DE3012022A1 - Reciprocating piston IC engine - has second combustion chamber in piston connected by restriction to cylinder combustion space - Google Patents

Abstract

The engine has a piston (7) which has a recess (21) to form a second combustion chamber. The recess is connected to the main combustion space (20) in the cylinder by a nozzle (18), preferably made of ceramic material, fitted in the piston crown (17). The nozzle gives a restricted passage (19) between the two combustion spaces (20, 21), through which the fuel-air mixture has to pass during compression and combustion. The combustion and expansion process is improved and better fuel consumption is obtained.

Description

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PATENT LAWYERS DIPL-ING. HORST ROSE "*" * DIPL-ING. PETEA KQSjEJL

Our file no. : 1716/13 Bad Gandersheim2 7th MAR. 1980 Karl BURGSKÜLLER

Combustion »piston engine

The invention relates to an internal combustion piston engine with at least one cylinder receiving at least one piston, each piston over at least one connecting rod with a crankshaft, is articulated, and with a combustion chamber for each cylinder, the volume in a first combustion chamber that changes during operation of the engine and at least one second combustion chamber of, arranged within an outer contour of the associated piston During the operation of the engine constant volume is divided, the first combustion chamber with the second combustion chamber in constant communication via at least one connection opening determined by the piston stands.

In known diesel machines of this type ("HÜTTE, des Ingenieurs Taschenbuch", Volume II A, 28th edition 1954, Verlag Wilhelm Ernst & Sohn, Berlin, pages 779 and 780, Fig. 93 and 94), namely the "Saurer combustion chamber" and the ^M MAN spherical combustion chamber ", the fuel is injected directly into the cylinder. The second combustion chamber in the piston has either a heart-like cross-sectional area or the shape of a spherical part and serves to support the mixture formation through additional air movement in the combustion chamber the second combustion chamber is relatively large in each case.

The invention is based on the object, compared to known machines with the same performance

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ORIGINAL INSPECTED ™ - ^{/ HU}

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. 01 reduce fuel consumption.

This object is achieved according to the invention in that the at least one connection opening is at least partially is designed as a nozzle opening. During the compression cycle air or mixture flows through the at least one nozzle opening into the second with an increase in pressure Combustion chamber. Fuel or water can also be injected directly through the at least one nozzle opening injected into the second combustion chamber.

In each case, the ignitable mixture is practically simultaneously ignited in the first and second combustion chambers. The mixture in the second combustion chamber expands with an increase in temperature and pressure and occurs like a jet at the corresponding piston speed through the at least one nozzle opening at very high speed into the first combustion chamber. The reaction impulse exerts a considerable additional energy impulse or thrust on the piston and thus on the Engine and supplements the drive energy due to the combustion in the first combustion chamber. This reduced the specific fuel consumption compared to conventional internal combustion piston engines.

According to one embodiment of the invention, the at least one nozzle opening formed by a nozzle body inserted into the piston. The nozzle body can z. B. be screwed into a threaded hole of the piston and to reduce wear from high temperature resistant Material, e.g. B. made of ceramic.

According to another embodiment of the invention, the nozzle body is aligned at least in the top dead center position of the piston with a passage of the DUsenkörpers for assembly purposes, from the outside accessible opening, e.g. B. threaded hole in a cylinder head. In the threaded hole z. B.

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ORiGiNALlNSPECTED

a spark plug or injector can be screwed in. In this way, the nozzle body can be installed with little effort Replace the machine either when it is worn or for adjustment purposes without having to dismantle the machine.

According to a further embodiment of the invention is the nozzle opening in the piston with its longitudinal axis at a right angle to a longitudinal axis of a piston pin extending plane and compared to a longitudinal axis of the piston in the direction of a working stroke of the piston heavily loaded lateral skirt surface of the piston arranged offset. This reduces the burden the lateral surface of the shaft and thus an otherwise expected higher wear of the cylinder and piston, Das applies in particular to conventional machines that have been retrofitted according to the invention.

Particularly favorable conditions arise when, according to the invention, the plane through the longitudinal axis of the Piston runs.

Tilting moments can be avoided if, according to the invention, the longitudinal axis of the nozzle opening is the longitudinal axis of the piston pin cuts.

According to one embodiment of the invention, the nozzle opening in the piston is coaxial with a longitudinal axis of the piston arranged.

According to another embodiment of the invention the nozzle opening is provided in a piston head, which is dome-shaped is formed and is connected gas-tight on its circumference with the piston via a thread. So lets achieve the desired effect in a relatively inexpensive and simple manner.

According to one embodiment of the invention, the first and every second combustion chamber can be connected to one another by at least one filling channel, with a confluence of each filling channel in the second combustion chamber being closable by a valve tongue resting resiliently on an inner wall of the second combustion chamber. -A-

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This makes it easier to fill the second combustion chamber with air or an ignitable mixture. the Valve tongues open on the compression stroke of the Kolbona and ensure that the second combustion chamber is safely filled with less energy.

Manufacturing advantages result if according to the invention a plurality of valve tongues are part of a valve cap attached to the piston.

According to another embodiment of the invention are the at least one second combustion chamber as a circumferential groove in the piston and the nozzle opening as an annular gap between a piston head and an inner surface of the cylinder. The configurations according to claims 12 and 13 allow a simple change in the size of the nozzle opening. According to the invention, a peripheral area of the Koibenbodens with a high temperature and wear resistant Be provided with armor. This protects the piston crown from being impaired by the burning and mixture flowing through the nozzle opening at high speed.

