoided. To do this, it is necessary to raise the intake port 2 f.
  • the spring length of the inner spring 36 can be increased, so that the length of the outer spring 37 is short, and it is not necessary to raise the position of the spring retainer 32.
  • the cylinder head An increase in the height dimension of 2 can be suppressed.
  • the cam carrier 11 passes through the intake and exhaust port cap shafts 50, 51 extending in parallel with the cam shafts 6, 8 so as to penetrate the journal receiving portion 11a and the lateral wall portion 11c. ing.
  • the rocker shafts 50 and 51 are the same as those of the cam carrier 11 above.
  • Locking screws (fixing means) 52 screwed to the horizontal wall portion 11c located between the cylinders are positioned and fixed so that they cannot rotate.
  • the rocker shafts 50, 51 rotatably support the intake / exhaust port intake arms 7, 9, respectively.
  • the intake and exhaust side rocking shafts 50 and 51 are disposed inside the intake and exhaust valves 4 and 5, respectively.
  • the intake and exhaust side rocker shafts 50 and 51 are arranged symmetrically with respect to the Bragg center line B deviated from the cylinder axis A to the exhaust side. As a result, the intake side rocker shaft 50 and the cylinder are aligned with each other.
  • the distance from the axis A is smaller than the distance between the exhaust side rocker shaft 51 and the cylinder axis A.
  • Each of the intake and exhaust side rocker shafts 50 and 51 is disposed near the plug axis B such that the inner half thereof overlaps the plug pipe 25 when viewed in the camshaft direction.
  • Escape recesses 50a and 51a are formed in the overlapping portions of the rocker shafts 50 and 51 with the plug pipe 25. These escape recesses 50 a and 51 a are cut out along the outer peripheral surface of the plug pipe 25 so as to form an arc shape in plan view.
  • the rocker arm and the like are assembled according to the following procedure.
  • Rocker arms 7, 9 are located on both sides of the journal receiving portion 11a of the cam carrier 11, and the rocker shaft 50 is positioned so that the collars 50b, 51b are located between them and the side wall portion 11c.
  • 51, the locking force shafts 50, 51 are released, and the concave portions 50 &, 5 la are rotated so as to face the cylinder center side, and locked with the lock screw 52.
  • this assembly is mounted on the receiving surface 10 f of the head body 10 so that the escape recesses 50 a and 51 a do not interfere with the plug pipe 25, and the camshafts 6 and 8 are mounted.
  • cam carrier 11 can be detached from the head body 10, and the externally mounted power shafts 50, 51 and rocker arms 7, 9 can be attached to the head body 10 before mounting.
  • assembly workability can be improved.
  • rocker shafts 50 and 51 escape to form recesses 50 a and 51 a, respectively. Since the lock screw 52 is fixed to the angular position corresponding to 5, the work of mounting the cam carrier 11 to the head body 10 can be easily performed.
  • the intake and exhaust side rocker shafts 50 and 51 are arranged such that the inner halves overlap the plug pipe 25 when viewed in the camshaft direction. Since relief recesses 50a, 51a are formed in the overlapping portion of the 51 with the Bragg pipe 15, each rocker shaft 50, 51 is connected to the cylinder axis A by the clearance recesses 50a, 51a.
  • the valve can be placed closer to the side, and the valve pinch angle can be reduced accordingly. As a result, the shape of the combustion chamber can be improved and the entire engine can be made more compact.
  • each of the above-mentioned rocking shafts 50 and 51 can be brought closer to the cylinder axis A side, the rising angle of the intake port 2 f can be increased, and therefore, the intake port 2 f of the cylinder head 1 can be increased.
  • the fuel injection valve 40 is arranged below the fuel injection valve 40, the swelling of the inner surface of the intake passage for securing a space for disposing the fuel injection valve 40 can be eliminated, and the intake resistance can be reduced.
  • the suction arms 7 and 9 on the intake and exhaust sides are respectively provided with bases 7 (1 and 9d having support holes 7c and 9 (through which the shafts 50 and 51 are passed) and bases 7d and
  • the arm tip 7 e, 9 e extends outwardly following 9 d, and the valve tip 31 is in contact with the lower surface of the tip of the arm section 7 e, 9 e.
  • the tip of 9e is formed to be thick in the valve opening and closing direction, and pin holes 7g and 9g are formed in the thick portions 7f and 9f, into which the above-described engagement pins 20 are inserted. Have been.
  • each of the slipper surfaces 7h, 9h has an arc shape with a radius R as shown in Fig. 12, and the bases 7d, 9h are within a circle r extending from the slipper surfaces 7h, 9h. d and the arm portions 7e and 9e are located.
  • the slipper surfaces 7 h and 9 h are formed by performing a polishing process by rotating a polishing blade (not shown) along the circle r.
  • the slipper surfaces 7 h and 9 h of the intake and exhaust side rocker arms 7 and 9 are formed into an arc shape having a radius R, and the base is formed inside a circle r formed by extending the slipper surfaces 7 h and 9 h. Since the 7d, 9d and the arm portions 7e, 9e are located, the polishing tool can be rotated and moved along the circle r, and the desired surface roughness and processing accuracy can be obtained. Polishing can be performed in a short time, and the processing cost can be reduced. That is, as shown by the two-dot chain line in FIG.
  • the fuel pump 41 includes a pump body 41 a having a fuel suction port and a discharge port (not shown), a driving section 41 b having a plunger 41 c, the driving section 41 b and the pump body 41 a
  • the plunger 41c is reciprocatingly driven to pressurize the fuel, thereby forming a fuel supply pipe and a fuel rail (not shown).
