Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
  • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
  • F02M59/46—Valves
• • 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
  • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
  • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
  • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
• • 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
  • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
  • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
  • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
  • F02M45/08—Injectors peculiar thereto
  • F02M45/083—Having two or more closing springs acting on injection-valve
• • 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
  • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
  • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
  • F02M61/042—The valves being provided with fuel passages
  • F02M61/045—The valves being provided with fuel discharge orifices
• • 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
  • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
  • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
  • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
• • 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
  • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
  • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14

Definitions

• the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
• a fuel injector known from DE 41 01 235 Cl, has a valve body which is connected to a valve holding body by means of a clamping nut.
• a bore is formed in the valve body, in which a valve member is arranged to be axially movable against the force of two closing springs. The valve member closes at its end on the combustion chamber side
• the valve member projects away from the combustion chamber with a spring tappet into a spring chamber which receives the closing springs and is formed in the valve holding body.
• the first closing spring arranged in the section of the spring chamber facing away from the valve member is supported with its end facing the valve member via a spring plate on the spring tappet of the valve member and with its other end on the end of the spring chamber facing away from the valve member.
• the second closing spring which is arranged in the section of the spring chamber facing the valve member, is supported on its side facing the valve member on a side through the Valve member movable spring plate from and at the other end to a support disc fixed in the spring chamber.
• the fixation is done by caulking the wall of the spring chamber against the support disk and disadvantageously requires a lot of space because of the thick support disk in this case. In addition, the support disc cannot be removed non-destructively.
• the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that the support plate is supported only on parts of its circumference on the valve holding body by protruding into the area of the grooves, thereby reducing the space required in the valve holding body. Because the one side is freely accessible during assembly of the fuel injector, the support plate can be easily inserted.
• the spring chamber is designed as a central bore and the grooves are formed by blind bores which are smaller in diameter and can be carried out easily and inexpensively and which are arranged around the central bore.
• the blind holes are made before drilling the central bore and are arranged so that their surfaces overlap with that of the central bore. After the central bore has been drilled, grooves with a crescent-shaped cross section result on its wall.
• these blind bores can be distributed evenly or unevenly over the circumference of the central bore. This ensures that the fuel supply line, which must be led through the wall surrounding the spring chamber, extends between the blind bores. space. A very slim valve holding body can thus be realized.
• the support disk has a chamfer at its edge, so that the support disk comes into positive contact with the bottom surfaces of the grooves formed by blind holes without the bottom surfaces of the blind holes having to be reworked.
• the bottom surface of bores is conical when using conventional drilling tools. After drilling the central bore forming the spring chamber, the crescent-shaped bottom surfaces thus have a bevel. If the support disc is provided with a chamfer which has approximately the same angle as the base surface, the support disc bears in a form-fitting manner against the base surface without the base surfaces of the blind holes having to be reworked.
• FIG. 1 shows a first embodiment of the fuel injection valve with an inwardly opening valve member in partial longitudinal section with an outwardly opening valve member
• FIG. 2 shows a second embodiment of the fuel injection valve in longitudinal section
• FIG. 3 shows a cross section through the fuel injection valve along the line III-III of FIG FIG. 1 or FIG. 2
• FIG. 4 shows an enlarged detail from FIG. 1 in the area of the spring chamber
• 5a and 5b show two different exemplary embodiments of the bottom surfaces of the grooves
• FIG. 6 shows an exemplary embodiment of the supporting disc with straight edges
• FIG. 7 shows an exemplary embodiment of the supporting disc with chamfered edges.
• FIG. 1 shows a first exemplary embodiment of a fuel injection valve according to the invention.
• a valve body 1 is clamped against a valve holding body 6 with the interposition of an intermediate disk 3.
• a bore 2 is formed in the valve body 1, in which a piston-shaped, axially movable valve member 4 is guided over part of its length.