According to a further embodiment of the invention is in the inner surface of the cylinder or the cylinder head an the annular gap in the area of the top dead center position of the piston enlarging annular recess is provided. The recess facilitates and improves the filling of the second combustion chamber with air or ignitable Genisch and allows practically simultaneous ignition in both combustion chambers.

It has a favorable influence on the flow conditions and thus the efficiency of the machine if, according to the invention a circumferential area of the piston crown, starting from a central area, one extending upwards and inwardly extending first inclined surface and one

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has downwardly and inwardly extending second inclined surface.

According to one embodiment of the invention, the at least one second combustion chamber designed as a circumferential groove in ° 5 of the piston, while the at least one nozzle opening runs in a central region of a piston crown.

In this case, according to the invention, the nozzle opening to the Pistons arranged coaxially and connected to the circumferential groove by branch channels distributed over the circumference. So is a quick and complete flow exchange possible between the first and the second combustion chamber.

According to one embodiment of the invention is between the first and second combustion chambers have a piston head with a piston head cooperating with an inner surface of the cylinder Piston ring arranged. The piston ring can be slotted at an angle to improve its function be. According to the invention, the piston ring can be located at a distance from the inner surface of the cylinder at the top Have bevel. In this way, air or an ignitable mixture from the first combustion chamber can be sent to the Flow past the piston ring into the second combustion chamber, but not the other way around. This serves a good and in the degree of proficiency favorable filling of the second combustion chamber.

To reduce its mass while maintaining high strength and good elasticity, according to the invention the piston ring can be made hollow.

According to a particular embodiment of the invention is the piston ring of circular or circular ring-shaped cross-sectional area, the piston ring in an after outer V-shaped extended circumferential groove of the piston into

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ORIGINAL INSPECTED

rngt and a lower inclined boundary surface of the circumferential groove provided with brackets that support the piston ring and are spaced from one another over the circumference.

According to one embodiment of the invention is in the Inner surface of the cylinder in the area of the top dead center position of the piston at least one over only one Pocket-shaped recess extending part of the cylinder circumference intended. This allows the efficiency of the second combustion chamber to be filled while maintaining this the guide of the piston ring.

From a manufacturing point of view, it is favorable if in accordance with the invention the piston head by means of a central threaded extension into a threaded hole in an intermediate piston head is screwed in.

Favorable flow and connection conditions result when, according to the invention, the circumferential groove in the piston which forms the second combustion chamber moves away from ■ expanded from the outside inwards and then narrowed.

According to a further embodiment of the invention a beam reflector is arranged in a cylinder head opposite each nozzle opening. The radiation reflector can made of high temperature and wear resistant material, e.g. ceramic, and protects the cylinder head against the adverse effects of the hot high-speed gas jet emerging from the nozzle opening.

To increase the mass of the beam and thus its reaction pulse, according to the invention, in the cylinder a water injection nozzle to take effect. According to the invention, the water injection nozzle can be coaxial with the nozzle opening be arranged so that water can also be injected directly into the second combustion chamber. The water injection nozzle For this reason, according to the invention, it can also be arranged concentrically with a beam reflector.

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ORIGINAL INSPECTED

A special embodiment of the invention is characterized in that a two-stroke engine first piston guided in the cylinder and with two at diametrically opposite points of a first piston shaft arranged first piston pin pin is hinged to a first connecting rod that concentrically guided in the first piston skirt and a second piston with a second piston pin on one between the two first connecting rods arranged second connecting rod is articulated, the crankshaft with each other aligned first crank pins for the first two connecting rods and one opposite the first crank pin 180 offset second crank pin for the second connecting rod, and that the first combustion chamber between the first and the second piston is arranged and the first and second piston each have a second combustion chamber exhibit. This results in a comparatively compact machine with only a small stroke of each piston and an extraordinarily high frequency of work strokes.

According to one embodiment of the invention, at least one of the first two piston pin journals on the one hand constantly connected to a pre-compression chamber of the cylinder and on the other hand through the second piston with the first combustion chamber connectable scavenging opening. So is the wall of the cylinder while saving more Weakening recesses of the charge exchange guaranteed.

To simplify the flushing of the combustion chambers With air or an ignitable mixture, according to the invention, each precompression chamber can always be equipped with a cavity Be connected to the crankcase.

To support the gas exchange, according to one embodiment of the invention, the cylinder is by a

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Cylinder head closed, with a pump chamber between the cylinder head and the first piston via at least one

Before k omp re ss Ions
Pump channel is constantly connected to the \ room. According to the invention, the at least one pump channel can have a groove in an inner wall of the cylinder. However, according to the invention, the at least one pump channel can also be laid inside a wall of the cylinder or outside the cylinder.

According to one embodiment of the invention aligned ■ \ ο the at least one irrigation port in the upper dead center position of the first piston with a longitudinal axis of a mounted in a wall of the cylinder injection nozzle. In this way, for example, an injection nozzle for fuel and / or an injection nozzle for water can be provided.

According to a further embodiment of the invention The extension of the longitudinal axis of the at least an injection nozzle spaced from a longitudinal axis of the first piston. This can be used in the first and mid-infrared achieve favorable flow and combustion conditions also in the two second combustion chambers.

According to one embodiment of the invention, the Longitudinal axis of the at least one injection nozzle with respect to the cylinder from the outside and bottom to the inside and top inclined. This also enables favorable flow and combustion conditions to be achieved.

According to one embodiment of the invention, Je at least one outlet opening is provided in the first piston shaft and in a wall of the cylinder. Appropriately are according to the invention the outlet openings in the circumferential direction offset by 90 ° with respect to the first piston pin pin. This opens up a favorable discharge path for the burnt gases and at the same time ensures that

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if possible, fresh cargo cannot escape from the outlet openings.