  • the fuel is fed to each of the fuel injection valves 40 through the above.
  • the fuel pump 41 is disposed above the exhaust camshaft 8 between the two cylinders, and the plunger 41c is provided on the exhaust camshaft 8 at three cam nozzles 8a formed at intervals of 120 degrees. Driven by
  • the fuel pump 41 is mounted and fixed to the cam carrier 11 of the cylinder head 2 via a bracket 42 through a mounting hole 3 d formed in the top wall of the head cover 3. I have.
  • the bracket 42 is made of aluminum die-cast, and is adjacent to the main body 42 b having the mounting hole 42 a to which the driving part 41 b is mounted, and the exhaust camshaft 8.
  • a base portion 42 c having a rectangular shape in plan view formed so as to straddle the cam caps 16, 16 which are fitted with each other.
  • a bolt hole 4 2 d is formed in each corner of the base portion 42 c. Is shaped Has been established.
  • the base portion 42c is fixed to the cam carrier 11 together with the cam caps 16 by the cam bolts 43 inserted into the bolt holes 42d.
  • the main body portion 4 2b has a substantially rhombic shape in plan view, and has a large-diameter portion 4 2e facing the peripheral portion of the mounting hole 3d on the lower surface of the head cover 3 with a slight gap therebetween.
  • the small-diameter portion 42 f projects from the mounting hole 3 d to the outside of the head cover 3, and fixing bolts 44, 44 are implanted at both ends of the small-diameter portion 42 f.
  • a relief recess 42b 'for preventing contact with the camshaft 8 is provided on the lower surface of the main body 42b.
  • a circumferential groove 42g is formed on the outer peripheral portion of the large diameter portion 42e.
  • a rubber seal member 45 is mounted in the peripheral groove 42g, and the rubber seal member 45 is in contact with the peripheral portion of the mounting hole 3d. As a result, the space between the mounting hole 3 d and the bracket 42 is oil-tightly sealed.
  • the fuel pump 41 has a mounting flange portion 41 d which has a small-diameter portion 42 f of the bracket 42 with a gasket 46 interposed therebetween, and is fixed to the bracket 4 by fixing bolts 44 and nuts 47. Fixed to 2.
  • the fuel pump 41 is arranged obliquely such that its axis A1 is inclined outward with respect to the cylinder axis A (see FIG. 5).
  • the gasket 46 is formed by arranging a thin metal plate on both surfaces of a resin member, whereby the fuel pump 41 and the bracket 4 are oil-tightly sealed.
  • the fuel pump 41 since the fuel pump 41 is directly fixed to the cam carrier 11 of the cylinder head 2 via the brackets 4 • 2, the fuel carrier 4 1 having high strength and rigidity is provided with fuel.
  • the pump 41 can be fixed, and the generation of noise due to the vibration of the fuel pump 41 can be suppressed as compared with the case where the pump 41 is fixed to the conventional head cover.
  • bracket 4 since only bracket 4 needs to be added, the increase in cost can be suppressed.
  • the fuel pump 41 is connected to the cam carrier 11 The fuel pump 41 and the camshaft 8 can be easily and reliably aligned.
  • the bracket 42 is composed of a main body 42 b to which the driving part 41 b of the fuel pump 41 is attached and a base part 42 c, and the base part 42 c Since the cam caps 16 and 16 together with the adjacent cam caps 16 and 16 are fixed together by the cam bolts 43, the mounting strength of the fuel pump 41 can be increased and the position with the cam shaft 8 can be improved. The alignment can be performed easily and reliably. In addition, since the cam bolt 43 for fastening the cam cap 16 to the cam carrier 11 is shared, an increase in the number of parts can be suppressed.
  • the fuel pump 41 can be retrofitted after the engine unit is assembled, and the assemblability can be improved. .
  • the fuel pump 41 is arranged so that its axis A1 is directed outward with respect to the cylinder axis A, the wiring of the spark plug 24 and the fuel and fuel above the head cover 3 are arranged. A space for arranging fuel pipes and the like to the injection valve 40 can be secured.
  • the fuel pump is directly fixed to the high-strength and rigid cylinder head, so that the noise caused by the vibration of the fuel pump is lower than when the fuel pump is fixed to the conventional head cover. Generation can be suppressed. Also attached to cylinder head It is only necessary to form a boss portion or add a bracket, thereby suppressing an increase in cost.
  • the structure in which the fuel pump is mounted on the cylinder head to which the camshaft is mounted is adopted, the positioning between the fuel pump and the camshaft can be performed easily and accurately.
  • a bracket including a main body and a base to which the driving unit of the fuel pump is attached is interposed, and the base is jointly fastened to the cam carrier together with the adjacent cam cap. Since the fuel pump is fixed, the mounting strength of the fuel pump can be increased, the positioning with the camshaft can be performed easily and reliably, and the cam port that fastens the cam cap to the cylinder head can be shared. The increase can be suppressed.
  • the main body of the bracket is exposed to the outside through the through hole of the head cover, and an elastic seal member is provided between the peripheral portion of the through hole and the main body.
  • the seal member With the seal member, the bracket and the head cover can be sealed oil-tight, and the vibration of the fuel pump can be suppressed from transmitting to the head cover. Can be prevented.
  • the fuel pump can be retrofitted to the main body after the engine unit is assembled, so that the assemblability can be improved.
  • the fuel pump is inclined outward with respect to the cylinder axis, so that a wiring space for a spark plug wiring, a fuel pipe, and the like can be secured above the head cover.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

