EP0606371B1 - A fuel injector for internal combustion engines - Google Patents
A fuel injector for internal combustion engines Download PDFInfo
- Publication number
- EP0606371B1 EP0606371B1 EP92921416A EP92921416A EP0606371B1 EP 0606371 B1 EP0606371 B1 EP 0606371B1 EP 92921416 A EP92921416 A EP 92921416A EP 92921416 A EP92921416 A EP 92921416A EP 0606371 B1 EP0606371 B1 EP 0606371B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- section
- valve
- foremost
- end section
- slide valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
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
- 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
- F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
- F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
-
- 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
- F02M61/166—Selection of particular materials
Definitions
- the invention relates to a fuel injector valve for internal combustion engines, including a hollow slide valve guide fixedly disposed in the external housing of the injector and the foremost end of which is designed as an atomizer closed in front and provided with a central bore, said atomizer having in its side wall a number of transversely extending nozzle holes for the injection of atomized fuel, a slide valve axially displaceable in the guide for opening and closing the nozzle holes and having a foremost section with a cylindrical end section carried by a shank and which is journalled with tight fit in the bore of the atomizer in order to close the nozzle holes when the valve is in the closed position; said injector valve having a flow passage through which pressurized fuel may flow past the slide valve and on to the nozzle holes when the slide occupies its opening position in which its end section exposes the holes, and a closure spring acting against the fuel pressure for holding the slide in its closing position; the axial length of the end section of the slide valve being at most of the same order of magnitude as the diameter of the bore in
- DK patent No. 149 141 deals with a fuel injector valve, wherein the slide valve and its foremost section which project down into the atomizer are comparatively rigid in the transverse direction, thereby requiring the slide be mounted completely coaxially with the bore in the atomizer. Even a very slight failing alignment between the slide and the atomizer bore may entail failure in the fuel injector valve.
- the rearmost slide valve section journalled in the valve guide has a comparatively large diameter and is ground to size to fit into the valve guide whereas the foremost slide section projecting down into the bore of the atomizer has a smaller diameter and is ground to size so that the cylindrical end section is journalled with tight fit within the atomizer bore.
- the end section In order to ensure tight barring of the nozzle holes, even when the fuel pressure in the flow passage immediately before and after the actual fuel injection attains very high values, such as 800 to 1000 bar, the end section must fit extremely precisely in the atomizer bore and, consequently, the clearance between the end section and the bore typically amounts to 10 to 15 »m.
- the slide valve consisting of steel has been hardened to a glass-hard state, meaning that the handling as well as the grinding of the slide valve must be effected very cautiously in order to prevent the slide valve from breaking as a consequence of its brittleness.
- This circumstance in unison with the high demands for coaxiality and tolerances of the ground surfaces result in that the slide valve is expensive to manufacture.
- the entire slide valve has to be exchanged when the end section is worn down. The dispatch and exchange of the slide valve is also difficult due to the brittleness of the slide because even a rather slight transverse impingement may cause breaking of the slide valve.
- a fuel injector valve of the initially mentioned kind is known from DE-A-28 37 606.
- the foremost section is here slidably journalled in the remainder of the slide valve and includes in addition to the cylindrical end section a long cylindrical upper section which slides against an internal cylindrical surface in the remainder of the slide valve.
- the cylindrical upper section serves to keep the foremost section completely coaxial with the remainder of the slide valve during valve movements so that the end section is coaxial with the bore of the atomizer.
- the shank connecting the end section with the upper section has high stiffness towards bending.
- the slide valve as a whole is complicated to manufacture partly because the foremost section includes two separate cylindrical surfaces requiring grinding, partly because the foremost section is very long and thin.
- the fuel injector valve according to the invention is characterized in that the foremost section is fixed to the remainder of the slide valve and having a flexibility allowing the cylindrical end section to align itself with the bore, and that the cylindrical end section is the only part of the foremost section which slides against an associated surface during opening or closing of the valve. Due to the flexibility of the foremost section of the slide valve the bore in the atomizer automatically aligns the end section of the slide valve to its own longitudinal axis so that the end section does not necessarily have to be completely coaxial with the rearmost slide valve section journalled in the valve guide.
- the flexibility also has the advantage that the wearing of the end section and the atomizer will be diminished in relation to the wearing of the prior art injector in which even a very slight misalignment between the end section and the atomizer may result in seizing and rapid wearing of the atomizer.
- the foremost section of the slide valve may be manufactured independently of the rearmost section.
- this is utilized in facilitating the manufacturing of the slide valve in that the cylindrical external side of the foremost end section of the slide valve is finally ground to size independently of the grinding of other slide surfaces.