According to one embodiment of the invention, the first piston and / or in an intermediate piston bottom a piston head of the second piston in each case at least two nozzle openings evenly distributed in the circumferential direction arranged. This avoids tilting moments due to the jet impulses on the piston.

According to another embodiment of the invention, there are in the piston crown and / or in the piston crown In alternation with the nozzle openings, beam reflectors are arranged in such a way that with each nozzle opening of the piston bottom a beam reflector of the piston crown is aligned and vice versa. This measure serves the operational safety and increasing the efficiency and service life of the machine by avoiding any cavitation.

According to a further embodiment of the invention, each first piston pin pin tapers outwards stepped conical, while each first connecting rod with a complementary stepped conical opening on the associated first piston pin pin by means of a locking ring “This bearing ensures that the first two connecting rods are in a defined operating position to each other and offers advantages in the strength of the pulled out of the wall of the first piston skirt Piston pin journal,

According to another embodiment of the invention a feed nozzle for scavenging air or an air-fuel scavenging mixture opens into the cylinder with a right angle a longitudinal axis of the crankshaft arranged mouth plane surface, wherein on one of the first connecting rods is attached to the muzzle plane cooperating control slide. So can be in a simple way and

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defines the flushing medium - giving it a larger, optimal one
Admission period than for example with the known three-channel system and a more complete filling possible - in the
Insert crankcase.

A safe mode of operation can be achieved if, according to the invention, the feed nozzle is in the flat surface of the mouth has a labyrith seal arrangement.

Advantageous operating conditions are obtained if, according to one embodiment of the invention, the control slide is essentially C-shaped and has an outlet opening with a recess in the mouth plane surface of the feed connector during the compression stroke in
the area shortly after the upper perpendicular position
until shortly before the bottom dead center position of the first KoI-ben increasingly opens up to the full cross-section and then decreases again.

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130 0 41/0116

The invention is explained in more detail below with reference to the exemplary embodiments shown in the drawings. Ea show:

Fig. 1 is a longitudinal section through a first embodiment the internal combustion piston engine with a central nozzle body,

2 shows a longitudinal section through another embodiment with an eccentric nozzle body,

3 shows a longitudinal section through a further embodiment with a hood-shaped piston head,

4 shows a longitudinal section through another embodiment with filling channels and valve cap,

and 5A in each case /

5 fine longitudinal section through a further embodiment with a nozzle opening designed as an annular gap,

6 shows the detail VI in FIG. 5 in an enlarged illustration,

7 shows a longitudinal section through another embodiment with a piston ring in the piston head,

8 shows the detail VIII in FIG. 7 in an enlarged representation,

9 shows a sectional view corresponding to FIG. 8 with a differently designed piston ring,

FIG. 10 is a side view of the joint of the piston ring according to FIG. 9,

11 shows the sectional view along line XI-XI in FIG. 7, but without the piston,

12 shows a longitudinal section through a further embodiment with a piston ring and water injection nozzle,

13 shows a longitudinal section through a particular embodiment of the internal combustion piston engine two pistons per cylinder,

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14 shows the sectional view along line XIV-XIV in Fig. 13,

15 shows the sectional view along line XV-XV in FIG. 13.

Fig. 1 shows a two-stroke internal combustion piston engine 1 with a crankshaft 4 rotating in a crankcase 2 in the direction of an arrow 3 on which a connecting rod 6 connected to a piston pin 5 is articulated. The piston pin 5 is part of a Piston 7, which is slidable within a cylinder 8 inserted into the crankcase 2 and with piston rings 9 is provided. The cylinder 8 has an inlet port 10 for an ignitable two-stroke mixture, the so-called fresh charge, and an outlet opening 11 for the burnt gases, both controlled by the piston 7 will. The cylinder 8 of the air-cooled machine 1 is provided with cooling fins 12 and one also with cooling fins 13 having cylinder head 14 is provided. A spark plug 16 is inserted into a threaded bore 15 of the cylinder head 14 screwed in.

In a piston head 17 of the piston 7, a nozzle body 18 is in a central threaded bore with a Nozzle opening 19 screwed in. The nozzle opening 19 forms a permanent connection between a first combustion chamber 20 of itself during operation of the engine 1 changing volume and a second combustion chamber 21 formed within the piston 7 of during the operation of the machine 1 constant volume. The nozzle body 18 is aligned with the thread

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Bore 15 can be expanded and used through this passage. The second combustion chamber 21 is larger than the first combustion chamber 20 in the maximum compression top dead center position of the piston 7, which in Pig.

1 has not yet been fully reached.

During the compression stroke of the piston 7, which is just taking place in the state shown in FIG ignitable two-stroke mixture is increasingly compressed by the piston 7 moving upwards and flows from the The first combustion chamber 20, which is becoming smaller and smaller, through the nozzle opening 19 into the second combustion chamber 21. When ignited by the spark plug 16, the flame front is not only planted in the first combustion chamber 20, but rather through the nozzle opening 19 also practically without delay into the second combustion chamber 21. The charge in the first combustion chamber 20 expands when heated and drives the piston 7 downwards. The charge in the second combustion chamber 21 also under-expands. Warming off. The hot gases flow at a higher rate Speed through the nozzle opening 19 into the first combustion chamber 20 and thereby impart the piston 7 an additional significant impulse due to the mass ejection through the nozzle opening 19. This impulse which due to the "restrained" beam only with the downward movement of the crank pin from the top dead center position begins to form and in the area of the horizontal position of the crank pin its greatest intensity developed, and those from the combustion in the first combustion chamber 20 gained force components complement each other with at most the same working pressure as in conventional ones Machines and get over the piston pin 5 and the Connecting rod 6 to crankshaft 4, the aforementioned impulse reduces the specific fuel consumption compared to conventional machines that only have the first combustion chamber 20.