• the valve member 4 controls at least one injection opening 5 on its combustion chamber end, which connects it to an inlet channel 10 formed in the valve body 1 and in the valve holding body 6 during the opening stroke movement.
• the inlet channel 10 is connected to a high-pressure fuel pump via a high-pressure inlet line, not shown in the drawing.
• An elongated spring chamber 16, 17 is arranged in the valve holding body 6 and is divided into a first spring chamber 16 facing away from the combustion chamber and a second spring chamber 17 facing away from the combustion chamber by means of a support disk 25 arranged approximately at its middle height, the first spring chamber 16 via an outlet channel 11 is connected to a drain line, not shown in the drawing.
• the spring chamber 16, 17 is connected to the bore 2 by an opening 18 formed in the intermediate disk 3, and the first 16 and second spring chamber 17 are connected to each other by a passage opening 36 formed in the support disk 25.
• the valve member 4 has a spring plunger 13 which is smaller in diameter and which is disc 3, the second spring chamber 17 and the support plate 25 protrudes into the first spring chamber 16, the spring plunger 13 being guided in the passage opening 36 of the support plate 25.
• a first spring plate 28 is arranged, between the and the end of the first spring chamber 16 facing away from the combustion chamber, a first closing spring 20 is arranged, which biases the first spring plate 28 and thus also the valve member 4 in the direction of the spring plunger 13 to the combustion chamber.
• a stop sleeve 7, which surrounds the spring plunger 13, is guided in the intermediate disk 3 and protrudes into the second spring chamber 17 and a second spring plate 29 comes to rest against the end thereof remote from the valve member 4. Between the support plate 25 and the second spring plate 29 is under
• a second closing spring 21 preferably designed as a helical compression spring, which presses the stop sleeve 7 against the valve body 1.
• the stop sleeve 7 is axially movable in the opening 18 of the washer 3 against the closing force of the second closing spring 21.
• a stop surface 14 is formed on the stop sleeve 7, against which the valve member 4 comes to rest during part of the maximum stroke during its opening stroke movement.
• a stop shoulder 23 is formed in the intermediate disk 3, which shoulder is formed by reducing the diameter of the opening 18 towards the spring chamber 16, 17 and against which the stop sleeve 7 comes to rest against the force of the second closing spring 21.
• the bottom surfaces 34 are at the same height of the spring space 16,17 arranged in a common radial plane to the longitudinal axis of the spring space 16,17, whereby the support disc 25 lying on the bottom surfaces 34 is aligned perpendicular to the longitudinal axis of the spring space 16,17.
• FIG. 1 A further exemplary embodiment of the fuel injection valve according to the invention is shown in FIG.
• a piston-shaped valve member 4 is axially displaceably arranged in a bore 2, which is formed in a valve body 1.
• the valve body 1 is clamped against a valve holding body 6 by means of a clamping nut 8 and a valve connecting body 50 is fastened to the valve holding body 6 at the end facing away from the combustion chamber by means of a clamping nut 52.
• the valve member 4 is guided in a section of the bore 2 facing away from the combustion chamber and merges into a closing head 40 likewise guided in the bore 2 on the combustion chamber side. Since the closing head 40 is larger in diameter than the valve member 4, a pressure shoulder 41 is formed on the closing head 40.
• valve member 4 The part of the valve member 4 between the guided sections is surrounded by a pressure chamber 42, which can be filled with fuel under high pressure via an inlet channel 10 formed in the valve holding body 6 and the valve body 1 and a high-pressure inlet line, not shown in the drawing.
• a pressure chamber 42 which can be filled with fuel under high pressure via an inlet channel 10 formed in the valve holding body 6 and the valve body 1 and a high-pressure inlet line, not shown in the drawing.
• an injection channel 44 is formed, the injection opening 45 arranged on the lateral surface of the closing head in the closed position of the valve member 4, that is, when the closing head 40 rests on the end face 46 of the valve body 1, is closed by the valve body 1 and via which injection channel 44 in the to the outside, towards the combustion chamber toward the opening stroke movement of the valve member 4, the pressure chamber 42 is connected to the combustion chamber.
• a spring chamber 16 is formed in the valve holding body 6, in which a spring tappet 13 is arranged, which is connected to the valve member 4 on the combustion chamber side and a spring plate 28 is arranged on the end remote from the combustion chamber.
• a plurality of grooves 32 of equal length are formed, which extend from the end of the valve holding body 6 facing away from the combustion chamber to a certain height of the spring chamber 16.
• a support disk 25 comes to rest, which has a passage opening 36 for guiding the spring plunger 13.
• a closing spring 20 preferably designed as a helical compression spring, is arranged under prestress. Due to the force of the closing spring 20, the spring plate 28 is urged away from the combustion chamber and the valve member 4 with the closing head 40 is thus also pressed against the end face 46 of the valve body 1 via the spring tappet 13.