- the lifetime of the slide valve has further been enhanced by a preferred embodiment in which at least the foremost part of the cylindrical external surface of the end section consists of an erosion-resistant material, such as Stellite 6.
- the erosion-resistant material reduces the wearing of the front end of the end section that may occur when the end section by the opening of the injector valve exposes the nozzle holes, and the fuel starts flowing at very high velocities through the nozzle holes.
- the high flow velocities occurring at the opening of the valve immediately next to the extreme end of the end section apply heavy pressure loads thereon.
- the erosion-resistant material is capable of receiving said loads, thereby prolonging the lifetime of the slide valve.
- the fuel injector valve illustrated in Figs 1, 2 and 5 has an elongated external housing 1 which at its rearmost end has a head 2 by which the injector valve in a known manner may be mounted in the cylinder cover of an internal combustion engine and be connected with a fuel pump, not shown.
- the head 2 includes a fuel oil inlet 3 which is in flow connection with a duct 4 extending through a central thrust piece 5 and a valve member 6 journalled in a valve housing 7, the rearmost end of which abuts on a forwards facing shoulder on the thrust piece 5 and whose foremost end has a conical surface kept in tight abutment on a corresponding conical surface on a valve guide 8 which at its rearmost end fits tightly into housing 1 and carries at its foremost end an atomizer 9 projecting through housing 1 and into the combustion chamber of the engine cylinder, not shown, when the injector valve is mounted on the cylinder cover.
- a slide valve generally designated 10 is axially displaceable internally of the valve guide 8 and includes a rearmost section 11 whose cylindrical external surface is ground to size and journalled with tight fit in a central guide bore in valve guide 8.
- the slide section 11 carries a foremost slide section 12 that is substantially thinner than the rearmost section 11 and projects into a central bore 13 in the atomizer.
- a central tube 14 extending into the rearmost section of the slide valve is integral with the valve guide 8 and has a forwards facing shoulder restraining the rearwards movement of slide valve 10.
- a closure spring 16 rearwardly abutting on the valve guide 8 and forwardly on a rearwards facing shoulder 17 at the rear end of the slide valve section 11 is received in a hollow space 15 in the valve guide so that the closure spring loads the slide valve in the forwards direction towards the closing position shown in Fig. 2.
- the inlet duct 4 is through transverse bores and a following valve seat 18 in communication with a flow passage 19 extending through pipe 14 and discharging in front into a distributor chamber 20 provided in the slide valve and which chamber through transverse bores 21 is in flow connection with an annular chamber 22 defined between the external side of the slide valve and the surrounding parts of the valve guide.
- a conical seating 23 is formed in valve guide 8 at the foremost end of the chamber 22, and the slide valve is at the front end of section 11 provided with a corresponding conical seating 24 which in the closing position of the injector valve is urged sealingly in abutment on seating 23 by closure spring 16.
- the foremost section 12 of the slide valve is at its backwards end provided with a threaded portion 25 screwed into a central bore at the foremost end of the slide valve section 11 so that a rearwards directed shoulder 26 on section 12 abuts on the front end of section 11.
- a safety pin 27 inserted through unitary bores in slide valve sections 11 and 12 prevents the foremost section from unintentionally rotating clear of the rearmost section 11. This safety against releasing may also be effected in other ways, e.g. by glue, such as Loctite (reg. Trademark).
- the shoulder 26 merges forwardly into a comparatively thin and elongated shank 28 the foremost end of which carries an end section 29 with a cylindrical external surface 30 journalled tightly fitting into the bore 13 of the atomizer.
- nozzle holes 31 In the wall of the atomizer there is provided a number of transversely extending nozzle holes 31 so positioned that the end section 29 bars the nozzle holes when the injector valve is in the closing position illustrated in Fig. 2, whereas the end section 29 in the opening position of the injector valve (Fig. 1) has been moved so much backwards that the nozzle holes are completely exposed.
- valve member 6 When the valve member 6 abuts on the valve seat 18, preheated oil may over a transverse bore in thrust piece 5 flow through the injector valve and keep it heated.
- the valve member 6 When the pressure of the fuel oil in inlet 3 rises sharply immediately prior to initiating the injection, the valve member 6 is displaced to the rear into the position shown in Fig. 1 and bars the passage for circulating oil, following which the fuel oil flows past the valve seat 18 down through the passage 19 and out into chamber 22 in which the pressure in the oil builds up until it overcomes the force exerted by the closure spring 17 and the slide valve is moved rearwards from the closing position shown in Fig. 2.