The nozzle body 18 is expediently made of high temperature-resistant material, e.g. ceramic -14-

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BATH ORIGINAL

or E-Mail.

In the following _{FIGS. Ure} n, the same parts as j η FIG. 1 are identified by the same reference numerals.

In the embodiment according to FIG. 2, the spark plug 16 and the nozzle body 18 are arranged eccentrically. The nozzle opening 19 lies with its longitudinal axis 22 at a right angle to a longitudinal axis 23 of the piston pin 5 extending plane and opposite a longitudinal axis 24 of the piston 7 in the direction of a working stroke of the piston comparatively heavily loaded lateral shaft surface 25 of the piston 7 on the left in FIG. 2 offset. In which The embodiment according to FIG. 2 runs through this plane

the longitudinal axis 24 of the piston 7. Furthermore, intersects the Longitudinal axis 22 of the nozzle opening 19 is the longitudinal axis 23 of the piston pin,

By this and similar eccentric arrangements of the nozzle body 18, the direction of the after ignition Optimize the gas jet passing from the nozzle opening 19 into the first combustion chamber 20. It can be achieve that the reaction force of the gas jet the piston 7 in one of the piston 7 of the now more stressed Shank surface 25 affects the lifting senses. As a result, the left half of the cylinder 8 in FIG. 2 becomes and the opposite shaft surface 25 is relieved, the mechanical efficiency of the machine increases and the wear diminished.

According to Fig. 3, the nozzle body 18 is in a hood-shaped trained piston head 17 screwed. The piston head 17 is in turn connected via a circumferential thread 26 screwed to the piston 7.

In the exemplary embodiment according to FIG. 4, a beam reflector is inserted into a threaded hole in the cylinder head 14 screwed in coaxially with the dune body 18. The beam reflector 27 is preferably made of ceramic and has the Task that through the nozzle opening 19 in the first Ver ~

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combustion chamber 20 passing gas jet by means of a Annular trough 28 to divide and divide. This reduces the stress on the cylinder head 14 and the risk of it Cavitation by the gas jet is reduced and, on the other hand, the piston is additionally acted upon, especially in terms of time.

In Fig. 4 FUllkanäle 29 distributed over the circumference are provided in an upper region of the piston 7 through which the first combustion chamber 20 can be connected to the second combustion chamber 21. One confluence of each filling channel 29 in the second combustion chamber 21 can be closed by a valve tongue 31 resting resiliently on an inner wall 30 of the second combustion chamber 21. The valve tongues 31 are components of a valve cap 33 fastened to piston 7 by armature 32.

The design of the piston 7 according to FIG. 4 is particularly suitable for high-speed machines 1 and leads to an energy-saving filling of the second combustion chamber 21. During the compression stroke of the piston 7, the 4 is almost complete, the ignitable mixture flows from the first combustion chamber 20 both through the nozzle opening 19 as well as through an enlarged annular gap 34 between the cylinder 8 and the piston head 17 through the Filling channels 29. As long as the mixture pressure in the filling channels 29 is greater than the mixture pressure in the second combustion chamber 21, the valve tongues 31 are lifted off the inner wall 30 by the mixture flow. This is ensures a particularly rapid filling of the second combustion chamber 21 with an ignitable mixture. The through the annular gap 34 flowing, relatively cool portion of the mixture also contributes in a desirable manner to a Cooling of the cylinder 8 and the piston crown 17 at.

The nozzle body 18 can according to FIG. 4 after unscrewing the beam reflector 27 through its threaded hole can be installed and removed through it.

FIG. 5A will be described following FIG.

130-041 / 011S

Fig. 5 shows a four-stroke internal combustion piston engine 35 with each cylinder 8 an inlet valve and an outlet valve 37, the valves 36,37 are each biased by a valve spring 38 in sealing contact with a valve seat ring 39 of the cylinder head 14. The details of the valve control are known per se and have been omitted here. The cylinder head 14 is closed at the top by a cylinder head cover 40 ..

According to FIG. 5, the second combustion chamber 21 is designed as a circumferential groove in the piston 7, a nozzle opening 41 exists as an annular gap between the piston head 17 and an inner surface 42 of the cylinder 8. A circumferential area The piston crown 17 is provided with a high-temperature-resistant and wear-resistant armor 43. Of the Piston head 17 is by means of a central threaded extension 44 in a threaded bore of an intermediate piston head 45 screwed in and through an expanding conical threaded plug screwed into the threaded extension 44 46 secured.

According to FIG. 6, an annular gap 41 is in the inner surface 42 of the cylinder 8 in the vicinity of the top dead center position of the piston 7 enlarging annular recess 47 is provided. The perimeter of the bucket bottom 17 has, starting from a central region 48, a first one extending upward and inward Inclined surface 49 and a downwardly and inwardly extending second inclined surface 50.

According to FIG. 7, the nozzle body 18 and thus the nozzle opening 19 are arranged concentrically in the piston head 17 and through branch channels 51 distributed over the circumference with the one formed as a circumferential groove in the piston 7 second combustion chamber 21 connected. In a groove of the piston head 17 is a with the inner surface 42 of the cylinder 8 cooperating piston ring 52 used.

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As FIG. 8 shows, the piston ring 52 is hollow and is provided at the top with a bevel 53 located at a distance from the inner surface 42 of the cylinder 8.

