Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
  • F02D19/02—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with gaseous fuels
  • F02D19/021—Control of components of the fuel supply system
  • F02D19/022—Control of components of the fuel supply system to adjust the fuel pressure, temperature or composition
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
  • F02B17/005—Engines characterised by means for effecting stratification of charge in cylinders having direct injection in the combustion chamber
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
  • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
  • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
  • F02B23/101—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
• • 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
  • F02M21/0203—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels characterised by the type of gaseous fuel
  • F02M21/0209—Hydrocarbon fuels, e.g. methane or acetylene
  • F02M21/0212—Hydrocarbon fuels, e.g. methane or acetylene comprising at least 3 C-Atoms, e.g. liquefied petroleum gas [LPG], propane or butane
• • 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
  • F02M21/0245—High pressure fuel supply systems; Rails; Pumps; Arrangement of 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
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
  • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
  • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
  • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
  • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
  • F02B2023/108—Swirl flow, i.e. the axis of rotation of the main charge flow motion is vertical
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B75/00—Other engines
  • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
  • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
  • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B75/00—Other engines
  • F02B75/12—Other methods of operation
  • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
  • F05C2201/00—Metals
  • F05C2201/04—Heavy metals
  • F05C2201/0433—Iron group; Ferrous alloys, e.g. steel
  • F05C2201/0448—Steel
  • F05C2201/046—Stainless steel or inox, e.g. 18-8
• • 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
  • Y02T10/12—Improving ICE efficiencies
• • 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 invention relates to a liquid gas engine.
• LPG engines are spark-ignited gasoline engines that are fed with LPG.
• Liquefied petroleum gas also known as LPG (Liquified Petrolium Gas)
• LPG Liquified Petrolium Gas
• propane and butane as its main components. It is produced during the extraction of crude oil and in refinery processes and can be liquefied under pressure. Liquid gas is characterized by a high octane number (RON> 100).
• LPG engines differ from gasoline engines in that they have a different mixture preparation, which is due to the high evaporation tendency of the LPG.
• Liquid gas is supplied as liquid under pressure to the engine in appropriate pressure lines.
• the liquid gas is converted into the gaseous state with the supply of heat.
• the evaporator is a heat exchanger to which heated cooling water is fed in order to heat and vaporize the liquefied petroleum gas.
• the evaporator is combined with a pressure regulator to keep the now gaseous liquid gas in a certain pressure range.
• the liquefied gas is then fed to a gas / air mixer which mixes liquefied gas with air.
• a gas / air mixer is known for example from DE 33 32 923 C2.
• the mixer consists of a ring element which supplies liquid gas to a central air flow passing through the ring element and swirls it with it.
• the company DAF has a LPG engine for buses under the Type designation LT 160 LPG presented.
• This LPG engine corresponds to a diesel engine that has been converted to a LPG engine.
• the engine presented by DAF is equipped with a LPG injection system that injects LPG into an intake duct.
• This injection system corresponds completely to those currently used in gasoline engines (cars).
• the liquid gas is injected into the intake duct, the vapor temperature of the liquid gas should reduce the mixture temperature and improve efficiency.
• This cooling by evaporation can lead to icing of the injection valves in the start-up phase and when the air humidity is high, which means that operation at cold outside temperatures cannot be guaranteed.
• heating an ignitable mixture poses considerable dangers.
• the invention has for its object to provide a liquid gas engine that is simple in construction and ensures safe operation with high power output.
• the liquid gas engine according to the invention is a gasoline engine with a high-pressure injection device which injects liquid gas directly into the combustion chamber. As a result, the liquid gas in the liquid state, in which it can be handled easily and safely, is conducted to the combustion chamber of the engine.
• the liquid liquefied gas is injected directly into the combustion chamber, atomized and evaporated.
• the transition from the liquid to the gaseous state of matter thus takes place only in the combustion chamber.
