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
  • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
  • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
  • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
  • F02M21/0248—Injectors
  • F02M21/0251—Details of actuators therefor
  • F02M21/0254—Electric actuators, e.g. solenoid or piezoelectric
• • 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
  • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
  • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
  • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
  • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
  • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
  • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
• • 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
  • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
  • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
  • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
  • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
  • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
  • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
  • F02M51/0675—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto the valve body having cylindrical guiding or metering portions, e.g. with fuel passages
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
  • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
  • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
  • F02M21/0248—Injectors
  • F02M21/0257—Details of the valve closing elements, e.g. valve seats, stems or arrangement of flow passages
  • F02M21/026—Lift valves, i.e. stem operated valves
  • F02M21/0269—Outwardly opening valves, e.g. poppet 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
  • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
  • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
  • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
  • F02M21/0248—Injectors
  • F02M21/0275—Injectors for in-cylinder direct injection, e.g. injector combined with spark plug
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
  • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
  • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/30—Use of alternative fuels, e.g. biofuels

Definitions

• the present invention relates to a gas injector for blowing in a gaseous fuel, in particular hydrogen or natural gas or the like, with reduced wear and improved damping behavior, in particular for internal combustion engines.
• the gas injector is designed in particular for direct injection into a combustion chamber of an internal combustion engine.
• Gas injectors are known from the prior art in different configurations.
• a problem with gas injectors is inherent in the fact that due to the gaseous medium to be blown in, no lubrication is possible with the medium, as is possible, for example, with fuel injectors that inject gasoline or diesel. This results in excessive wear during operation compared to fuel injectors for liquid fuels. In this context, it would be desirable to have a gas injector with improved wear behavior.
• the gas injector according to the invention for blowing in a gaseous fuel with the features of claim 1 has the advantage that wear on the gas injector can be significantly reduced.
• the service life of the gas injector is lengthened and essentially corresponds to the service life of a fuel injector for liquid fuels.
• a closing element can carry out a significantly better damped closing process, so that wear on the valve seat and on other components of the closing element is reduced or is prevented.
• this is achieved in that the gas injector has a lubricant which is located in a closed lubricant space and in which movable parts of the gas injector are arranged.
• the gas injector includes a magnetic actuator with an armature, an inner pole and a coil.
• the armature which is mechanically connected to a closing element that opens and closes a gas path on a valve seat, is provided in order to enable a movement for opening and/or closing the injector.
• the armature located in the lubricant space which is pulled against the inner pole of the magnetic actuator due to electromagnetic forces when the coil is energized, is therefore located inside the lubricant space and is constantly supplied and lubricated with lubricant. As a result, wear on the armature is significantly reduced in comparison with the gas injectors previously known from the prior art.
• a flexible sealing element which seals the lubricant space in a partial area. Furthermore, by using the sealed lubricant space filled with lubricant, the service life of the gas injector can be extended significantly.
• the lubricant space is preferably completely filled with lubricant.
• the gas injector comprises a braking device which is arranged in the lubricant chamber and is set up to brake the closing element from the open to the closed state during a resetting process of the gas injector.
• the braking device comprises a braking bolt, a damping space which is in fluid communication with the lubricant space, and an elastic braking element, in particular a spring.
• the braking bolt and the elastic braking element are in operative connection with the closing element and/or the armature, with the braking bolt also being set up during the reset process to displace lubricant from the damping chamber in order to dampen a return of the brake bolt and thus a return of the closing element.
• the provision of the damping chamber can prevent the formation of vapor bubbles in the liquid lubricant when the hydraulic sticking is overcome, see above that in particular wear due to cavitation can be prevented.
• This is additionally supported by the acceleration of the additional masses provided with the braking device.
• a further deceleration is realized by the displacement of the lubricant between the armature and the brake bolt.
• a return speed of the closing element can also be further reduced by friction of guide elements or the like with the braking bolt. All this reduces the impact force of the anchor at the stop, so that the service life of the anchor can be further extended.
• the brake bolt comprises in particular a main body with a contact surface which is arranged on a side of the main body of the brake bolt facing the closing element and can be brought into operative connection with the closing element and serves as a stop surface.
• the main body is preferably cylindrical. More preferably, an annular flange is arranged on the side of the main body facing the closing element. The annular flange preferably serves as a stop surface.
• the elastic braking element of the braking device is arranged in the damping space.
• the elastic braking element is preferably a compression spring, in particular a cylinder spring.
• the damping space is in fluid communication with the lubricant space via a guide play of the brake bolt.
• the gas injector also includes a throttle which connects the damping space to the lubricant space.