9 shows a modification in that the piston ring 52 has an annular cross-sectional area is and into an outwardly V-shaped widening The circumferential groove 54 of the piston head 17 protrudes. A lower one inclined boundary surface 55 of the circumferential groove 54 has at a distance from one another over the circumference distributed, the Piston ring 52 supporting brackets 56.

Fig. 10 shows inclined abutment surfaces 57 of the piston ring 52. The piston ring 52 according to FIG. 8 is equipped with similar inclined abutment surfaces.

During the compression stroke, the piston ring 52 according to FIGS. 8 to 10 is pushed into the second combustion chamber 21 flowing mixture is resiliently deformed radially inward, the abutment surfaces 57 resting against one another. When the filling of the second combustion chamber 21 has ended, and in particular during the working stroke, If the piston ring 52 according to FIGS. 8 and 9 rests resiliently the inner surface 42 of the cylinder 8.

In Fig. 11, the pistons have been omitted for the sake of simplicity. In the inner surface 42 of the cylinder b , in the area of the top dead center position of the piston 7, pocket-shaped recesses 58 that extend only over a part of the cylinder circumference and are located at a distance from one another are provided.

Fig. 12 shows a modified embodiment of the Machine 35 insofar as a beam reflector is coaxial with the nozzle body 18 in a threaded hole in the cylinder head 14 59 is screwed in. A nozzle channel 60 extends through the center of the beam reflector 59

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through the already burning mixture according to the temperature the machine 35 automatically dosed small amount of preheated water can be added. This water quantum reaches the second combustion chamber 21 and increases the mass and thus the energy of the gas jet, the flows from the second combustion chamber 21 through the nozzle opening 19. This allows the heat economy and the efficiency of the machine 35 can be increased.

In Fig. 5A an elastically deformable, dome-shaped piston head 17 with a corrugated lower edge 120 in a recess 121 of the piston 7. Of the Edge 120 forms passage openings 122, which are in constant Are connected to the nozzle opening 41 designed as an annular gap. The annular recess 47 is in this Case in relation to the outermost edge located in the top dead center position in the central region 48 of the piston head 17 is provided in the cylinder head 14.

To adapt the width of the nozzle opening to the operating conditions is in a threaded bore 123 of the piston 7 an adjusting screw 124 with at its frustoconical Head 125 formed notch profile 126 screwed. The notch profile 1 - 6 engages in a complementary one Groove profile 127 of a receiving opening provided in the piston head 17 128 for the adjusting screw 124. To Removal of the spark plug 16 can be the adjusting screw 124 with a screwdriver in that direction against the Resistance of the self-locking notch profile 126 - groove profile 127 - turn connection under elastic deformation of the piston head 17 brings the desired increase or decrease in the width of the nozzle opening 41.

13 to 15 show a two-stroke internal combustion piston engine 61, in which a first piston 62 is guided in the cylinder 8 and with two diametrically opposite? - lying points of a first piston skirt 63 arranged first piston pin pin 64 and 65 each on a first connecting rod 66 and 67 is articulated. Concentric

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In the first piston skirt 63, a second piston 68 is guided and with a second piston pin 69 on one articulated between the two first connecting rods 66, 67 arranged second connecting rod 70. The crankshaft 4 has aligned first crank pins 71 and 72 for the two first connecting rods 66,67 and one opposite the first crank pin 71, 72 offset by 180 on the second crank pin 73 for the second connecting rod 70.

A first combustion chamber 74 is between an intermediate piston base 75 of the first piston 62, the first Piston skirt 63 and a piston head 76 of the second piston 68 are defined. The first piston 62 is connected to a second Combustion space 77 between the intermediate piston crown 75, the first piston skirt 63 and a piston crown 78 of the first piston 62 equipped. The second piston 68 also has such a second combustion chamber 79 between the piston crown 76, a second piston skirt and an intermediate piston crown 81,

In the intermediate piston base 75 and the piston base 76 are each 90 ° to each other in the circumferential direction offset two nozzle bodies 18 and two beam reflectors 27 are used (see. Also Fig. 15). The relative arrangement is taken so that with a nozzle opening 19 of the piston bottom 75 always a beam reflector 27 of the piston head 76 is aligned and vice versa. The piston crown 78 and the Piston intermediate bottom 75 penetrates concentrically through the spark plug 16, one electrode 82 of which can be moved axially through the Cylinder head 14 is passed. The electrode 82 is outside of the cylinder head 14 through a threaded hole 83 of the cylinder head 14 surrounded by screwed-in cover cap 84.

The first two piston pin journals 64,65 are each penetrated by a flushing opening 85 and 86. On the one hand, each flushing opening 85, 86 is always provided with a precorapression space 87 and 88 of the cylinder 8 connected and on the other hand - controllable by the second piston 68 - with connectable to the first combustion chamber 74. The pre-20

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compression space 87 _f 88 extend with their longitudinal axis parallel to a longitudinal axis 89 of the first piston 62 and are constantly a cavity 90 of the crankcase 2 Rait connected.

A pump chamber 91 between the cylinder head 14, the cylinder 8 and the piston head 78 protrudes over diametrically opposed pump channels that are parallel to the longitudinal axis 89 92 and 93 in constant communication with the pre-compression chambers 87, 88. 13 to 15 are the

here

Pump channels 92 and 93 respectively loaded as a groove in the _A Eaum inner surface 42 of the cylinder 8 is formed.

