DE1775956A1 - ARRANGEMENT OF PISTON AND PISTON RINGS FOR COMBUSTION ENGINES - Google Patents

Description

DR. MOLLER-BORe DIPL.-PHYS. DR. MANITZ DIPL.-CHEM. DR. DEUFEL DIPL.-ING. FINSTERWALD DIPL.-ING. GRÄMK0W

177CQCC PATENTANWÄLTE II / <J% f * ßO

Mak / th - G 216? 26th NOV. WL

SEALFIRE
2bis, rue Royale, Luxembourg

Arrangement of pistons and piston rings for internal combustion engines

The invention relates to a piston assembly and piston rings for internal combustion engines.

Pistons for internal combustion engines have segments or rings, which have to fulfill the double task, namely the sealing of the combustion chamber between the piston and Cylinder ensure and prevent most of the oil thrown against the walls of the cylinder enters the combustion chamber.

In general, three or more segments or rings have hitherto been provided, of which at least two, the so-called compression or piston rings, allow the passage of gases from the combustion chambers into the crankcase during the compression stroke, the combustion stroke and the exhaust stroke and from the housing into the Resist combustion chambers during the intake stroke. So far, this has mainly been achieved through the following means used jointly or individually: 209ÖÖ1 / QÖ77

OBlGlNAL

Greatest possible restriction of the clearance between piston rings and the piston grooves receiving them, inclined design of the piston rings in such a way that they are in their grooves Circles are worn, which are arranged at two ends of a diagonal of their cross-section, strongest possible Reduction of their cross-section and finally shaping of the circumference, which is closely matched to the cylinder wall.

The oil control ring is located in a groove below of the two above, generally at the top of the shaft of the piston that slides and grinds in the cylinder. the Oil control elements essentially consist of two lips j they are either supported by a one-piece ring Worn out of cast iron or consist of rails made of steel which are held against the cylinder and the walls of the groove by a Expanding springs are printed or they consist of sections of steel lips that are almost tight or butted together are elastically interconnected and an arrangement of two circular against the cylinder held lips. The surfaces of today's oil control rings are either stored with little play or are pressed elastically as tightly as possible against the lateral walls of the piston groove} in all cases the space between the two lips is open and communicates to a large extent with the bottom of the groove that in turn has an essential connection with the crankcase.

Certain internal combustion engines, especially diesel engines, have a larger number of piston rings, with the Sealing with more than two compression rings and / or

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wiping takes place with more than one oil wiper ring.

In other words, according to the current state of the art the group consisting of pistons and piston rings segments, the seal between the combustion chambers and the crankcase on the one hand ensured by a succession of obstacles like formed by the compression rings and oil scraper ring

which in their butes with the least possible Game are stored, where öedee of these obstacles Sealing contributes to the added proportions of the pressure losses that occur at the blow-through circuit, and on the other hand the oil is reached by scraping the cylinder walls using these series-connected obstacles, the main suppression function being the wiper or rings (s) is due.

The disadvantage of this present arrangements is the fact that the location of the role and the interaction of each piston ring with the piston at any moment of the working game can not be forcibly defined, thereby \ results in a transient and unreliable behavior, at the same time the The number of elements and the space occupied is greater than absolutely necessary.

On the other hand, these piston rings are at risk of paralysis due to impurities in their ring groove of the piston exposed. These disadvantages now make two compression rings or more necessary. In addition, changes to the

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Gas losses from the combustion chambers, called "blow-by", which are based on giving rise to pressure peaks above the wiper ring, which are able to change its behavior to disturb in operation at this point in certain cases when this pressure increases the contact pressure against the cylinder exceeds and causes its momentary lifting from the wall of the cylinder. These phenomena are the Main reasons for the excesses in oil consumption that often occur with in-line engines, even though they are off apparently identical (parts are put together - they have passed the same controls - considerable Show deviations in oil consumption. After all, efforts are made to achieve an economical oil consumption Limiting and isolating the smallest possible amount of oil that escapes during stripping or scraping, which is what The lack of or decomposition of the lubricant present in the top of the cylinders increases the risk of their damage brings itself.