• a ring shoulder 48 is formed on the spring plunger 13 facing away from the combustion chamber and facing the support disk 25, the outer diameter of which is larger than the diameter of the passage opening 36 of the support disk 25.
• This ring shoulder 48 arrives during the outward opening stroke movement of the valve member 4 the support disc 25 to the system and thereby limits the opening stroke of the valve member 4 to a maximum stroke.
• the support disk 25 is introduced into the spring chamber 16 before the valve connecting body 50 is mounted on the valve holding body 6. Since the support disc 25 also serves as a limitation of the maximum opening stroke, the desired maximum opening stroke can easily be set by a corresponding thickness of the support disc 25.
• Injection opening emerges from hole 2.
• the pressure chamber 42 is thus connected to the combustion chamber and fuel is injected into the combustion chamber.
• the opening stroke movement of the valve member 4 is continued until the ring shoulder 48 comes to rest on the support disk 25.
• the closing movement is initiated in that the pressure in the pressure chamber 42 drops until the resulting force on the pressure shoulder 41 of the closing head 40 is less than the force of the closing spring 20, whereby the valve member 4 is moved back into the bore 2 by the closing spring 20, until the closing head 40 rests on the end face 46 of the valve body 1.
• the injection opening 44 is closed again by the valve body 1 and the injection of the fuel into the combustion chamber is stopped.
• the support plate 25 is pressed against the bottom surfaces 34 of the grooves 32 during the entire injection cycle with the force of the closing spring, so that the support plate 25 does not move.
• FIG. 3 shows a cross section through the spring chamber 16, 17 of the fuel injection valve along the line III-III of the FIGS. gur 1 and Figure 2 shown, the closing spring 20,21 has been omitted in Figure 3.
• the grooves are formed by three blind bores 32 ', which are smaller in diameter than the diameter of a subsequently introduced bore which creates the spring space 16, 17.
• the cross sections of the blind bore 32 ' overlap with the bore forming the spring space 16, 17, so that a crescent-shaped cross-sectional area of the grooves 32 results.
• FIG. 3 shows the position of the inlet channel, which is arranged in the intermediate area of two grooves 32 and thus has the required wall thickness for the passage of fuel under high pressure, without reserving any special space for itself.
• FIG. 4 shows an enlargement of FIG. 1 in the area of the grooves 32 and in FIGS. 5a and 5b enlargements of FIG. 4 in the area of the bottom surfaces 34.
• the holes drilled with it have a conical bottom surface 34.
• the bottom surfaces 34 of the grooves are chamfered and have a crescent-shaped cross section, as shown in FIG. 5a. If, instead, a floor surface 34 perpendicular to the longitudinal axis of the spring space 16, 17 is desired, it must be reworked accordingly or a milling tool used.
• FIG. 5 b shows the bottom surface 34 of such a reworked groove 32.
• FIG. 6 shows a support disk 25 according to the invention with an edge formed perpendicular to the support surfaces of the support disk 25.
• the shape of the support disk 25 is formed in that three circular surfaces with radius Rl are each offset by 120 degrees around a center point and are connected by transitions so that an approximately triangular surface with rounded corners and concavely curved sides is formed.
• a passage opening 36 is formed in the center of the support disk 25 and serves as a guide for the spring plunger 13.
• the support disk 25 formed in this way engages precisely in the grooves 32 formed by the blind bores due to the shape composed essentially of three circular surfaces, the radius of the blind bores being equal to or somewhat larger than the radius R1 of the circular surfaces.
• the support disk 25 comes into contact with the bottom surfaces 34 of the grooves 32 and is secured against twisting by engaging in the grooves 32.
• FIG. 7 shows a further exemplary embodiment of a support disk 25 according to the invention.
• the shape of the cross section is the same as that of the support disk shown in FIG. 6, but here the support disk 25 is provided with a chamfer 38 with a chamfer angle ⁇ which corresponds to the apex angle ⁇ of the drill used to produce the grooves 32.
• the support disk 25 arrives in a form-fitting manner on the bottom surface 34 of the groove 32, as shown in FIG. 5a.
• the support disc 25 can be almost on both sides so that assembly errors can be connected.
• the grooves 32 overall permit a compact, slim design of the injection valve.

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

Applications Claiming Priority (3)

Publications (1)

Family

ID=7925804

Family Applications (1)

Country Status (8)

Families Citing this family (3)

Family Cites Families (2)

• 1999
  • 1999-10-15 DE DE19949818A patent/DE19949818A1/de not_active Withdrawn
• 2000
  • 2000-09-27 CZ CZ20012116A patent/CZ20012116A3/cs unknown
  • 2000-09-27 JP JP2001533312A patent/JP2003513198A/ja active Pending
  • 2000-09-27 BR BR0007212-5A patent/BR0007212A/pt not_active IP Right Cessation
  • 2000-09-27 EP EP00975807A patent/EP1144860A1/de not_active Withdrawn
  • 2000-09-27 KR KR1020017007315A patent/KR20010093157A/ko not_active Application Discontinuation
  • 2000-09-27 WO PCT/DE2000/003394 patent/WO2001031194A1/de not_active Application Discontinuation
  • 2000-09-27 CN CN00802278A patent/CN1327513A/zh active Pending

Non-Patent Citations (1)

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