• the very fine atomization of the liquefied gas injected with high pressure ensures an excellent distribution in the combustion chamber and the sudden evaporation of the liquefied gas results in perfect mixing of the fuel with the air contained in the combustion chamber, so that the combustion mixture after ignition ideally burns.
• FIG. 1 schematically shows a single-cylinder liquid gas engine with an injection device
• FIG. 2 shows the injection device shown in FIG. 1 in longitudinal section
• FIG. 3 shows an armature of FIG. 2 in cross section, an armature
• FIG. 4 shows in cross section a valve body of the injection device shown in FIG. 2,
• Fig. 5 shows a crank loop motor in partial section.
• the liquid gas engine according to the invention has an injection device 1, which injects liquid gas directly into a combustion chamber 4 of the liquid gas engine via an injection nozzle 2.
• the combustion chamber is in a manner known per se by a cylinder 5, a cylinder head 11 and a piston 12 limited.
• An injector 2 and a spark plug 10 are arranged in the cylinder head 11.
• the injection nozzle 2 is connected to the injection device 1 via a line 72.
• the injection device is connected via a liquid gas supply line 113 and a liquid gas return line 92 to a pressure tank 111 (shown schematically in simplified form in FIG. 1).
• the liquid gas is above the vapor pressure of z. B. 8-12 bar to ensure that it can not evaporate in the supply line 113.
• Liquid gas not discharged from the injection device 1 is returned to the pressure tank 111 via the liquid gas discharge line 92.
• the injection device 1 conveys the liquid gas in short pressure surges at a pressure of 40 bar, preferably 60 bar, to the injection nozzle 2, at which the intermittently injected liquid gas is atomized in very fine droplets distributed over the combustion chamber 4. The droplets evaporate suddenly in the air fed into the combustion chamber 4 via the inlet channel 8. The result is an ideally mixed fuel / air mixture which can be ignited by the spark plug 10.
• the ignition timing is controlled by an electronic control device 6 in accordance with several parameters, such as, for example, the outside temperature, the crankshaft position and the amount of liquid gas injected. Due to the high calorific value of the liquid gas, it is advisable to delay the ignition timing somewhat compared to comparable petrol engines.
• the spent exhaust gas is then discharged from the combustion chamber 4 via an exhaust gas duct 3.
• the cooling effect generated by the evaporation of the liquid gas occurs in the combustion chamber 4.
• the cooling effect is correspondingly low and is compensated for by the compression generated by the compression stroke of the piston 12.
• the load is high, there is a much larger amount of liquid in the combustion chamber 4 injected.
• the cooling effect is increased accordingly, so that a significant increase in efficiency is achieved with large loads due to the "internal" cooling.
• the injection device 1 is preferably designed as an electromagnetically driven reciprocating piston pump 1, which works according to the energy storage principle, so that the liquid gas is injected into the combustion chamber 4 with short pressure surges.
• Reciprocating pumps 1 of this type are known, for example, from DE 41 06 04 1 5 A and DE 42 06 817 A.
• the reciprocating piston pump 1 has an essentially elongated cylindrical pump housing 15 with an armature bore 16, a valve bore 17 and a pressure chamber bore 18, which are each introduced one after the other in the pump housing 15 and form a passage extending through the entire pump housing 15.
• the armature bore 16 is arranged behind the valve bore 17 in the injection direction and the pressure chamber bore 18 is arranged in front of the valve bore 17 in the injection direction.
• the bores 16, 17, 18 are arranged concentrically to the longitudinal axis 19 of the pump housing 15, the armature bore 16 and the pressure chamber bore 18 each having a larger inner diameter than the valve bore 17, so that the armature bore 16 and the valve bore 17 through a first ring step 21 and the valve bore 17 and the pressure chamber bore 18 are separated from one another by a second annular step 22.
• the armature bore 16 delimits an armature space 23 in the radial direction, in which an approximately cylinder-shaped armature 24 is arranged such that it can move back and forth in the longitudinal axis direction.
• the armature space is delimited in the axial direction to the front by the first annular step 21 and to the rear by a front end face 25 of a cylindrical sealing plug 26 which is screwed into the end of the armature bore 16 which is open to the rear in the injection direction.
• the armature 24 is formed from a substantially cylindrical body with a front and rear end face 28, 29 and a lateral surface 30 in the injection direction.
• the provision of the conical surface 31 on the armature 24 further reduces the contact and thus the friction surface, as a result of which the friction between the armature 24 and the inner surface of the armature bore 16 and thus also the heat development is further reduced.
• the armature 24 is provided in the region of its lateral surface 30 with at least one, preferably two or more grooves 32 running in the longitudinal axis direction.