- the fuel oil flows forwards into the space surrounding the shank 28 and passes through recesses 32 therein on to the part of the bore 13 positioned in front of the end section 29. Due to the fact that the end section 29 in the closed position of the injector extends a distance forwards past the nozzle holes 31, a pressure build-up is effected in the fuel oil in front of the end section 29 prior to exposing the nozzle holes, meaning that the fuel oil substantially from the beginning of the injection is injected at full pressure, thereby ensuring a good combustion.
- the foremost section 12 and the rearmost section 11 of the slide valve are ready-made as two separate units which are assembled only immediately before mounting the slide valve 10 in the injector valve.
- the comparatively thick slide valve section 11 may due to its large rigidity against transverse bending be processed at a high cutting force.
- the foremost section 12 is in the embodiment illustrated in Figs 2, 3 and 4 composed of two elements, viz. the shank 28 and a ring 33 consisting of an erosion-resistant material, such as Stellite 6.
- the shank 32 At its foremost end the shank 32 has a larger diameter and is there provided with three longitudinal recesses 32 distributed along the circumference and allowing, as mentioned, the fuel oil to pass internally past the ring 33.
- the recesses 32 leave in the foremost end of the shank three radially protruding lobes 34 to which the ring 33 is secured, for instance by means of hard soldering. Alloy 50 may be used as the solder.
- the foremost section 12 of the slide valve shall only be produced on a smaller scale, it may appropriately be implemented as shown in Figs 5 and 6.
- the foremost section is there manufactured from a single steel blank on the foremost end section and a distance up along the side, corresponding to the intended face for journalling in the bore 13 of the atomizer, of which a layer of erosion resistant material has been welded, such as Stellite 6.
- the shoulder 26 and the shank 28 are manufactured by turning and a central bore 35 that is longer than the cylindrical end section 29 is drilled from the front end of the blank.
- the portion 36 of the shank positioned behind the end section 29 and having a smaller diameter than the end section 29 but a larger diameter than the part of the shank 28 positioned behind, is subsequently provided with an appropriate number, e.g.
- the flow passage allowing the combustible to flow past the slide valve includes the recesses 32 of the embodiment illustrated in Fig. 2 whereas they include the grooves 37 and the bore 35 in the embodiment illustrated in Fig. 5.
- the sections may of course be assembled in another way, for instance by means of press fit or by a similar joining method.
- the shank may further be designed in another way, e.g. as a number of parallel and thin rods connecting the rearmost section of the shank with the end section 29.
- the essential feature of the shank according to the invention is its flexibility allowing the end section 29 to conform to the bore 13 independently of the journalling bearing of the rearmost slide valve section in the valve guide 8.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
- The invention relates to a fuel injector valve for internal combustion engines, including a hollow slide valve guide fixedly disposed in the external housing of the injector and the foremost end of which is designed as an atomizer closed in front and provided with a central bore, said atomizer having in its side wall a number of transversely extending nozzle holes for the injection of atomized fuel, a slide valve axially displaceable in the guide for opening and closing the nozzle holes and having a foremost section with a cylindrical end section carried by a shank and which is journalled with tight fit in the bore of the atomizer in order to close the nozzle holes when the valve is in the closed position; said injector valve having a flow passage through which pressurized fuel may flow past the slide valve and on to the nozzle holes when the slide occupies its opening position in which its end section exposes the holes, and a closure spring acting against the fuel pressure for holding the slide in its closing position; the axial length of the end section of the slide valve being at most of the same order of magnitude as the diameter of the bore in the atomizer, and the length of the shank being at least several times longer than the axial length of the end section, which foremost section is a separate element.
- The disclosure of DK patent No. 149 141 deals with a fuel injector valve, wherein the slide valve and its foremost section which project down into the atomizer are comparatively rigid in the transverse direction, thereby requiring the slide be mounted completely coaxially with the bore in the atomizer. Even a very slight failing alignment between the slide and the atomizer bore may entail failure in the fuel injector valve.
- The rearmost slide valve section journalled in the valve guide has a comparatively large diameter and is ground to size to fit into the valve guide whereas the foremost slide section projecting down into the bore of the atomizer has a smaller diameter and is ground to size so that the cylindrical end section is journalled with tight fit within the atomizer bore. In order to ensure tight barring of the nozzle holes, even when the fuel pressure in the flow passage immediately before and after the actual fuel injection attains very high values, such as 800 to 1000 bar, the end section must fit extremely precisely in the atomizer bore and, consequently, the clearance between the end section and the bore typically amounts to 10 to 15 »m. The demand for full coaxiality between the end section of the slide valve and the rearmost section journalled in the valve guide necessitates that the two sections are ground in the same setting-up and, consequently, the connection between the end section and the remainder of the slide valve must have such a high stiffness against transverse bending that the shearing force provided by the cutting force of the grinder does not result in any noticeable bending of the slide valve.