The novel piston-piston ring arrangement according to the invention, on the other hand, only has the assignment of the piston in principle two things:

A compression ring and an oil retaining ring, wherein these elements are designed in such a way that each piston ring no longer acts as an obstacle to gas leakage acts with uncertain and unreliable behavior, but like a valve that is assigned to the piston in the manner of a seat but also with the other segment or piston ring comes into play, the interaction of all of these Elements is forcibly determined by design.

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This result is obtained by looking at the whole or makes use of parts of the following means: The compression ring and its groove are on the one hand like this constructed to allow access to the in the Combustion chamber existing pressure on all or part of the upper surface of the piston ring abolish. If the surfaces of the piston ring and ring groove are pressed against each other and the access "

possibility of this pressure on the undersides of the piston. ™ To prevent the ring when the undersides of the piston ring and groove are pressed against each other, one takes care of the other by grinding or mechanical perfection for an increased sealing of the undersides of the piston ring and Groove. So the compression ring is exposed to increased pressures during the work cycle, which affects its inertia and oppose the friction on the cylinder and its surface opposite the combustion chamber energetically against the Press the groove by forcibly closing the gas passage.

The oil control ring and its ring groove are designed in such a way that j that:

a) the pressure resulting from the permanent loss through the compression ring provides access to the entire Surface of the oil control ring or part of it Has;

b) that by combining the weight of the piston ring, its contact pressure against the walls of the cylinder and either the play of the piston ring in its groove or the contact pressure of the surfaces of an elastic piston ring against its groove and its play on the one hand with the largest amounts of residual passage on the compression ring and the oil stripped on the cylinder that

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Subtracting this permanent loss as well as the stripped one Oil takes place exclusively with passage between the adjacent walls of the piston ring and the groove, but never between the piston ring and the cylinder; and that on the other hand with the smallest amounts of residual loss of the compression ring and the oil stripped from the cylinder, the pressure of the residual loss is at least b is slightly greater than that of the dynamic pressure of the oil in the bottom of the hat of the oil control ring prevails}

c) that by grinding or mechanical perfection an increased sealing of the surfaces of the piston ring and groove is brought about.

The functionality of the oil control ring can still be improved, by allowing dynamic pressure access of the stripped oil on all of its base or one Part of this enables and in which one provides openings in the bottom of the groove, which ensure the return of the oil and prevent blowing past the housing in such a way that the | dynamic oil pressure of the bottom of the groove during the downward - the piston speed is reduced or suppressed. During the work cycle, the remaining Loss of the compression ring caused pressure and that of the oil control ring is limited to values below those that cause the lips of the oil control ring to lift off the cylinder; these pressures counteract each of its surfaces and determine an equilibrium position due to the inertia force and the friction on the cylinder, the simultaneously opens two passages to the housing, one for

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the gas originating from the residual loss, the other for the oil stripped on the cylinder.

Under these different conditions, the oil control ring performs the following functions:

a). It is forcibly given its scraping function when going downhill upright and secures up to the maximum wear conditions of the engine plays the role of an exhaust valve for blowing past and, if necessary, provides for the return the stripped oil to the housing, as it prevents the risk of losing contact with the cylinder, is protected}

b) On the upstroke it forcibly carries the oil that the has lubricated the upper parts of the cylinder back, which on the one hand lubricates them more generously can without consuming oil and on the other hand the lubricant from the upper parts of the Cylinder is renewed through recirculation and replacement.

The high one, with a compression ring according to the invention *

and through the forced oil circulation above the oil control, The sealing produced by the ring ensures the piston crown a property that cannot be achieved with conventional piston rings as well as one less increased by overpressure of the burner effect Temperature as well as good lubrication; For these three reasons, the entire piston crown can be used, the mechanical load-bearing capacity between piston and cylinder under working conditions comparable to that of the piston skirt to extend what, among other advantages, the cooling of the piston and its mechanical behavior improved.

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- σ -

Of course, you could also use the invention resort to more than two piston rings by making each operate as a positive valve, as above set out and explained in the description. This * would on the one hand result in an advantage of security for the case where one of the multiple organs would fail, on the other hand the disadvantage that during the Working cycle, the pressure differences used according to the invention were divided and valve movements were given to each piston ring, which is safe for everyone would reduce its coercive effect; Finally, there is the disadvantage that you have to make do with additional organs would have to.