• the throttle ensures that the damping process can run in a defined manner, since the lubricant is then transferred from the damping chamber to the lubricant chamber via the throttle.
• the throttle is preferably a small connecting hole between the damping chamber and the lubricant chamber.
• the gas injector further preferably comprises an anchor bolt which bears against the closing element, the anchor bolt being connected to the anchor.
• An end of the anchor bolt facing away from a sealing seat of the gas injector is designed to come into contact with the brake bolt when the gas injector is in the closed state.
• the closing element is preferably a valve needle.
• the closing element and the anchor bolt are preferably firmly connected to one another, particularly preferably via a spring plate.
• the gas injector preferably includes an anchor bolt guide in which the anchor bolt is guided.
• the anchor bolt guide forms a stop for the brake bolt.
• the gas injector comprises a guide body which is arranged in the lubricant chamber and has a guide area for guiding the brake bolt.
• the guide body preferably has a recess, in particular at an end of the guide body directed toward the sealing seat, in which the brake bolt is guided.
• a first gap between the brake bolt and the armature bolt guide preferably has a first width B, which is smaller than a second gap with a second width C between the armature and the inner pole.
• the axial gap B between the armature bolt guide and the brake bolt is preferably in a range from 1% to 90% of the axial gap C between the armature and the inner pole.
• the axial gap B between the anchor bolt guide and the brake bolt is particularly preferably smaller than 25% of the axial gap C, more preferably in a range from 3% to 20% of the axial gap C.
• the axial gap C preferably has a size of 0.05 mm to 3 mm, in particular 0.8 mm.
• the first and second flexible sealing elements are each a membrane or each a rubber element.
• the membrane can be single-layer or multi-layer and can be fixed, for example by means of laser welding, to the respective components for sealing the lubricant chamber.
• the flexible sealing element of the lubricant space preferably comprises a first and a second flexible sealing element.
• the two sealing elements are particularly preferably bellows.
• the lubricant chamber is thus sealed by two flexible sealing elements, which means that if the lubricant is displaced in the lubricant chamber, it can be prevented that an unfavorable overpressure or negative pressure develops, which, for example, can exert an unwanted force on the closing element of the gas injector via components of the lubricant reservoir.
• By providing two flexible sealing elements even if an unfavorable force is exerted on one of the sealing elements, which could lead to an increase in pressure in the sealed lubricant space, compensation can be provided by the second flexible sealing element. Thus, an undesirable change in pressure inside the sealed lubricant space can be successfully prevented.
• the accumulator spring exerts a predetermined force on the lubricant in the closed lubricant space, preferably from the outside.
• An overpressure of between 0.5 and 10.times.10.sup.5 Pa is preferably exerted here, particularly preferably 1 to 5.times.10.sup.5 Pa.
• the lubricant in the lubricant space can thus be brought under a predetermined pretension, as a result of which undesired deformations which could have an impact on a stroke of the closing element can be reliably prevented.
• the first flexible sealing element is a first bellows and the second flexible sealing element is a second bellows.
• the first and second bellows are of identical design, ie have the same mean bellows diameter and the same number of bellows corrugations. In this way, in particular, the production costs of the gas injector can be reduced.
• the second bellows is more preferably connected to the accumulator spring via a spring plate. As a result, a simple and cost-effective structure can be implemented. Furthermore, as a result, a certain pretension can be exerted directly on the second bellows by means of the accumulator spring, as a result of which the rigidity of the second bellows is slightly increased compared to the first bellows.
• the gas injector also includes a first and a second closing element guide.
• the first and second closing element guides are preferably both arranged in the lubricant chamber.
• the closing element preferably has only the two first and second closing element guides, so that all the guiding elements for the closing element are arranged inside the lubricant space filled with lubricant. This ensures that all important components of the gas injector inside the lubricant chamber are lubricated. As a result, a service life of the gas injector can in practice correspond to that of an injector for liquid fuels.
• An oil in particular mineral oil, is preferably used as the lubricant.
• a liquid fuel in particular diesel or petrol, is used.
• a grease or a PAO oil (poly alpha olefins) or an ester oil or a polyglycol oil is used as the lubricant.
• the first and second flexible sealing element are each a single-layer or multi-layer bellows.
• the bellows is preferably made of metal or alternatively made of a plastic.
• the first bellows is preferably fixed directly to the closing element with a first end and fixed to a housing component of the gas injector with another end.
• Metal bellows for example, can be fixed by means of a welded connection.
• a gas path of the gaseous fuel is preferably provided in an area between a valve housing of the gas injector and an actuator housing of the gas injector.
• the actuator can be arranged in a housing and at least partially preassembled as an assembly.