- Prior to grinding, the slide valve consisting of steel has been hardened to a glass-hard state, meaning that the handling as well as the grinding of the slide valve must be effected very cautiously in order to prevent the slide valve from breaking as a consequence of its brittleness. This circumstance in unison with the high demands for coaxiality and tolerances of the ground surfaces result in that the slide valve is expensive to manufacture. It is a further inconvenience that the entire slide valve has to be exchanged when the end section is worn down. The dispatch and exchange of the slide valve is also difficult due to the brittleness of the slide because even a rather slight transverse impingement may cause breaking of the slide valve.
- A fuel injector valve of the initially mentioned kind is known from DE-A-28 37 606. The foremost section is here slidably journalled in the remainder of the slide valve and includes in addition to the cylindrical end section a long cylindrical upper section which slides against an internal cylindrical surface in the remainder of the slide valve. The cylindrical upper section serves to keep the foremost section completely coaxial with the remainder of the slide valve during valve movements so that the end section is coaxial with the bore of the atomizer. The shank connecting the end section with the upper section has high stiffness towards bending. The slide valve as a whole is complicated to manufacture partly because the foremost section includes two separate cylindrical surfaces requiring grinding, partly because the foremost section is very long and thin.
- It is the object of the invention to provide a slide valve with a longer lifetime than the prior art slide valve and which is easier to manufacture, handle and exchange.
- For this purpose the fuel injector valve according to the invention is characterized in that the foremost section is fixed to the remainder of the slide valve and having a flexibility allowing the cylindrical end section to align itself with the bore, and that the cylindrical end section is the only part of the foremost section which slides against an associated surface during opening or closing of the valve. Due to the flexibility of the foremost section of the slide valve the bore in the atomizer automatically aligns the end section of the slide valve to its own longitudinal axis so that the end section does not necessarily have to be completely coaxial with the rearmost slide valve section journalled in the valve guide. The flexibility also has the advantage that the wearing of the end section and the atomizer will be diminished in relation to the wearing of the prior art injector in which even a very slight misalignment between the end section and the atomizer may result in seizing and rapid wearing of the atomizer.
- In view of the fact that it is no longer necessary that the mutually fixed foremost and rearmost end sections of the slide valve have to be completely coaxial, the foremost section of the slide valve may be manufactured independently of the rearmost section. In accordance with the invention this is utilized in facilitating the manufacturing of the slide valve in that the cylindrical external side of the foremost end section of the slide valve is finally ground to size independently of the grinding of other slide surfaces. By grinding the foremost comparatively thin end section in a separate setting-up, it is obtained that the risk of breaking the foremost, glass-hard slide valve section during grinding has been considerably reduced because this section only has to withstand the grinding force acting on the small end section.
- When the foremost slide valve section is worn down and must be exchanged, it is according to the invention possible merely to exchange the foremost slide valve section comprising the shank and the end section and thus allow the rearmost slide valve section to remain in operation, thereby reducing to a considerable degree the expenses incurred by the exchange and facilitating the dispatching and handling of the necessary spare parts.
- The lifetime of the slide valve has further been enhanced by a preferred embodiment in which at least the foremost part of the cylindrical external surface of the end section consists of an erosion-resistant material, such as
Stellite 6. The erosion-resistant material reduces the wearing of the front end of the end section that may occur when the end section by the opening of the injector valve exposes the nozzle holes, and the fuel starts flowing at very high velocities through the nozzle holes. The high flow velocities occurring at the opening of the valve immediately next to the extreme end of the end section apply heavy pressure loads thereon. The erosion-resistant material is capable of receiving said loads, thereby prolonging the lifetime of the slide valve. - Examples of embodiments of the invention will now be described in detail with reference to the schematical drawings, in which
- Fig. 1 is an axial section through an embodiment of the injector valve, the slide valve being shown in the opening position,
- Fig. 2 is an axial section on a larger scale through the foremost part of the injector valve illustrated in Fig. 1, the slide valve being shown in the closing position,
- Fig. 3 is a sectional view of a side elevation of the foremost section of the slide valve,
- Fig. 4 is a cross-section through the slide valve along the line IV-IV in Fig. 3,
- Fig. 5 is an axial view through the foremost part of a second embodiment of the injector valve, and
- Fig. 6 is a cross-section along the line VI-VI in Fig. 5 through the foremost section of the slide valve.