The invention is illustrated below with reference to the drawing, for example described; in this shows:

Pig. 1 a piston arranged in a cylinder with a compression ring and an oil control ring, which are used in ring grooves,

FIGS. 2 and 3 are partial views of the piston arrangement shown in FIG. 1, in each of which a compression ring inserted into its annular groove on an enlarged scale is shown

4 to 6 partial views of the piston arrangement shown in FIG. 1, in each of which an oil control ring inserted into its annular groove on an enlarged scale is shown

Fig. 7 is a partial view of the piston arrangement shown in Fig. Λ , in which another type of oil control ring inserted into its annular groove is shown on an enlarged scale,

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7a, 7b and 7c detailed views of details of the Ring groove and the oil control ring in Fig. 7 in enlarged scale, ■

8 shows a compression ring inserted into its annular groove on an enlarged scale,

FIGS. 9 to 12 show detailed views of FIG

Compression rings or oil f wiper rings on a larger scale and

13 to 15, 15a and 15b are detailed views of one in his Ring groove used compression ring on an enlarged scale, in which between the back of the compression ring and a ring seal is arranged on the hat base.

Fig. 1 shows a piston of the internal combustion engine 101 in a cylinder 102. The piston has a shaft 103, which is fitted in the usual manner in the cylinder 102 Piston also has a piston ring carrier head 104. The ^

Outside diameters at various heights of this head are typically a few tenths of a millimeter smaller than that of the shaft, according to a feature of the invention, they can be enlarged so that the walls 105 and 106 of the Head 104, when the engine has reached its working temperature, come into mechanical contact with the cylinder, which causes the walls of the head 104 in Extension of the shaft can be formed, with only the thermal correction mentioned must be taken into account.

*) 'Fi £. 16 is a detailed view of an oil scraper ring in which one additional hat is shown below the ring.

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This head basically has two grooves, namely one, 107, for the compression ring 111, the other, 108, for the oil control ring 112. The bottom of the groove of the oil control ring largely protrudes from the housing in the usual way openings 109 in connection, which usually open in the middle or directed downwards with respect to the groove 108; According to one feature of the invention, however, they preferably open into the groove at the same level or above it The top and the top wall of these openings are then perpendicular to the piston axis or are preferably to the topmost Point of the inner cavity of the piston oriented towards, as is the case with the wall 110.

A compression ring 111 is in the groove 107 and an oil control ring 112 in the NuA; 108 arranged. This arrangement, consisting of pistons and piston rings, is distinguished through the following points:

The compression ring 111 is a known type of ring that is preferably coated with a hard wearing layer, for example chromium or molybdenum; he is in the Groove 107 mounted with normal clearance, usually on the order of 0.01 to 0.05 mm between the side surfaces amounts to; assigned to NuI? 107 it has a rectangular or slightly trapezoidal cross-section and the following details:

Primo: The compression ring and groove join when the adjacent top surfaces of the piston ring and groove are pressed against one another by a means that reserves access for the pressure in the combustion chamber against all or part of the top of the compression ring. This result is obtained, for example

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compulsorily, FIG. 2, by a slight opening of the surfaces of the compression ring 213 and its groove 21A from Piston seen outwards, which makes its contact quite far from the outer edge of the surface 213 and in less secure Way, Fig. 3 shows an approximately parallel construction of the adjacent upper sides of the piston ring 313 and the groove 314, albeit not in a tight manner, secures - case the normal production of piston rings and grooves today; this procedure is actually less secure, because this is within the limits of the manufacturing tolerance it is not ruled out that the load-bearing behavior is established and between the surfaces 313 and 314 · - in the vicinity the circumference a grinding takes place, whereby the pressure of the combustion chamber 315 cannot pass between them can when they are pressed against each other.

Secundo; The compression ring and its groove are butted when the adjacent undersides of the ring and groove are "pressed against each other" by a means whereby the pressure from the compression chamber is retained, which goes to the bottom of the groove through the construction of the "primo" upper surfaces and through the game of the ring in ^

the groove to prevent this pressure from penetrating between these adjacent undersides. That Result is z. B., Fig. 2, positive by a slight opening of the undersides of the compression ring 216 and the Groove 217 of the piston received to the outside, whereby their contact is secured quite far from the outer edge of the surface 216 where the angle b of this opening is quite small- thus the pressing of these two surfaces against each other due to the flexibility of the ring during the engine work cycle takes place. You get this result, however

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in a less secure manner according to FIG. 3 by the fact that the adjacent undersides of the Hinges 316 and the groove 317 Constructed exactly parallel and tight, which is not the case with today's production of the surfaces of rings and grooves The case is that, as mentioned above under "primo", only in run roughly parallel and are not tight.