L'invention concerne une structure de montage de pompe de carburant pour moteur à injection de carburant, capable d'entraîner une pompe de carburant (41) qui alimente une soupape d'injection de carburant (40) par la came d'un arbre à came (8). La pompe (41) est introduite dans un orifice de montage (3d) formé sur un capot (3) et fixée au support de came (11) de tête de cylindre (2) par le biais d'une patte (42).
PCT/JP2003/005800 2002-05-10 2003-05-08 Structure de montage de pompe de carburant pour moteur a injection de carburant WO2003095824A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2002135762 2002-05-10
JP2002-135762 2002-05-10
JP2003009478A JP4139693B2 (ja) 2002-05-10 2003-01-17 燃料噴射式エンジンの燃料ポンプ取付け構造
JP2003-009478 2003-01-17

Publications (1)

Publication Number Publication Date
WO2003095824A1 true WO2003095824A1 (fr) 2003-11-20

Family

ID=29422397

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2003/005800 WO2003095824A1 (fr) 2002-05-10 2003-05-08 Structure de montage de pompe de carburant pour moteur a injection de carburant

Country Status (2)

Country Link
JP (1) JP4139693B2 (fr)
WO (1) WO2003095824A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2093392A3 (fr) * 2008-02-19 2010-05-19 Yamaha Hatsudoki Kabushiki Kaisha Moteur à combustion interne à quatre temps
US7814891B2 (en) * 2007-12-13 2010-10-19 Hyundai Motor Company Fuel pump set
JP2012229662A (ja) * 2011-04-26 2012-11-22 Toyota Boshoku Corp 燃料ポンプの取付構造