The flushing openings 85, 86 are each aligned in the area of the top dead center position shown in FIGS. 13 and 14 of the first piston 62 with a longitudinal axis 94 and 95 an injection nozzle 96 mounted in the cylinder 8, and the longitudinal axes 94, 95 of the injection nozzles 96, 97 are, respectively

at an angle 98 (FIG. 13) with respect to the horizontal and inclined at an angle 99 (FIG. 15) with respect to a vertical plane. This results in a good distribution distribution of the medium to be injected in the first combustion chamber 74. For example, fuel can be injected through the injection nozzle 96 and water is injected into the first combustion chamber 74 through the injection nozzle 97.

One outlet port 100 and one 101 (FIG. 14) each is in the first piston shaft 63 and in the wall of the cylinder 8 provided. According to FIG. 13, an uppermost limit of the outlet opening 100 is an amount 102 above that uppermost limit of the flushing openings 85,86 to the gas exchange to improve.

The second piston 68 is opposite the first piston shaft 63 only by a number of labyrinth grooves 103 sealed because the sum of the velocities of the first and second piston increases the effectiveness of the labyrinth seal favored in the work cycle. Instead, piston rings can also be provided. It is favorable that of the two Pistons 62,68 only one, namely the second piston 68, which-

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must have like sealing elements. This reduces the friction losses and the wear and tear.

Each first piston pin pin 64, 65 tapers outwards in a stepped conical manner. Each first connecting rod 66.67 is with a complementary stepped conical opening on the associated first piston pin pin 64,65 by means a locking ring 104 and 105 held.

In the cylinder 8 is a feed connector 106 for scavenging air or an air-fuel scavenging mixture with a right angle to a longitudinal axis 107 of the crankshaft 4 arranged mouth plane surface 108 screwed. The feed nozzle 106 has an outlet opening 109 and a labyrinth seal arrangement 110 in the orifice plane 108 equipped,

Is outside of the first connecting rod 67, a fitting at the mouth end face spool 111 mounted The control slide 111 is formed like C-essentially and opens with a recess 11 2 (Fig. 14) the outlet port 109 during the compression stroke in the range of from just after the top dead center position until shortly before the bottom dead center position of the first piston 62 increasing to the full cross section and then decreasing again. During the rest of the travel of the first piston 62, the outlet opening 109 is closed by the control slide 111.

In FIG. 13, the nozzle bodies 18 and the beam reflectors 27 are each drawn offset by 45 °. On the Crankshaft, a flywheel 113 is mounted,

14, the electrode 82 is electrically insulated 114 between its exposed ends encased and sealed with the insulation 114 via a sealing ring 115 of the cover cap 84. In the area below The cover cap 84 is passed through an electrode 117 connected to an ignition cable 116, which electrode is connected to the upper exposed end of electrode 82 is a spark gap

forms and causes ignition sparks at the lower end of the spark plug 16,. . -22-

The operation of the machine 61 is as follows:

In the relative position shown in FIGS. 13 and 14, the pistons 62, 68 have just finished their working stroke. The burned gases have largely flowed out through the outlet openings 100, 101, and fresh air is through the scavenging openings 85, 86 into the first combustion chamber 74 and via the nozzle openings 1 $ | _; only partially flowed into the second combustion chambers 77, 79. These flow processes continue until the second piston 68 means. its uppermost control surface the flushing openings 85, and the outlet opening 100 closes. Before this, fuel is injected through the flushing opening 85 by the injection nozzle 96 and, if necessary, water preheated by the injection nozzle 97 is injected through the flushing opening 86.

This is followed by the compression stroke, which also completely fills the second combustion chambers 77, 79, during which the pistons 62, 68 generate negative pressure in the cavity 90, the flushing chambers 87, 88, the pump channels 92, 93 and the pump chamber 9I and - in the case of the control slide 111 open mouth surface 108 of the feed nozzle 106 - suck fresh air into the interior of the machine 61. In the area of greatest compression, the ignitable mixture is ignited by the spark plug 16. The combustion pressure in the first combustion chamber 74 acts on both pistons 62, 68 and a reaction jet ^{pulse for each nozzle opening 19 and a} further, but smaller, pulse at each of the jet reflectors 27 on the associated piston 62 or 68 due to the progressive combustion in the second combustion chambers 77, 79. As soon as the outlet opening 100 is exposed by the second piston 68, burnt gas flows off. Shortly thereafter, the flushing openings 85, 86 are also opened so that the fresh air compressed by the control slide 111 after the opening surface 108 has been closed into the first combustion chamber 74 and from there into the second combustion chambers 77 »79.

-23-

130041/011 «

can flow.

The machine 61 is advantageous in several respects. The negative effect of the parallelogram of forces Connecting rod length and crank radius is compared to conventional Machines with the same stroke volume are much cheaper, so that there is an increased loss of friction and the emergence of eating symptoms - in the now considerably increased, forces acting on the piston - has been prevented. Furthermore, the same is previously manageable highest piston speed twice the speed and thus twice the number of work cycles, ever Time unit achievable, as well as a significantly more favorable power-to-weight ratio of the machine 61. Tilting moments are through There is no need to fear the distributed arrangement of the nozzle bodies 18 in the pistons 62, 68. Plus the kinematics of the crankshaft drive compared to comparable single-piston machines and the balancing of the inertia forces, as far as possible, completed.

Patent Attorneys Dfpl.-Ing. Horst Rose Dtpi.-I.sg. Peter Kose!