Tertip: The adjacent undersides of the compression ring and groove are adjusted with respect to each other and / or attached to each other in such a way that when these two surfaces are pressed against each other, an increased seal occurs between them, the criterion of which is associated with a good circumferential load-bearing capacity of the ring on the cylinder and a limited one Machining clearance limits the "blow-by" volume to a value that is at most the same, generally much smaller and much more stable than that which has been achieved up to now with good piston ring designs with multiple compression rings.

This result is obtained, for example, according to FIGS. 2 and 3 by grinding in the adjacent undersides of the piston ring 216 and 316 and / or the groove 217 and 317 *, preferably against each other, whereby the piston ring when grinding in a constriction is the same as that which it receives from the cylinder, exposed, but the result can also be achieved by machining these surfaces with very high precision, the piston ring being subjected to the same constriction.

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The oil control ring 112 is also known as a piston ring Kind; its cross section is rectangular or slightly trapezoidal and has the following special features associated with the groove 108 on:

P rimos oil control ring and groove joint when the adjacent upper sides of oil control ring and groove are pressed against each other, by means of a means that allows access to the entire surface or part of the oil control ring for the pressure prevailing in the clearance between piston and cylinder above the piston ring. The result Δ is obtained in a positive manner, FIG. 4, for example through a slight opening c in the upper sides of the oil control ring 416 and its groove 417 outwards as seen from the piston, whereby their contact is ensured quite far from the outer edge of the pool 416 and in less certain way, FIG. 5j is made possible by an approximately parallel but not tight construction of the adjacent upper sides of piston ring 516 and groove 517, which represents the normal present-day production case of the surface of piston rings and grooves; this second method is actually less reliable, since it does not rule out the possibility of the bearing pressure being set within the limits of the machining tolerances and of grinding in between the surfaces 516 i

and 517 causes near the perimeter, whereby not is allowed that in the clearance 518 between pistons and cylinder pressure can penetrate between them if they are pressed against each other,

Secundo: Oil control ring and groove have, when the adjacent undersides of ring and groove are pressed against each other, a means of holding back the access of the oil pressure prevailing in the clearance between piston and cylinder below the ring against the entire underside of the oil control ring or against part of it.

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This result is compulsorily obtained. Fig. 4 either through, a slight opening / the underside of the oil control ring 419 and its groove 420 as seen from the piston outside, thereby ensuring their contact fairly far from the outer edge of surface 419 or less secured way, Fig. 5 »by an approximately parallel but not tight construction of the adjacent undersides of oil control ring 519 and groove 520, what the normal Production case reproduces the surfaces of piston rings and grooves; this second method is in fact less sure, since this does not rule out that in the Manufacturing tolerances of the bearing pressure and a grinding in between the surfaces 519 and 520 in takes place near the circumference, thereby preventing the dynamic pressure of the oil in the clearance 521 between Piston and cylinder adjusts itself and adjusts itself between these when they are pressed against one another.

The interruptions in the continuity of the underside of the groove of the oil control ring, which are caused by the usual machining modern pistons with regard to the presence of openings for the outflow of oil or for thermal insulation slots are provided, must be omitted.

Although the feature mentioned under "secundo" is favorable an arrangement according to the invention, it is useless for the case where the piston with a per se known means for withdrawing oil from the crankcase is provided, which is on the cylinder during the downstroke stripped through the lower lip of the oil control ring

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is, these means for example from a groove or a collecting pocket and openings penetrating the shaft of the piston are provided.

Tertio: The adjacent upper sides of the oil control ring and groove are fitted and / or supported against each other in such a way that when the two surfaces are bridged against each other, an increased seal is created between them. In association with a good load-bearing capacity along the circumference of the oil control ring on the -

Cylinder and a limited editing game without help ^ the wear of the multiple compression rings a regulation of the entrained in the upper parts of the cylinder Oil, with this result at least equal, generally better and more regular than that by good Piston ring configurations with multiple piston ring assemblies of the known type can be achieved.