• the lubricant chamber can also be arranged in a relatively simple manner inside the actuator housing.
• the gas path of the gaseous fuel is formed through a region of the magnet actuator, in particular through the coil space in which the coil of the magnet actuator is arranged.
• a separate actuator housing for the magnetic actuator can be omitted.
• An electrical contact is then particularly preferably routed through the gas path of the gaseous fuel. In this way, in particular, the complexity of the structure of the gas injector can be reduced. It should be noted that the electrical contact, which leads through the gas space, must of course be sealed from the outside.
• a filter is arranged in the gas path for the gaseous fuel in order to filter out any solid particles present in the gaseous fuel or to filter out solid particles caused by manufacture or assembly.
• a guide component is also preferably provided on the closing element, in particular if the closing element is a long valve needle.
• the gas injector is preferably an outwardly opening injector. More preferably, the gas injector is pressure force balanced. As a result, the force required to open the gas injector by the magnetic actuator is independent of the gas pressure. The time it takes to open and close the injector after the start and end of current application is therefore also independent of the gas pressure. This in turn allows operation at different gas pressures. The gas pressure can be reduced if a small injection quantity is desired, and the gas pressure can be increased if a large injection quantity is desired.
• the injector is pressure-force-balanced when the mean diameter of the bellows is equal to the diameter of the seat contact line between the closing element and the valve body. However, the mean bellows diameter can also be smaller or larger than the seat diameter.
• the total closing force on the valve needle is reduced with a higher gas pressure and the injector opens faster when energized and closes more slowly after energizing. This results in an increased gas injection volume.
• the closing force on the valve needle increases with a higher gas pressure. This in turn can compensate for an increase in the amount of seat leakage due to the higher gas pressure.
• a return preferably takes place by means of a return spring.
• a pressure-balanced injector there is in particular no pressure force on the valve needle from the gaseous fuel when the gas injector is in the closed state, so that a load on the closing element can be significantly reduced.
• Figure 1 shows a schematic sectional view of a gas injector according to a first embodiment of the invention
• Figure 2 is a schematic enlarged partial sectional view of the
• Figure 3 is a schematic, enlarged partial sectional view of a
• a gas injector 1 according to a first preferred exemplary embodiment of the invention is described in detail below with reference to FIGS.
• the gas injector 1 for introducing a gaseous fuel comprises a magnetic actuator 2, which moves a closing element 3, in this exemplary embodiment, an outwardly opening valve needle, from a closed state to an open state.
• FIG. 1 shows the closed state of the gas injector.
• the magnetic actuator 2 includes an armature 20, which by means of an armature bolt
• the magnetic actuator 2 includes a Inner pole 21, a coil 22 and a magnet housing 23, which ensures a magnetic yoke of the magnetic actuator.
• the gas injector 1 comprises a main body 7 with a connection pipe 70 through which the gaseous fuel is supplied.
• a valve housing 8 in which the magnetic actuator 2 is arranged is fixed to the main body 7 .
• the valve housing 8 is followed by a housing sleeve 19 and a valve tube 90, at the free end of which a valve seat 11 is provided, on which the closing element 3 releases and closes a passage for the gaseous fuel.
• FIG. 1 shows an electrical connection 13, which is routed through the main body 7 to the magnetic actuator 2.
• the reference numeral 10 designates a resetting element for the closing element 3 in order to reset it back into the closed state shown in FIG. 1 after an opening process.
• FIG. 1 also shows a gas flow as a gas path 14 through the gas injector 1 .
• the gas flow begins at the connection pipe 70 and is then diverted into an annular space 80 between the valve housing 8 and the main body 7.
• the gas flow 14 continues past an outer area of the magnetic actuator 2 through a filter 15 to in front of the valve seat 11 Breakthroughs are provided in the respective components, which are not all shown in FIG.
• the gas injector 1 When the gas injector 1 opens, the gaseous fuel then flows past the outer circumference of the magnetic actuator 2 and the open valve seat 11 into a combustion chamber of an internal combustion engine, which is indicated by the arrows A in FIG.
• the closing element 3 thus releases the gas path 14 on the valve seat 11 and closes it.
• a first guide area 31 and a second guide area 32 are provided for guidance between the closing element 3 and a valve body 9, as can be seen in detail from FIG.
• the first guide area 31 is formed directly between the closing element 3 and the valve body 9 close to the valve seat.
• the second guide area 32 is included formed between a spring plate 16 and the valve body 9.
• the spring plate 16 is firmly connected to the closing element 3 , with the restoring element 10 being supported between the valve body 9 and the spring plate 16 .