130041/0118

Claims (1)

DIPL-ING. HORST RUSE DJPL-ING. PETER KOSEL PATENT LAWYERS _{Ä Ä} _. _{Ä Ä A} _ Our file number: 1716/13 Bad Gandersheim, 27. MAR. 1980 Karl BURGSMÜLLER PATENT CLAIMS Internal combustion piston engine with at least a cylinder accommodating at least one piston in each case, each piston having at least one connecting rod with a crankshaft articulated, and with each cylinder a combustion chamber that leads into a first combustion chamber of changing volume during operation of the machine and at least one within one Outer contour of the associated piston arranged second combustion chamber of during operation of the machine constant volume is divided, wherein the first combustion chamber with the second combustion chamber over at least one connection opening determined by the piston is in constant communication, characterized in that that the at least one connection opening at least is partially designed as a nozzle opening (19; 41). 2. Machine according to claim 1, characterized in that the at least one nozzle opening (19) through an in the nozzle body (18) inserted into the piston is formed, 3. Machine according to claim 2, characterized in that the nozzle body (18) at least in the top dead center position of the piston (7) with a passage of the nozzle body (18) for assembly purposes, from externally accessible opening, e.g. threaded hole (15; cf. 27,59), in a cylinder head (14) is aligned. 4. Machine according to one of claims 1 to 3, characterized in that the nozzle opening (19) in the Piston (7) with its longitudinal axis (22) in a right 130041 / 011S ^ - ■ ORIGINAL iN9PECTS3 at an angle to a longitudinal axis (23) of a piston pin (5) plane and to a longitudinal axis (24) of the piston (7) in the direction of a side which is comparatively heavily loaded during the working stroke of the piston (7) Shank surface (25) of the piston (7) is arranged offset. 5. Machine according to claim 4, characterized in that the plane through the longitudinal axis (24) of the piston (7.) runs. 6. Machine according to claim 4 or 5, characterized in that the longitudinal axis (22) of the nozzle opening (19) the longitudinal axis (23) of the piston pin (5) intersects. 7. Machine according to one of claims 1 to 3, characterized in that the nozzle opening (19) in the Piston (7) coaxial with a longitudinal axis (24) of the piston (7) is arranged. 8. Machine according to one of claims 1 to 7, characterized in that the nozzle opening (19) in one Piston head (17) is provided, which is hood-shaped and on its circumference with the piston (7) over a ² ^ thread (26) is connected gas-tight. 9. Machine according to one of claims 1 to 8, characterized in that the first (20) and every second (21) Combustion chamber can be connected to one another by at least one filling channel (29), and that a confluence each filling channel (29) into the second combustion chamber (21) by a resilient on an inner wall (30) of the valve tongue (31) adjacent to the second combustion chamber (21) can be closed. 10. Machine according to claim 9 _f, characterized in that a plurality of valve tongues (31) are components of a valve cap (33) fastened to the piston (7). -26- 130041/011 * Ol 11. Machine according to claim 1, characterized in that the at least one second combustion chamber (21) as a circumferential groove in the piston (7) and the nozzle opening (41) as an annular gap between a piston head (17) and an inner surface (42) of the cylinder (8) are formed. 12. Machine according to claim 1, characterized in that the at least one second combustion chamber (21) between the piston (7) and an elastically deformable, hood-shaped piston head (17) is formed so that an edge (120) of the piston head (17) has several passage openings (122) and on the piston (7) is supported that the nozzle opening (41) as an annular gap between the piston head (17) and an inner surface (42) of the cylinder (8) is formed, and that the piston head (17) by at least one adjusting screw (124) can be biased by changing the width of the nozzle opening (41) with respect to the piston (7). 13. Machine according to claim 12, characterized in that a frustoconical head (125) of the adjusting screw (124) engages with a notch profile (126) in a complementary groove profile (127) of the piston head (17). 14. Machine according to one of claims 11 to 13, characterized in that a peripheral region of the piston head (17) is provided with a high-temperature-resistant and wear-resistant armor (43). 15. Machine according to one of claims 11 to 14, characterized in that in the inner surface (42) of the cylinder (8) or the cylinder head (14) enlarges the annular gap in the area of the top dead center position of the piston (7) annular recess (47) is provided. 16. Machine according to one of claims 11 to 15, - dadujch characterized in that a peripheral region of the piston head (17), starting from a central region (48), a upwardly and inwardly extending first inclined surface (49) and a secondly downwardly and inwardly extending Has inclined surface (50). -27- 130041/0116 Ol 17. Machine according to one of claims 1 to 7, characterized characterized in that the at least one second combustion chamber (21) is designed as a circumferential groove in the piston (7) and the at least one nozzle opening (19) runs in a central region of a piston head (17). • 18th Machine according to Claim 17, characterized in that the nozzle opening (19) is arranged coaxially with the piston (7) and is connected to the circumferential groove by branch channels (51) distributed over the circumference. 19. Machine according to claim 17 or 18, characterized in that between the first (20) and the second (21st) combustion chamber, a piston head (17) with one with a
Inner surface (42) of the cylinder (8) cooperating piston ring (52) is arranged. 20. Machine according to claim 19, characterized in that the piston ring (52) at the top one at a distance from the inner surface (42) of the cylinder (8) located bevel (53). 21. Machine according to claim 19 or 20, characterized in that the piston ring (52) is hollow. 22. Machine according to claim 19 or 20, characterized in that that the piston ring (52) has a circular or circular ring-shaped cross-sectional area, that the piston ring (52) in an outwardly V-shaped extended circumferential groove (54) of the piston (7) protrudes, and that a lower inclined limit tongue surface (55) of the circumferential groove (54) with at a distance from each other distributed over the circumference, the piston ring (52) supporting brackets (56) is provided. 23. Machine according to one of claims 17 to 20, characterized in that in the inner surface (42) of the cy- Linders (8) in the area of the top dead center position of the