This result is given by, for example, I "ig. 4- and 5j Grinding in the adjacent upper sides of the rings 4-16 and 516 and / or the groove 417 and 517 »preferably against each other, reached, whereby the ring is exposed to a constriction equal to that of the cylinder | takes in; This can also be achieved by machining these surfaces with very high precision, the Ring is exposed to the same constriction.

Quarto: The oil control ring is mounted in its groove with a clearance that is determined by the following criteria: When the piston has a means other than the space between adjacent undersides of the oil control ring and the groove

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in order to lead the oil wiped off by the oil control ring to the housing, the clearance of the ring must in its groove:

a) be sufficient to remove most of the ■ permanent loss of the compression ring in the housing, without the gas pressure of the permanent loss in the circular space between pistons at the moment of the peak of this quantity and cylinders above the oil control ring do not have the specific support pressure under the most unfavorable conditions reaches or runs the risk of reaching the lips of the oil control ring on the walls of the cylinder;

b) be limited, however, so that in the ranges or speeds which lead to the lowest "blow-by ^M volume, the ^M blow-by" pressure above the ring is at any moment clearly above the dynamic pressure of the oil on the ground the groove of the oil control ring remains in order to prevent that, even if the pressure peak of the blow-by opens the passage between the surfaces, the pressure of the oil at the bottom of the groove does not keep the passage open, especially during the work cycle, and so does the oil at the bottom of the groove makes it possible to deposit on the cylinder above the oil wiper element.

This is the return of the oil stripped on the cylinder to the crankcase through the clearance between adjacent ones The undersides of the oil control ring and groove are ensured, the above criteria a) and b) must take the play into account, which is necessary for the passage of the oil, which is therefore superimposed on the above-mentioned game.

4 and 5, for example, these results are obtained through the games 422 and 522 of the oil control rings in their

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Grooves that are set so that the contact pressure of the oil control rings 412 and 512 on the cylinder above corresponds to the conditions mentioned.

The details mentioned above under primo to quarto have been described for an oil control ring of fixed height, for example by casting, as in FIGS. 4 and 5 shown, written on or punched from steel,

broken through and folded, as Fig. 6 shows, λ

This embodiment shows a piston 601, of which the area between shaft 60J and head 604 is shown are. Its groove 608 contains an oil control ring 612 from the known design made of punched, openwork or folded steel. With these things one can take into account, that their surfaces 616 and 619 are only continuous Surface on part of the radial width bounded by the edges 625 and. 624 of the central breakthroughs 625 offer, implement the conditions mentioned under primo and secundo in a favorable manner by forms each surface of the groove with a central portion 626-627 for the top and 628-629 for the bottom, which is parallel to the adjacent side of the ring. Then one creates an access for the pressures mentioned above against the surfaces of the rings by means of openings in the surfaces of the groove c and f, which are oriented outwards from the piston are. In this case, the condition tertio is created by grinding in the ring under its operating constriction ensured as well as by the bearing pressure of the groove or by high-precision machining of the adjacent upper sides parallel to ring and groove, or through the interposition of a Seal between these surfaces; the radial width of this support is at least equal to the sum of minimal

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Width of the covering necessary for sealing, in of the order of 0.3 mm, and the maximum radial Wear of the cylinder 602 and the sing 612. Finally, the condition of quarto becomes due to the play 622 between the ring 612 and the parallel walls 626 ^ -627 and 628-629 of the bottom of the groove 608 ensured.

But you can also use those defined above under primo to ijuarto Features of a known oil control ring, a so-called three-part ring, which is shown in FIG is to apply. This type of ring consists of two rails 730 and 731, which are connected by means of a central Expanding device 732 on the one hand by its outer lips against the cylinder, on the other hand by the middle edge their outsides are pressed against the surfaces of their groove.