- The fuel injector valve illustrated in Figs 1, 2 and 5 has an elongated external housing 1 which at its rearmost end has a head 2 by which the injector valve in a known manner may be mounted in the cylinder cover of an internal combustion engine and be connected with a fuel pump, not shown. The head 2 includes a
fuel oil inlet 3 which is in flow connection with a duct 4 extending through acentral thrust piece 5 and avalve member 6 journalled in a valve housing 7, the rearmost end of which abuts on a forwards facing shoulder on thethrust piece 5 and whose foremost end has a conical surface kept in tight abutment on a corresponding conical surface on avalve guide 8 which at its rearmost end fits tightly into housing 1 and carries at its foremost end anatomizer 9 projecting through housing 1 and into the combustion chamber of the engine cylinder, not shown, when the injector valve is mounted on the cylinder cover. - A slide valve generally designated 10 is axially displaceable internally of the
valve guide 8 and includes arearmost section 11 whose cylindrical external surface is ground to size and journalled with tight fit in a central guide bore invalve guide 8. Theslide section 11 carries aforemost slide section 12 that is substantially thinner than therearmost section 11 and projects into acentral bore 13 in the atomizer. - A
central tube 14 extending into the rearmost section of the slide valve is integral with thevalve guide 8 and has a forwards facing shoulder restraining the rearwards movement ofslide valve 10. - A
closure spring 16 rearwardly abutting on thevalve guide 8 and forwardly on a rearwards facingshoulder 17 at the rear end of theslide valve section 11 is received in ahollow space 15 in the valve guide so that the closure spring loads the slide valve in the forwards direction towards the closing position shown in Fig. 2. - The inlet duct 4 is through transverse bores and a following
valve seat 18 in communication with aflow passage 19 extending throughpipe 14 and discharging in front into adistributor chamber 20 provided in the slide valve and which chamber throughtransverse bores 21 is in flow connection with anannular chamber 22 defined between the external side of the slide valve and the surrounding parts of the valve guide. Aconical seating 23 is formed invalve guide 8 at the foremost end of thechamber 22, and the slide valve is at the front end ofsection 11 provided with a correspondingconical seating 24 which in the closing position of the injector valve is urged sealingly in abutment onseating 23 byclosure spring 16. - The
foremost section 12 of the slide valve is at its backwards end provided with a threadedportion 25 screwed into a central bore at the foremost end of theslide valve section 11 so that a rearwards directedshoulder 26 onsection 12 abuts on the front end ofsection 11. Asafety pin 27 inserted through unitary bores inslide valve sections rearmost section 11. This safety against releasing may also be effected in other ways, e.g. by glue, such as Loctite (reg. Trademark). Theshoulder 26 merges forwardly into a comparatively thin andelongated shank 28 the foremost end of which carries anend section 29 with a cylindricalexternal surface 30 journalled tightly fitting into thebore 13 of the atomizer. - In the wall of the atomizer there is provided a number of transversely extending
nozzle holes 31 so positioned that theend section 29 bars the nozzle holes when the injector valve is in the closing position illustrated in Fig. 2, whereas theend section 29 in the opening position of the injector valve (Fig. 1) has been moved so much backwards that the nozzle holes are completely exposed. - When the
valve member 6 abuts on thevalve seat 18, preheated oil may over a transverse bore inthrust piece 5 flow through the injector valve and keep it heated. When the pressure of the fuel oil ininlet 3 rises sharply immediately prior to initiating the injection, thevalve member 6 is displaced to the rear into the position shown in Fig. 1 and bars the passage for circulating oil, following which the fuel oil flows past thevalve seat 18 down through thepassage 19 and out intochamber 22 in which the pressure in the oil builds up until it overcomes the force exerted by theclosure spring 17 and the slide valve is moved rearwards from the closing position shown in Fig. 2. Immediately after theseatings shank 28 and passes throughrecesses 32 therein on to the part of thebore 13 positioned in front of theend section 29. Due to the fact that theend section 29 in the closed position of the injector extends a distance forwards past thenozzle holes 31, a pressure build-up is effected in the fuel oil in front of theend section 29 prior to exposing the nozzle holes, meaning that the fuel oil substantially from the beginning of the injection is injected at full pressure, thereby ensuring a good combustion. - The
foremost section 12 and therearmost section 11 of the slide valve are ready-made as two separate units which are assembled only immediately before mounting theslide valve 10 in the injector valve. The comparatively thickslide valve section 11 may due to its large rigidity against transverse bending be processed at a high cutting force. - The