Piston (7) at least one extends over only part of the
Cylinder circumference extending pocket-shaped recess (58) is provided. 24. Machine according to one of claims 11 to 23, characterized in that the piston head (17) by means of _ ₂ g_ 130041/0118 A central threaded extension (44) is screwed into a threaded bore of a piston intermediate base (45). 25. Machine according to one of claims 11 to 24, characterized characterized in that the second combustion chamber (21) forming circumferential groove in the piston (7) from the outside to inside initially expanded and then narrowed. 26. Machine according to one of claims 1 to 25, characterized in that opposite each nozzle opening (19) Beam reflector (27; 59) arranged in a cylinder head (14) is. 27. Machine according to one of claims 1 to 26, characterized in that a water injection nozzle in the cylinder (8) (60) takes effect. 28. Machine according to claim 27, characterized in that the water injection nozzle (60) is coaxial with the nozzle opening (19) is arranged. 29. Machine according to claim 27 or 28, characterized in that the water injection nozzle (60) is concentric with a beam reflector (59) is arranged. 30. Machine according to one of claims 1, 2 and 8 to 27, characterized in that in a two-stroke engine (61) a first piston (62) is guided in and with the cylinder (8) two first piston pin pins arranged at diametrically opposite points of a first piston skirt (63) (64,65) is articulated in each case on a first connecting rod (66,67) that concentrically in the first piston shaft (63) a second piston (68) guided and with a second piston pin (69) is articulated to a second connecting rod (70) arranged between the two first connecting rods (66, 67) is, the crankshaft (4) aligned first crank pins (71,72) for the first two connecting rods (66,67) and a second crank pin (73) offset by 180 ° with respect to the first crank pin (71,72) for the second connecting rod (70), and that the first 1300 * 1/0116 Oil combustion chamber (74) between the first (62) and the - /. wide (68) piston is arranged and the first (62) and second (68) pistons each have a second combustion chamber (77; 79). . 05 31. Machine according to claim 30, characterized in that that at least one of the two first piston pin journals (64,65) on the one hand always with a pre-compression chamber (87,88) of the cylinder (8) connected and on the other hand controllable by the second piston (68) with the first combustion chamber (74) has connectable flushing opening (8 5,86). 32. Machine according to claim 31, characterized in that each precompression chamber (87; 88) is constantly with one Cavity (90) of a crankcase (2) is connected. 33. Machine according to claim 31 or 32, characterized in that that the cylinder (8) is closed by a cylinder head (14), and that a pump chamber (91) between the cylinder head (14), the cylinder (8) and the first piston (62) via at least one pump channel (92, 93) is constantly connected to the pre-compression space (87, 88). 34. Machine according to claim 33, characterized in that the at least one pump channel (92, 93) has a groove in an inner surface (42) of the cylinder (8). 35. Machine according to one of claims 31 to 34, characterized in that the at least one flushing opening (85.86) in the area of the top dead center position of the first piston. (62) with a longitudinal axis (94,95) one in one Wall (118) of the cylinder (8) mounted injection nozzle (96,97) is aligned. 36. Machine according to claim 35, characterized in that the extension of the longitudinal axis (94.95) of the at least an injection nozzle (96,97) extends at a distance from a longitudinal axis (89) of the first piston (62). 37. Machine according to claim 35 or 36, characterized in that the longitudinal axis (94.95) of the at least 130-041 / 0110 C. ORIGINAL INSPECTED An injection nozzle (96, 97) is inclined inward and upward from the outside and bottom with respect to the cylinder (8). 38. Machine according to one of claims 30 to 37, characterized in that each at least one outlet opening (100,101) are provided in the first piston shaft (63) and in a wall (118) of the cylinder (8). 39. Machine according to claim 38, characterized in that the outlet openings (100,101) in the circumferential direction are offset in relation to the first piston pin pin (64,65). 40. Machine according to one of claims 30 to 39, characterized in that in an intermediate piston base (75) of the first piston (62) and / or in a piston head (76) of the second piston (68) in each case at least two nozzle openings (19) arranged distributed evenly in the circumferential direction are. 41. Machine according to claim 40, characterized in that in the piston crown (75) and / or in the piston crown (76) are arranged in alternation with the nozzle openings (19) beam reflectors (27) that with each Nozzle opening (19) of the piston crown (75), a beam reflector (27) of the piston crown (76) is aligned and vice versa. 42. Machine according to one of claims 30 to 41, characterized characterized in that each first piston pin pin (64,65) tapers outwardly in a stepped conical manner and each first connecting rod (66,67) with a complementary stepped conical opening on the associated first piston pin pin (64,65) is held by means of a locking ring (104, 105). 43. Machine according to one of claims 30 to 42, characterized in that a feed connector in the cylinder (8) (106) for scavenging air or an air-fuel scavenging mixture with a perpendicular to a longitudinal axis (107) the crankshaft (4) arranged mouth plane surface (108) opens, and that on one (67) of the first connecting rods 130041/011 « ORIGINAL INoFbCTED 2 " - Ol (66,67) a control slide (111) cooperating with the mouth plane surface (108) is attached. 44. Machine according to claim 43, characterized in that the feed connector (106) in the mouth plane surface (108) has a labyrinth seal assembly (110). 45. Machine according to claim 43 or 44, characterized in that the control slide (111) is substantially C-shaped and with a recess (112) a Outlet opening (109) in the orifice plane surface (108) during of the compression stroke in the range from shortly after the top dead center position to shortly before the bottom dead center position des.ersten piston (62) increasingly opens up to the full cross section and then decreases again. Patent Attorneys.-Lng. Horst Rö ~ e DJj3l.-lng. Peter Kos' ·! 130041 / O11S ORIGINAL INSPECTED