This type of ring leads to the conditions in the rest position primo and secundo, through angular openings g and h between the adjacent surfaces of their rails and their groove 716 and 717 on the one hand, 719 and 720 on the other hand; however, in operation, when there is friction and inertia on them, the rails 730 and 731 can go against the place adjacent walls 717 and 720 and run the risk of not to meet these conditions. An inventive The means of restoring these primo and secundo conditions is to change the arrangements in accordance with the Figures 7a and 7h on each outside of the rail 716 and 716 719 near the perimeter with a very slight circular Knurling, for example 0.02 mm deep. Another remedy is to make a circular one Knurling of analogous thickness, 734 »736 - Fig. 7c - on to provide the outer edge of the surfaces of the groove. Another

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Means still consists in the circumference of the surfaces of the rails and / or the hat at the points 133, 134 and 135 to provide a finish that is insufficient, to be tight at the low pressures that occur.

The condition tertio is obtained with this hang exactly like in the previous one, by grinding in the ring on its constriction during operation and its groove support

or by machining the adjacent upper surfaces I.

of the ring and the groove with very high precision.

The quarto condition is created by the combination of the elastic contact pressure of the middle parts of the outer surfaces and 719 of the rails against the surfaces of the groove 717 and 720 with the game 736 uncl 737 ensured, whereby each The splint can approach its expander under the action of pressures acting on its outside and bring into play at most the same games among each other and their neighboring surfaces of the groove.

Fig. 8 illustrates an embodiment in which the Angle of the neighboring faces of a compression f

ring and its groove is open to the outside, the adjacent surfaces of the groove and ring are parallel over a portion 841-842 and 843-844 of the depth of the groove from the bottom of the groove - and then over a part 842 845 and 844 - 846 a slight opening i and j analogously which have according to the figures.

This arrangement is the same as the arrangement already shown in FIG. 6 for an oil control ring Compression rings like on oil control rings with only one or two adjacent faces of rings and grooves can be applied. ·.

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In addition to the features mentioned and illustrated, the piston and piston ring assemblies according to the invention reproduce, a large number of arrangements exist which provide more detailed details of the above Embodying characteristics and completing them by, however, the basic idea and the functioning of the novel Arrangements is retained.

b In the following there are some complementary explanations given to the aforementioned Figs. 1 to 8:

The entry bevels of the groove that have a significant Angle, for example 4-5 °, with the planes perpendicular to the Include the piston axis must not be confused with the small openings a, b, c, d, e, f, which are in Figs. 2, 4- and 5 can be seen, the angle of which is very small, for example equal to a fraction of a degree, as will be explained in more detail below. Without that, a principle contradiction to the invention with regard to the use of the chamfers at the inlets of the groove of the compression rings would exist, although these in the all-F are commonly used in the prior art, it did not seem necessary to represent them. Rather, it is expedient to have a bevel, a rounding or any on the inlets of the grooves of the oil control rings • 'Provide another form of angular separation that is favorable for the outflow of the medium. In these bevels are in Fig. 4 with 4-38 and 4-39; in Fig. 6 with 638 and 639; 738 and 739 in Figs. 7 and? a; Roundings 538 and 539 are shown in FIG.

The openings in the bottom of the groove 109, FIG. 1, do this blow-by and the scraped off oil to the housing, as already

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described; they can be found at 509, 5, 609, 6 and 709 in FIG. 7. The opening 609, FIG. 6, needs a special explanation;

Vie for the opening 109, Fig. 1, is already described, As is often used for modern pistons, these are formed by two long ■ slots in the groove of the oil control ring generally at a certain distance from this area

flow out.

According to the invention, the top wall 610 is this slot 609 connected to the groove 608 at the same level with or above its top 626-627 and is, starting from the Connection point 626 with the groove up to connection point 686 with the Vand of the central cavity of the piston connected to the uppermost point of this central cavity of the piston. The wall of the bottom of the groove is dashed in the sectors of no interest represented by the openings in the form of a slit. Also according to the invention is the inner wall of piston 640 connecting the inner wall of the stem to the open bottom of the groove at 628, against the uppermost point of the central cavity of the piston inclined and oriented.

7 shows another exemplary embodiment for the openings 709, if these consist of bores that are guided against the bottom of the groove; according to the invention is the penetration 74-1 of the bore 709 with the central cavity of the piston inclines so that its highest point is closer to the axis of the piston than its lowest point.

I ¹ Xg. 9 and 10 show a shoulder or a groove 94-7 and 1048 of the surface of each groove, respectively, in the groove of the compression ring and in the groove of the oil control ring

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Sealing with the surface of the segment sought when they are pushed against each other

11 and 12 each show the hat of the compression ring and the hat of the oil control ring in addition to the preceding grooves a paragraph 1149 and 1250 of the Surface of any hat that does not seal against the surface of the bing when pressed against each other offers special effort.