• the gas injector 1 comprises a closed lubricant space 4.
• the closed lubricant space 4 is completely or partially filled with a liquid lubricant, e.g. oil.
• the first and second flexible sealing element 51, 52 is each designed as a bellows.
• the first and second flexible sealing element 51, 52 is of the same design.
• the flexible sealing elements 51, 52 can also be, for example, a membrane or a hose or the like instead of a bellows.
• the second flexible sealing element 52 is fixed to an accumulator spring plate 41, for example by means of a welded connection.
• the gas injector 1 includes an accumulator compression spring 40 which is supported on the main body 7 and pretensions the second flexible sealing element 52 via the accumulator spring plate 41 .
• Connecting bores 18a are provided in the guide body 18 so that the lubricant located in the lubricant chamber 4 is also located in the area within the second flexible sealing element 52 .
• the first flexible sealing element 51 is fixed directly to the closing element 3 and connected to the valve body 9 at the other end.
• transverse bores 91 are provided in the valve body 9 so that there is a fluid connection between the interior of the first flexible sealing element 51 and the interior of the valve body 9 .
• the lubricant space 4 thus has two flexible sealing elements 51 , 52 and the accumulator compression spring 40 .
• the accumulator pressure spring 40 exerts a certain preload, for example 1 x 10 5 Pa, on which there is a pressure in the lubricant chamber 4 existing lubricants. If, during an opening process, the lubricant is displaced by the stroke of the closing element 3 or by thermal expansion or cooling of the lubricant, any overpressure/negative pressure that may arise inside the lubricant chamber 4 can be caused by deflection at the second flexible sealing element 52 in conjunction with a contraction of the Storage pressure spring 40 are compensated.
• the flexible sealing element 51 can thus be avoided by an unwanted force acting on the closing element 3 via the active surface of the bellows.
• the anchor bolt 24 with the anchor 20 fixed thereto is arranged in the closed lubricant space 4 . Since the lubricant chamber 4 is filled with a lubricant, for example a liquid fuel such as petrol or diesel, or a grease or the like, the armature 20 is continuously lubricated. In this way, the problem that occurs in the prior art with gaseous fuels, namely that the moving parts are not lubricated, can be compensated for.
• a lubricant for example a liquid fuel such as petrol or diesel, or a grease or the like
• a filling channel 17a is provided for filling the closed lubricant space 4 .
• the filling channel 17a is sealed in a fluid-tight manner by means of a sealing ball 17 .
• a braking device 6 is also arranged in the closed lubricant space 4 .
• the braking device 6 comprises a braking bolt 60, a damping chamber 62 filled with lubricant and an elastic braking element 61.
• the damping chamber 62 is in fluid communication with the lubricant chamber 4.
• the braking bolt 60 and the elastic braking element 61 are in an operative connection with the closing element 3 when the gas injector returns to the closed starting position to achieve in the closed state of the gas injector ( Figure 1).
• the brake bolt 60 is guided in the guide body 18 .
• the damping space 62 is formed directly on the brake bolt 60 on a side of the brake bolt 60 facing away from the valve seat 11 .
• the damping chamber 62 is connected to the connecting bores 18a and thus to the main area of the lubricant chamber 4 via a throttle 63, which is a small bore.
• the brake spring 61 is arranged in a spring space 67 .
• the brake bolt 60 has a contact surface 60a which is in contact with the anchor bolt 24 .
• the closed state which is shown in FIG. 2, there is a first gap 101 between the brake bolt 60 and a stationary anchor bolt guide 25.
• the anchor bolt guide 25 guides the anchor bolt 24 during an opening and closing process.
• the braking spring 61 is arranged between the braking bolt 60 and the guide body 18 .
• the brake bolt 60 has a flange 60b which is provided with play relative to the guide body 18 .
• a passage 65 which can be formed, for example, as a slot on the end of the guide body 18 directed towards the anchor bolt guide 25 .
• a fluid connection for the lubricant from the spring chamber 67 via the guide play 64 and the passage 65 to the lubricant chamber 4 can thus be provided.
• the first gap 101 is also formed between the contact surface 60a of the brake bolt 60 and the anchor bolt guide 25 .
• the gap 101 has a first width B, which is smaller than a second width C between the armature 20 and the inner pole 21 (see Figures 1 and 2) at the second gap 102. This ensures that a stroke of the brake bolt 60 , which is prestressed in the axial direction by the compression spring 61, is smaller than a stroke of the armature 20. This allows sufficient fluid to flow from the lubricant chamber 4 via the throttle 63 into the damping chamber 62 during the injection process.