• the armature 24 has a cross-sectional shape (FIG. 3) with two laterally arranged semicircular elements 24a and with two wide, flat grooves 32 in the area between the semicircular elements 24a.
• a continuous bore 33 is made centrally on the armature 24 in the longitudinal axis direction.
• a delivery piston tube 35 is inserted, which forms a central passage space 36.
• a plastic ring 37 is seated on the front end face 29 of the armature 24 and is penetrated by the delivery piston tube 35.
• An anchor spring 38 is supported on the plastic ring 37 and extends to a corresponding bearing ring 39. This bearing ring 39 is seated on the first ring stage 21 in the armature bore 16.
• the delivery piston tube 35 is non-positively connected to the armature 24.
• the unit consisting of feed piston tube 35 and armature 24 is referred to below as feed piston element 44.
• the delivery piston element 44 can also be formed in one piece or in one piece his .
• a guide tube 40 is seated in the valve bore 17 in a form-fitting manner and extends rearward into the armature space 23 into the area within the spiral spring 38.
• an outwardly projecting ring web 41 is provided, which is supported on the second ring step 22 to the rear.
• the annular web 41 does not extend completely radially to the inner surface of the pressure chamber bore 18, so that a narrow, cylindrical gap 42 is formed between the annular web 41 and the pressure chamber bore 18.
• the guide tube 40 is secured against axial displacement to the rear by the annular web 41.
• the delivery piston tube 35 which is non-positively connected to the armature 24 extends forward into the guide tube 40 and backwards into an axial blind bore 43 of the sealing plug 26, so that the delivery piston tube 35 both at its front end 45 in the injection direction and at its rear end 46 is performed.
• the delivery piston element 44 is guided without tilting, so that undesired friction between the armature 24 and the inner surface of the armature bore 16 can be reliably avoided.
• a valve body 50 is axially displaceably mounted, which forms a substantially cylindrical, elongated, peg-shaped solid body with a front and rear end face 51, 52 and a jacket surface 53.
• the outer diameter of the valve body 50 corresponds to the clear width of the passage in the guide tube 40.
• An annular web 54 is provided on the outer surface 53 of the valve body 50 and is arranged approximately at the end of the front third of the valve body 50.
• the ring web 41 of the guide tube 40 forms an abutment for the ring web 54 of the valve body 50 in the rest position of the valve body 50, so that it cannot be moved further back.
• the valve body 50 is on its circumference with three grooves 55 extending in the longitudinal axis direction (Fig. 4).
• the ring web 54 is interrupted in the area of the grooves 55.
• the rear end face 52 of the valve body 50 is conical at its edge region and interacts with the end face of the front end 45 of the delivery piston tube 35.
• the three-dimensional shape of the front end 45 of the delivery piston tube 35 is adapted to the rear end face 52 of the valve body 50, in which the inner edge of the delivery piston tube 35 is chamfered and the wall of the delivery piston tube 35 is somewhat worn away on the inside.
• the delivery piston tube 35 thus forms with its front end 45 a valve seat 57 for the valve body 50. If the valve body 50 bears against the valve seat 57 with its rear end face 52, the passage through the grooves 55 made in the area of the lateral surface of the valve body 50 is blocked .
• a pressure chamber body 60 which consists of a cylinder wall 61 and a front end wall 62, a hole or bore 63 being made centrally in the end wall 62 .
• the pressure chamber body 60 With its cylindrical wall 61, the pressure chamber body 60 is positively inserted in the pressure chamber bore 18, with its end faces 64 located at the free end of the cylinder wall 61 being arranged abutting the outwardly projecting annular web 41 of the guide tube 40, with radial through bores 65 in the pressure chamber body 60 are provided, which creates a connection between the pressure chamber 66 and the fuel supply bore 76.
• the pressure chamber body 60 delimits with its interior a pressure chamber 66 into which the valve body 50 can immerse and pressurize the fuel in the pressure chamber 66.
• the pressure chamber At its rear region in the injection direction, which extends approximately over half the length of the pressure chamber body 60, the pressure chamber has a larger clear width than in the previous their area.
• the larger clear width in the rear area is dimensioned such that the valve body 50 with its ring web 54 and a slight play can dip into the pressure chamber 66
• the clear width of the front area is dimensioned such that only for the ring web 54 front area of the valve body 50 and a coil spring 67 surrounding this area is sufficient space.
• the pressure chamber 66 is made only slightly larger than the space required during the injection process of the valve body 50.
• the coil spring 67 is seated at one end on the inside of the end wall 62 of the pressure chamber body 60 and is at its other end on the valve body 50 and in particular on the annular web 54, so that it pushes the valve body 50 and the pressure chamber body 60 apart.