foremost section 12 is in the embodiment illustrated in Figs 2, 3 and 4 composed of two elements, viz. theshank 28 and aring 33 consisting of an erosion-resistant material, such asStellite 6. At its foremost end theshank 32 has a larger diameter and is there provided with threelongitudinal recesses 32 distributed along the circumference and allowing, as mentioned, the fuel oil to pass internally past thering 33. Therecesses 32 leave in the foremost end of the shank three radially protrudinglobes 34 to which thering 33 is secured, for instance by means of hard soldering. Alloy 50 may be used as the solder. This two-parted implementation of theforemost section 12 of the slide valve is extremely appropriate for mass production, thering 33 and theshank 28 being both easy to manufacture in a NC-automaton. If appropriate, the shank may of course be designed with more than three radially protruding lobes. - If the
foremost section 12 of the slide valve shall only be produced on a smaller scale, it may appropriately be implemented as shown in Figs 5 and 6. The foremost section is there manufactured from a single steel blank on the foremost end section and a distance up along the side, corresponding to the intended face for journalling in thebore 13 of the atomizer, of which a layer of erosion resistant material has been welded, such asStellite 6. Theshoulder 26 and theshank 28 are manufactured by turning and acentral bore 35 that is longer than thecylindrical end section 29 is drilled from the front end of the blank. Theportion 36 of the shank positioned behind theend section 29 and having a smaller diameter than theend section 29 but a larger diameter than the part of theshank 28 positioned behind, is subsequently provided with an appropriate number, e.g. four,longitudinal grooves 37 distributed along the circumference and having a radial depth that is a little larger than the wall thickness of theannular end section 29 so that the grooves discharge intobore 35 and establish flow connection between the parts of thebore 13 of the atomizer positioned at the rear and in front of theend section 29. As final treatment the foremostslide valve section 12 the external surface of theend section 29 is ground to size. - The flow passage allowing the combustible to flow past the slide valve includes the
recesses 32 of the embodiment illustrated in Fig. 2 whereas they include thegrooves 37 and thebore 35 in the embodiment illustrated in Fig. 5. - Instead of the illustrated threaded assembling between the two extreme sections, the sections may of course be assembled in another way, for instance by means of press fit or by a similar joining method. The shank may further be designed in another way, e.g. as a number of parallel and thin rods connecting the rearmost section of the shank with the
end section 29. The essential feature of the shank according to the invention is its flexibility allowing theend section 29 to conform to thebore 13 independently of the journalling bearing of the rearmost slide valve section in thevalve guide 8.
Claims (7)
- A fuel injector valve for internal combustion engines, including a hollow slide valve guide (8) fixedly disposed in the external housing (1) of the injector valve and the foremost end of which is designed as an atomizer (9) closed in front and provided with a central bore (13), said atomizer having in its side wall a number of transversely extending nozzle holes (31) for the injection of atomized fuel, a slide valve (10) axially displaceable in the guide for opening and closing the nozzle holes and having a foremost section (12) with a cylindrical end section (29) carried by a shank (28) and which is journalled with tight fit in the bore (13) of the atomizer in order to close the nozzle holes when the valve is in the closed position; said injector valve having a flow passage (3,4,19,21,13; 32) through which pressurized fuel may flow past the slide valve (10) and on to the nozzle holes (31) when the slide occupies its opening position in which its end section (29) exposes the holes, and a closure spring (16) acting against the fuel pressure for holding the slide in its closing position; the axial length of the end section (29) of the slide valve being at most of the same order of magnitude as the diameter of the bore (13) in the atomizer, and the length of the shank (28) being at least several times longer than the axial length of the end section (29), which foremost section (12) is a separate element, characterized in that the foremost section (12) is fixed to the remainder of the slide valve (10) and has a flexibility allowing the cylindrical end section (29) to align itself with the bore (13), and that the cylindrical end section (29) is the only part of the foremost section (12) which slides against an associated surface during opening or closing of the valve.
- A fuel injector valve according to claim 1, characterized in that the end section (29) is a cylindrical ring (33) secured on the shank (28).
- A fuel injector valve according to claim 2, characterized in that the shank (28) at its end facing towards the ring has radially extending lobes (34), preferably at least three, to which the ring (33) is secured, preferably by means of soldering.
- A fuel injector valve according to claim 1, characterized in that the shank (28) and the end section (29) are manufactured from one blank, of which the end forming the end section includes a central bore (35) which in the area above the end section is in flow connection with the part of the central bore (13) of the atomizer positioned above the end section.
- A fuel injector valve according to any of the preceding claims, characterized in that at least the foremost part of the cylindrical external surface (30) of the end section consists of an erosion-resistant material, such as Stellite 6.
- A fuel injector valve according to any of the preceding claims, characterized in that the foremost section (12) of the slide valve comprising the shank (28) and the end section (29) are exchangeable as a unit independently of the remainder of the slide valve (10).