• the damping process is further supported by the braking spring 61 and hydraulic adhesion of the braking bolt 60 to the anchor bolt guide 25 .
• the damping space 62 can prevent cavitation during the closing process in this area between the anchor bolt guide 25 and the contact surface 60a of the brake bolt 60 . Friction of the brake bolt 60 in the guide body 18 also delays the restoring process and also the masses of the moving components to be accelerated in the entire lubricant chamber 4, which result in displacement of the lubricant in the closed lubricant chamber and thus additional braking during the closing process.
• the damping behavior can be adjusted individually for the respective gas injector.
• an abutment surface between the cushion bolt 60 and the anchor bolt guide 25 may be wedge-shaped, i.e. not perpendicular to a central axis X-X of the gas injector.
• radial slots can be provided in the contact surface 60a or the end face of the anchor bolt guide 25, which is directed towards the brake bolt 60, as a result of which a cavitation effect is further reduced and prevented.
• the gas injector 1 shown in FIG. 1 is pressure force balanced.
• This means that the closing element 3 is connected to the valve body 9 via the first flexible sealing element 51, with the first flexible sealing element 51 designed as a metal bellows having an average diameter which is equal to a diameter on the valve seat 11 at which the closing element 3 on the valve seat 11 seals.
• the first flexible sealing element 51 designed as a metal bellows having an average diameter which is equal to a diameter on the valve seat 11 at which the closing element 3 on the valve seat 11 seals.
• the closing element 3 when the closing element 3 has been placed in the open state (movement of the closing element 3 to the left in Figure 1) by actuating the magnetic actuator 2 and a gas injection is carried out, when the closing element 3 is reset, reliable damping is imminent the closing element is pressed into the valve seat 11 can be carried out.
• the brake bolt 60 is pressed in the direction of the damping chamber 62 by the anchor bolt 24 and moves only as slowly as the lubricant is pressed out of the damping chamber 62 through the throttle 63 into the lubricant chamber 4 .
• a closing speed of the closing element 3 is braked significantly and effectively before the closing element hits the valve seat 11 .
• FIG. 3 shows a partial cross section of a gas injector according to a second exemplary embodiment of the invention. Identical or functionally identical parts are denoted by the same reference symbols as in the first exemplary embodiment.
• FIG. 3 shows the braking device 6, which is designed differently from that in the first exemplary embodiment.
• the damping chamber 62 is no longer connected to the lubricant chamber 4 via a throttle, but via a guide play 64 between the brake bolt 60 and the guide body 18.
• a connection to the lubricant chamber 4 is then established via one or more passages 65, which extend in the radial direction are formed on the end face of the guide body 18, ensured.
• the brake spring 61 is arranged in the damping space 62 .
• the anchor bolt 24 thus presses onto the contact surface 60a of the brake bolt 60 so that the brake bolt is pressed in the direction of the arrow 66 towards the guide body 18 .
• Another advantage of the second embodiment is that there is a smaller volume of lubricant in the damping space 62 . In this way, in particular, vibrations on the brake bolt 60, which can result from the elasticity of the lubricant, can also be reduced.
• the second exemplary embodiment corresponds to the first exemplary embodiment, so that reference can be made to the description given there.
• the gas injector 1 can provide reduced wear on the moving parts, in particular on the valve seat 11 , armature 20 and in the armature bolt 24 . Furthermore, heat dissipation from the magnetic actuator 2 can be significantly improved by the sealed lubricant chamber 4 with a liquid lubricant. Furthermore, the two flexible sealing elements 51 , 52 can prevent unwanted forces from acting on the closing element 3 .

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• General Engineering & Computer Science (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• Chemical Kinetics & Catalysis (AREA)
• General Chemical & Material Sciences (AREA)
• Oil, Petroleum & Natural Gas (AREA)
• Analytical Chemistry (AREA)
• Electromagnetism (AREA)
• Physics & Mathematics (AREA)
• Fuel-Injection Apparatus (AREA)
• Magnetically Actuated Valves (AREA)

Applications Claiming Priority (2)

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• 2021
  • 2021-01-27 DE DE102021200689.2A patent/DE102021200689A1/de active Pending
  • 2021-12-13 KR KR1020237028599A patent/KR20230132579A/ko unknown
  • 2021-12-13 JP JP2023545268A patent/JP2024503928A/ja active Pending
  • 2021-12-13 EP EP21839401.3A patent/EP4285017A1/de active Pending
  • 2021-12-13 CN CN202180091982.8A patent/CN116783384A/zh active Pending
  • 2021-12-13 WO PCT/EP2021/085484 patent/WO2022161688A1/de active Application Filing

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