• the pressure chamber body 60 is axially fixed in the injection direction to the front by a connecting piece 70 which is screwed into the end of the pressure chamber bore 18 which is open to the front.
• the connecting piece 70 limits the position of the pressure chamber body 60 in the axial direction to the front, so that the coil spring 67 biases the valve body 50 to the rear.
• the connection piece is formed with an opening 71 for connecting the fuel delivery line 72 (FIG. 1).
• the connecting piece 70 has a bore 73 which is continuous in the longitudinal axis direction and in which a standing pressure valve 74 is accommodated.
• the ⁇ Standdruck- valve is preferably located adjacent to the pressure chamber body 60th
• the pressure chamber body 60 is provided on its outer surface with an annular groove 68, in which a plastic sealing ring 69 is mounted, which seals the pressure chamber body 60 against the inner surface of the pressure chamber bore 18.
• a liquid gas supply opening 76 in the area of the pressure chamber bore 18 is provided on the pump housing 15 for the supply of liquid gas. brought so that they can communicate with the holes 65 in the pressure chamber body 60.
• the liquid gas supply opening 76 is surrounded by a holder 77 for a liquid gas supply valve 78 which is screwed into the holder 77.
• the LPG supply valve 78 is designed as a one-way valve with a valve housing 79.
• the valve housing 79 has two axially aligned bores 80, 81, the bore 80 on the pump housing side having a larger inner diameter than the bore 81, so that an annular step is formed between the two bores which forms a valve seat 82 for a ball 83.
• the ball 83 is biased against the valve seat 82 by a spring 84, which is supported in the area around the liquid gas supply opening 76 on the pump housing 15 in the bore 80, so that liquid gas supplied from outside lifts the ball 83 from the valve seat 82 so that the liquefied gas is supplied through the bore 80 and the liquefied gas supply opening 76 into the pressure chamber bore 18.
• the blind hole or the blind bore 43 is arranged running in the longitudinal axis direction and opens into the armature space 23, the blind hole 43 extending over approximately two thirds to three quarters of the length of the sealing plug 26.
• One, preferably two or more long bores 88 extends from the rear region of the blind hole 43 to the peripheral region 89 of the front end face 25 of the sealing plug 26, so that a communicating connection is established between the armature space 23 and the blind hole 43.
• an outwardly leading bore 90 is introduced as a liquid gas drain opening.
• the bore 90 is extended on the outside by a connecting piece 91 for connecting the liquid gas return line 92 (FIG. 1).
• the cylindrical sealing plug 26 has a circumferential, outwardly projecting annular web 93 on its outer surface.
• the ring web 93 also serves, among other things, for the axial fixing of a locking ring 94 encompassing the pump housing 15 on the outside or a coil housing cylinder 95 arranged directly adjacent to the locking ring 94.
• the locking ring 94 forms two legs 96, 97 arranged at right angles to one another, one leg 96 rests on the outside of the pump housing 15 and the other leg 97 protrudes outwards and rests on the coil housing cylinder.
• the bobbin case cylinder 95 consists of a cylinder wall 98 and a cylinder base 99, which is connected laterally to the cylinder wall 98 and points inwards and has a hole, so that the bobbin case cylinder 95 points from the rear to the bobbin case 15 with the cylinder base 99 to the rear is pushed on until the cylinder wall 98 abuts a housing wall 100 projecting vertically outward from the coil housing 15 and thus delimits an annular chamber 101 with an approximately rectangular cross section for receiving a coil 102.
• the coil housing cylinder 95 and the locking ring 94 are thus clamped between the housing wall 100 and the ring web 93 of the sealing plug 26 and fixed in their axial position.
• the leg 96 of the locking ring 94 is chamfered on the inner edge of its end face, a sealing ring 103, such as, for example, between the bevel formed therein and the ring web 93.
• a sealing ring 103 such as, for example, between the bevel formed therein and the ring web 93.
• an O-ring is clamped.
• the coil 102 is approximately rectangular in cross section and is cast into a support body cylinder 104 with a U-shaped cross section by means of epoxy resin, so that the coil 102 and the support body cylinder 104 form a one-piece coil module.
• the support body cylinder 104 has a cylinder wall 105 and two side walls 106, 107, which protrude radially from the cylinder wall 105 and delimit the space for the coil 102, the cylinder wall 105 extending laterally beyond the rear side wall 106, so that its end face 108, the face 109 of the side walls 106, 107 and the inner surfaces of the cylinder wall 106 and the front side wall 107 fit positively in the annular chamber 101.
• a material 110 with low magnetic conductivity e.g. Copper, aluminum, stainless steel, introduced to avoid a magnetic short circuit between the coil 102 and the armature 24.