13 and 14 each show a known elastic seal, which is in the bottom of the hat "Compression ring is located between the bottom of the hat and the ring, and under working tension between the bottom of the ring and the bottom of the hat is mounted.

The seal 1368 according to FIG. 13 has a free cross section with four abutting lobes.

The seal 1469 according to FIG. 14 has a free cross section with four pointed lips, which lead to the outer roundings of the four lobes of seal 1368 are added.

Fig. 15 shows an elastic ring seal 1575 »which like in the previous cases on the bottom of the hat 150? of the compression ring 1511 between the bottom of the hat and the ring is arranged. Its cross-section shows a body in close contact with the bottom of the hat. This body has a rectangular shape in the example shown, but it can also have any other shape} on its the surface adjacent to the ring it hits one or more

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Edges 1576, 1577) which are in elastic contact with the Ring. The cross section of each of the rims 1576 and 1577 can be trapezoidal - the case of FIG. 14 - or have a geometric shape or a lip with a pointed and softer edge that prevents the flow of medium in the soil the groove in one or the other direction prevents} a combination of these possibilities can also be provided be, in particular two analog lips, but with opposite orientation to the movements i of the medium in both directions.

Fig. 15a shows an elastic ring seal 1575a »the completely fills the volume of the bottom of the groove except for the very narrow space which is reserved for the expansion of the sealing material and which by a very small Play of the seal in the groove or by installing gas bubbles in the sealing material (case of Fig. 15b) can be realized.

These different elastic, shown in Figs. 13 to ^ However, seals can also have any other known cross-sectional shape, for example they can f be square or rectangular. They are shaped or drawn or stamped from a product such as elastomers, while maintaining satisfactory characteristics Dimensions and elasticity to the temperatures of the bottom of the groove of the piston and the chemical attack to withstand hydrocarbons and combustion products. Synthetic rubber gives good results VITON obtained by Du Pont de Nomours with a Shore hardness of 70.

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The outside of the compression ring provided with the various seals preferably takes any shape that is able to the wear of the ring a slope, an angle or a rounding at the connection point to oppose its outer wall with the circumference of its surface. With this in mind, the ring 1311 According to FIG. 13, a symmetrically curved profile 1385 »eggs Ring 1411 according to FIG. 14 has a profile 1485 which is curved downward in contact. The ring 1511 according to FIG. 15 has a cylindrical shape Profile, which has a rounded 1585 with its top connected is. If the cones and bulges are not stand out strong enough so that with maximum wear or stress on the ring, a part of their profile hits it remains between the wear surface and the surface of the segment, so it is good to add a rounding here, as shown at 1585 in FIG.

16 shows a groove 1679 which is intended to be arranged beneath a groove in the ring. In the case of this figure, these in the shaft 1603 of a piston according to the invention in the vicinity of the groove 1608 is held Ölabstreif- W ring 1612; This groove is characterized by a connection 1680 with the shaft, is oriented towards the lower part of the piston, is progressive and without acute angles and is connected to the shaft via a connection 1681 and is located near the groove of the ring and has no sharp points Angle on. For example, choosing 7 ° for the angle at junction 1680 and 90 ° for the angle at junction 1681 gives a favorable result.

In order to explain how this novel arrangement works, it is sufficient to first determine the work cycle of a

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To consider four-stroke process, i.e., the one who the ring arrangement exposed to the most complex pressure conditions and the greatest errors in sealing and in Cause oil consumption is able.

The piston moves according to the arrow M in 1. In this shift, the compression ring, for example the ring 211 according to FIG. 2, is inertia and exposed to friction against the cylinder, both of which attempt to push the assembly against the top 214 of the groove to press, the explosion or combustion pressure prevailing in the combustion chamber 215 at top dead center, However, it exposes it to an oppositely directed very high force, which according to the invention acts on its upper side 213 acts, which this is structurally zugedafcht see the feature mentioned under primo in the description during its underside 216 is also protected against pressure in accordance with the structural design, which acts on its upper side 213 - see the feature mentioned under secundo in the description.