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4603405B2 (ja) * 2005-04-08 2010-12-22 ヤマハ発動機株式会社 鞍乗型車両
JP5163458B2 (ja) * 2008-12-05 2013-03-13 日産自動車株式会社 内燃機関
KR101033321B1 (ko) * 2009-04-24 2011-05-09 현대자동차주식회사 펌프 브래킷
KR101534693B1 (ko) * 2009-05-12 2015-07-07 현대자동차 주식회사 연료펌프세트를 구비한 가솔린 직분사 엔진
WO2012028893A2 (fr) 2010-08-31 2012-03-08 Matrahazi Janos Turbine éolienne
KR101219860B1 (ko) 2010-09-29 2013-01-08 현대자동차주식회사 가솔린 직접 분사 엔진용 고압 연료펌프의 설치구조
JP5811760B2 (ja) * 2011-04-26 2015-11-11 トヨタ紡織株式会社 燃料ポンプの取付構造
JP5910149B2 (ja) * 2012-02-17 2016-04-27 スズキ株式会社 車両用エンジンの燃料ポンプ装置
JP2013181521A (ja) * 2012-03-05 2013-09-12 Toyota Motor Corp 高圧燃料ポンプの駆動装置
JP2019210880A (ja) * 2018-06-06 2019-12-12 本田技研工業株式会社 鞍乗り型車両用内燃機関
SE542805C2 (sv) * 2018-07-31 2020-07-14 Hedman Ericsson Patent Ab Elektriskt aktiverad ventilaktuator för en internförbränningsmotor

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000291503A (ja) * 1999-04-08 2000-10-17 Toyota Motor Corp 高圧燃料ポンプの取付け構造
US20010013336A1 (en) * 2000-01-14 2001-08-16 Nobuaki Takasaki Fuel supply device for direct injection engine
JP2002061549A (ja) * 2000-08-22 2002-02-28 Mitsubishi Motors Corp 燃料ポンプ取付け構造

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000291503A (ja) * 1999-04-08 2000-10-17 Toyota Motor Corp 高圧燃料ポンプの取付け構造
US20010013336A1 (en) * 2000-01-14 2001-08-16 Nobuaki Takasaki Fuel supply device for direct injection engine
JP2002061549A (ja) * 2000-08-22 2002-02-28 Mitsubishi Motors Corp 燃料ポンプ取付け構造

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7814891B2 (en) * 2007-12-13 2010-10-19 Hyundai Motor Company Fuel pump set
EP2093392A3 (fr) * 2008-02-19 2010-05-19 Yamaha Hatsudoki Kabushiki Kaisha Moteur à combustion interne à quatre temps
JP2012229662A (ja) * 2011-04-26 2012-11-22 Toyota Boshoku Corp 燃料ポンプの取付構造

Also Published As

Publication number Publication date
JP2004028079A (ja) 2004-01-29
JP4139693B2 (ja) 2008-08-27

Similar Documents

Publication Publication Date Title
WO2003095824A1 (fr) Structure de montage de pompe de carburant pour moteur a injection de carburant
WO2003095804A1 (fr) Structure de soutien d'un ressort de vanne de moteur
JP3887086B2 (ja) 内燃機関の燃料系搭載構造
EP1344930B1 (fr) Moteur à combustion interne avec soupape d'injection de carburant
JP2004028081A (ja) エンジンのロッカシャフト配置構造
TWI248491B (en) Rotation prevention device for rocker arm shaft
JP2004028082A (ja) エンジンの動弁機構
EP1452699B1 (fr) Dispositif a butee tourbillon pour axe de culbuteur d'un mecanisme de soupapes de moteur a combustion interne
JP2002276308A (ja) ４サイクルエンジンのカム軸支持構造
US11352915B2 (en) Cylinder head
JP3714465B2 (ja) 内燃機関の一体型カムホルダ
US10286988B2 (en) Outboard motor and marine vessel
JPH09264153A (ja) エンジンの補機取付構造
JP2013113158A (ja) 内燃機関のヘッドカバー構造
JP3722177B2 (ja) 筒内噴射ガソリンエンジン
JPH06117327A (ja) エンジンのシリンダヘッド構造
JP3142616B2 (ja) 内燃機械の潤滑装置
US10087880B2 (en) Engine and straddled vehicle
JP3275774B2 (ja) エンジンのカムキャップ構造
JPH11324865A (ja) 直噴式多気筒ディーゼルエンジン
JPH11107854A (ja) 内燃機関
JPH09264225A (ja) 直噴式エンジンの燃料配管構造
JPH06146822A (ja) エンジンのシリンダヘッド構造
JPH03115712A (ja) エンジンの動弁装置
JPH082451Y2 (ja) エンジンのシリンダヘッド

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LU MC NL PT SE SI SK TR

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
122 Ep: pct application non-entry in european phase