• a liquid gas under a pre-pressure is supplied from the liquid gas tank into the pressure chamber 66 by means of the feed pump 112 and the liquid gas supply line 113 through the liquid gas supply valve 78. From the pressure chamber 66, the liquid gas flows through the grooves 55 introduced in the jacket area of the valve body 50, through the guide tube 40 into the gap between the valve seat 57 of the delivery piston tube 35 and the rear end face 52 of the valve body and through the passage space 36 of the delivery piston 35 into the blind hole
• the pressurized liquid gas flows through the bores 88 of the sealing plug 26 and floods the armature space, the regions of the armature space in front of and behind the armature 24 through the grooves 32 made in the armature 24 are communicating with each other, so that the entire anchor space is filled with liquid gas.
• the liquefied gas is passed through a liquefied gas return line 92 back into the liquefied gas tank 111.
• the admission pressure of the liquid gas is greater than the pressure drop occurring in the flow path, so that a continuous purging of the reciprocating piston pump 1 is ensured, and is lower than the passage pressure of the auxiliary pressure valve 74, so that no liquid gas is conveyed into the combustion chamber 4 in the starting position of the delivery piston element 44 .
• the armature 24 is moved forward in the impact or injection direction by the magnetic field generated in this way.
• the movement of the armature 24 and the delivery piston tube 35 connected to it in a non-positive manner acts during a forward stroke over the length s (corresponds to the distance between the valve seat 57 of the delivery piston tube 35 and the rear end face 52 of the valve body 50 in the starting position) only the spring force of the spring 38 counter.
• the spring force of the spring 38 is so soft that the armature 24 is moved almost without resistance, but is still sufficient for returning the armature 24 to its starting position.
• the armature 24 "floats" in the pressure space 23 filled with liquid gas, the liquid gas being able to flow back and forth between the areas in front of and behind the armature 24 in the armature space 23, so that no pressure opposing the armature 24 is built up.
• the delivery piston element 44 consisting of the armature 24 and the delivery piston tube 35, is thus continuously accelerated and stores kinetic energies .
• an injection device operating according to the energy storage principle enables the injection of liquid gas under high pressure with very short injection pulses.
• an injection device it is also possible to inject the liquefied petroleum gas during a work cycle with several injection pulses, for example in order to introduce a large amount of liquefied gas into the combustion chamber under high load or to effect charge stratification in the case of liquefied petroleum gas in the area of the spark plug at the time of ignition is enriched.
• the reciprocating piston pump 1 with a return line 92 described above one without a return line can also be used, which can be connected to conventional liquid gas tanks.
• the liquid gas engine according to the invention is preferably designed in the manner of a boxer engine as a crank loop engine. It essentially consists of two opposing cylinders 5 and 5 'arranged in the same axis, in which the working pistons 12 reciprocate in a straight line.
• the pistons are each connected to their piston rods 153, which also only perform linear reciprocating movements.
• the piston rods 153 are articulated with their inner ends to a centrally located, rotating crankshaft drive 154, which converts the linear movements of the piston rods into a rotary movement.
• the crank loop drive is located in a crank loop housing 155 to which the cylinders 5 and 5 'are fastened via partition walls 156.
• the crank loop drive has a crank loop frame 152, which includes a straight link 158 arranged transversely to the piston rod 153.
• a sliding block 159 in which a crank pin 160 of a crankshaft is rotatably mounted, moves in the link 158.
• crank loop motors are known for example from DE 29 62 391 AI, DE 32 18 320 AI and EP 187 930 B1.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical Kinetics & Catalysis (AREA)
• General Chemical & Material Sciences (AREA)
• Oil, Petroleum & Natural Gas (AREA)
• Fuel-Injection Apparatus (AREA)
• Output Control And Ontrol Of Special Type Engine (AREA)

Priority Applications (5)

Applications Claiming Priority (2)

Related Child Applications (1)

Publications (1)

Family

ID=7804218

Family Applications (1)

Country Status (7)

Cited By (2)

Families Citing this family (6)

Citations (13)

Family Cites Families (6)

• 1996
  • 1996-08-30 DE DE19635248A patent/DE19635248C2/de not_active Expired - Fee Related
• 1997
  • 1997-08-26 WO PCT/EP1997/004647 patent/WO1998009060A1/de not_active Application Discontinuation
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  • 1997-08-26 CN CN97197554A patent/CN1228827A/zh active Pending
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  • 1997-08-26 AU AU47003/97A patent/AU720373B2/en not_active Ceased
  • 1997-08-26 CA CA002262555A patent/CA2262555A1/en not_active Abandoned

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