- A method of manufacturing a slide valve of a fuel injector valve according to any of claims 1 to 6, characterized in that the cylindrical external surface (30) of the foremost section (12) of the slide valve is finally ground to size independently of the grinding of other slide surfaces.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DK169891A DK167502B1 (en) | 1991-10-04 | 1991-10-04 | FUEL ENGINE FOR COMBUSTION ENGINES |
DK1698/91 | 1991-10-04 | ||
PCT/DK1992/000282 WO1993007386A1 (en) | 1991-10-04 | 1992-09-24 | A fuel injector for internal combustion engines |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0606371A1 EP0606371A1 (en) | 1994-07-20 |
EP0606371B1 true EP0606371B1 (en) | 1995-08-09 |
Family
ID=8107302
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92921416A Expired - Lifetime EP0606371B1 (en) | 1991-10-04 | 1992-09-24 | A fuel injector for internal combustion engines |
Country Status (9)
Country | Link |
---|---|
EP (1) | EP0606371B1 (en) |
JP (1) | JP3027191B2 (en) |
KR (1) | KR100253673B1 (en) |
DE (1) | DE69204075T2 (en) |
DK (1) | DK167502B1 (en) |
HR (1) | HRP920658B1 (en) |
PL (1) | PL169883B1 (en) |
TW (1) | TW250529B (en) |
WO (1) | WO1993007386A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19815918A1 (en) * | 1998-04-09 | 1999-10-21 | Man B & W Diesel As | Fuel injector |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DK171975B1 (en) * | 1994-02-07 | 1997-09-01 | Man B & W Diesel Gmbh | Fuel injector for a large two-stroke internal combustion engine |
DK174075B1 (en) * | 1996-06-20 | 2002-05-21 | Man B & W Diesel As | Fuel injector for an internal combustion engine |
WO2000006891A1 (en) * | 1998-07-24 | 2000-02-10 | Man B & W Diesel A/S | A fuel valve for an internal combustion engine |
WO2000024671A1 (en) | 1998-10-28 | 2000-05-04 | Ebara Corporation | Waste carbonizing method |
DE19902282A1 (en) * | 1999-01-21 | 2000-08-17 | Siemens Ag | Injector for an injection system of an internal combustion engine |
WO2008071187A1 (en) * | 2006-12-15 | 2008-06-19 | Man Diesel A/S | A fuel injector for an internal combustion engine |
WO2008071188A1 (en) * | 2006-12-15 | 2008-06-19 | Man Diesel, Filial Af Man Diesel Se, Tyskland | A fuel injector for an internal combustion engine |
KR20090012056A (en) * | 2007-07-27 | 2009-02-02 | 베르트질레 슈바이츠 악티엔게젤샤프트 | An injection nozzle for fuel |
EP2031237B1 (en) | 2007-08-31 | 2010-09-29 | Wärtsilä Schweiz AG | Injection nozzle for injecting fuel |
DK2365206T3 (en) * | 2010-03-05 | 2014-05-19 | Wärtsilä Switzerland Ltd | Nozzle for a fuel injection device for internal combustion engines and method for making a nozzle |
JP5798898B2 (en) * | 2011-11-24 | 2015-10-21 | 三菱重工業株式会社 | Fuel injection device |
CN102748178A (en) * | 2012-07-26 | 2012-10-24 | 余姚市舒春机械有限公司 | Marine diesel injector assembly |
CN102748177B (en) * | 2012-07-26 | 2015-06-03 | 余姚市舒春机械有限公司 | Oil sprayer assembly of long-needle marine diesel engine |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2837606A1 (en) * | 1978-08-29 | 1980-03-06 | Daimler Benz Ag | Multi-jet fuel injector for Diesel IC engine - has pre-injection chamber with member controlling nozzle ducts on spring-loaded piston inside injector needle |
JPS6056165A (en) * | 1983-09-05 | 1985-04-01 | Toyota Central Res & Dev Lab Inc | Intermittent type swirl injection valve |
DE3418761A1 (en) * | 1984-05-19 | 1985-11-21 | Robert Bosch Gmbh, 7000 Stuttgart | INJECTION VALVE |
GB9008403D0 (en) * | 1990-04-12 | 1990-06-13 | Lucas Ind Plc | Fuel injection nozzle |
-
1991
- 1991-10-04 DK DK169891A patent/DK167502B1/en not_active IP Right Cessation
-
1992
- 1992-09-24 PL PL92303043A patent/PL169883B1/en unknown
- 1992-09-24 WO PCT/DK1992/000282 patent/WO1993007386A1/en active IP Right Grant
- 1992-09-24 KR KR1019940701085A patent/KR100253673B1/en not_active IP Right Cessation
- 1992-09-24 JP JP5506552A patent/JP3027191B2/en not_active Expired - Lifetime
- 1992-09-24 EP EP92921416A patent/EP0606371B1/en not_active Expired - Lifetime
- 1992-09-24 DE DE69204075T patent/DE69204075T2/en not_active Expired - Lifetime
- 1992-09-30 HR HR1698/91A patent/HRP920658B1/en not_active IP Right Cessation
- 1992-10-02 TW TW081107844A patent/TW250529B/zh active
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19815918A1 (en) * | 1998-04-09 | 1999-10-21 | Man B & W Diesel As | Fuel injector |
WO1999053196A1 (en) | 1998-04-09 | 1999-10-21 | Man B & W Diesel A/S | Fuel injection device |
CN1093226C (en) * | 1998-04-09 | 2002-10-23 | 曼B与W狄赛尔公司 | Fuel injection device |
Also Published As
Publication number | Publication date |
---|---|
PL169883B1 (en) | 1996-09-30 |
HRP920658B1 (en) | 1998-08-31 |
JPH06511064A (en) | 1994-12-08 |
DK167502B1 (en) | 1993-11-08 |
HRP920658A2 (en) | 1994-10-31 |
DK169891D0 (en) | 1991-10-04 |
DE69204075D1 (en) | 1995-09-14 |
JP3027191B2 (en) | 2000-03-27 |
KR940702982A (en) | 1994-09-17 |
WO1993007386A1 (en) | 1993-04-15 |
KR100253673B1 (en) | 2000-05-01 |
DE69204075T2 (en) | 1996-04-25 |
DK169891A (en) | 1993-04-05 |
TW250529B (en) | 1995-07-01 |
EP0606371A1 (en) | 1994-07-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0606371B1 (en) | A fuel injector for internal combustion engines | |
AU671492B2 (en) | Plasma cutting torch | |
US6125822A (en) | Two stage pressure relief valve | |
EP0744007B1 (en) | A fuel injector for a large two-stroke internal combustion engine | |
NZ228185A (en) | Fluid jet cutting nozzle assembly | |
JPS62282164A (en) | Injector | |
US20100294243A1 (en) | Fuel injection valve for internal combustion engines | |
US20220062923A1 (en) | Switcher nozzle high efficiency flow insert | |
DK174075B1 (en) | Fuel injector for an internal combustion engine | |
US5878961A (en) | Injection valve for injecting fuel directly into a combustion chamber of an internal combustion engine | |
GB2386974A (en) | Pilot control valve | |
GB1560979A (en) | Combined fuel injection pump and nozzle | |
WO2019178047A1 (en) | Spray tip design and manufacture | |
CA1289428C (en) | Interference connection between a fluid and a fluid injector | |
EP2378109B1 (en) | A fuel valve for large stroke diesel engines | |
AU2006314700A1 (en) | Device for the thermal deburring of workpieces | |
CA1292119C (en) | Apparatus for injecting substances into liquids | |
EP0074650A1 (en) | Fuel injection pump for internal-combustion engines | |
EP0919752B1 (en) | Balanced piston relief valve | |
EP0211848B1 (en) | Installation for the treatment of parts by means of an explosive gas mixture, particularly thermal deburring machine | |
EP0052937A1 (en) | A fuel injector for internal combustion engines | |
WO1989008526A1 (en) | Wire electrode guide apparatus for wire cut electric discharge machine | |
EP0580651B1 (en) | Internal-combustion engine | |
US2761646A (en) | Nozzle structure | |
EP0153968B1 (en) | Power steering pump |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 19940214 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): CH DE FR GB IT LI NL |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: MAN B&W DIESEL A/S |
|
17Q | First examination report despatched |
Effective date: 19941222 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): CH DE FR GB IT LI NL |
|
REF | Corresponds to: |
Ref document number: 69204075 Country of ref document: DE Date of ref document: 19950914 |
|
ET | Fr: translation filed | ||
ITF | It: translation for a ep patent filed |
Owner name: SOCIETA' ITALIANA BREVETTI S.P.A. |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090924 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: CH Payment date: 20110923 Year of fee payment: 20 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20110923 Year of fee payment: 20 Ref country code: GB Payment date: 20110920 Year of fee payment: 20 Ref country code: FR Payment date: 20110928 Year of fee payment: 20 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 20110929 Year of fee payment: 20 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20110928 Year of fee payment: 20 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R071 Ref document number: 69204075 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R071 Ref document number: 69204075 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: V4 Effective date: 20120924 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: PE20 Expiry date: 20120923 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION Effective date: 20120923 Ref country code: DE Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION Effective date: 20120925 |