In terms of construction, the compression ring works So as a (flap) valve high seal (under tertio in the description mentioned feature) that the passage of the gases closes immediately after the explosion or combustion and during the entire working cycle of the piston only lets through load pressure losses between the circumference and the cylinder, losses due to clearance and residual losses that structurally already very low because of the bearing pressure of the underside against the underside of the groove are. This role of the valve, which is taken over by the piston ring, ensures a compulsory regulation of the losses, which so down to the lowest attainable height as a function of surface properties in question

2 0 9 8 8 1/0077 BAD ORiQSNAL

are. In the case of a conventional arrangement, on the other hand, the behavior is of the piston ring uncertain, it can fluctuate between the upper and lower load pressure or float and the Changes in the volume of the losses reflect this instability. This pressing force of the compression ring against the The wall of the groove opposite to the combustion chamber obtained according to the invention is higher, the greater the pressure difference is between the forces acting on the hanging from above and below, with the latter acting as a valve} consequently, there arises a disadvantage that the compression rings must be multiplied; namely, it leads to the favorable effect of the pressure, which has to overcome inertia and friction in order to ensure the tightness of each one, must be overcome.

Blow-by studies on engines with controlled Ignition were carried out, which were provided with a good usual ring formation from two compression rings, and then tests on pistons and piston ring assemblies with a single compression ring per piston of the invention, showed, under otherwise identical conditions, a significantly lower blow-by volume in arrangements with a single piston ring according to the invention compared with a good conventional piston ring design .

During the same engine cycle, the oil control ring, for example the ring 412 according to FIG. 4, subjected to the action of inertia and friction against the cylinder 402, which are assigned to each other and try to press this against the upper wall of the groove.

BAD ORIGINAL 20988 1/0077

Would a perfect seal of the compression ring prevail, the oil control ring 412 would remain pressed against the upper wall of the groove, a position in which it fulfills its main role as the oil deposited on the cylinder is stripped through its lips and then through the play 422, which is open under the ring, over the bottom of the groove 408 and the openings 409 to the housing returned. The oil is now not rising back to the margin between piston and cylinder 418 high, there is a you- "™ there is contact between the tops of the ring 416 and the groove 417 which are pressed against each other; with such a stroke, on the other hand, that would be against the upper lip of the oil control ring at the end of the upward stroke collected oil is not returned.

In reality, however, the sealing of the piston ring is not perfect. His losses cause an overpressure in the Game between the piston and cylinder 418, which acts on the top 416 of the ring 412, because the access of this print to this page by design - primary feature of the description - ensured * is; is this pressure enough to overcome the friction and inertia that the ring is pushing against the top of its groove press, it presses the ring against this underside by loosening it completely or partially from the game 422, in such a way that the amount of blow-through in the housing is subtracted by the small oil ring or the oil cord through the circle 418-422-409 is recycled; the pressing or the approach- ' tion of the oil control ring against its underside causes an increase in the oil pressure at 421, which is below this The underside acts during each downward stroke of the piston - · characteristic secundo according to the description - and in each

BATH 2.Q9 8 8 1/0077

Moment of the work cycles a compensation position of the Oil control rings make sure of that below will be spoken. Is the piston with a known means for drawing off oil stripped from the cylinder

f © S _ _ww . piston, this effect of the oil pressure below that of the oil control ring is suppressed.

The operation of the piston-piston ring assembly according to the invention will now be given during the intake stroke, who is the next to pose problems for the ring formation after the engine cycle, especially in engines with controlled Ignition. The reason for this is the dangers that the oil under the effect of the increased negative pressure in the Explosion chambers prevails, rises again, especially at medium or low loads.

During the first part of this measure, during the , Piston from top dead center in the direction of arrow M itself moved, the compression ring and oil control ring are forcibly against the top of their groove by the action of Friction and inertia, as well as the associated negative pressure, which may arise in the case of the oil control ring Added pressure of the stripped oil on the underside. The compression ring closes in these positions 211, FIG. 2, the connection between the combustion chamber 215 and the game 218 without any special sealing between piston and cylinder under the compression ring; the oil control ring 412, Fig. 4-, on the one hand opens the oil return uum housing over the game 4-22, which is then under his Bottom is open, but on the other hand brings the rise of the oil ruling through the remaining at 418 Negative pressure between the contacts of its top with

20988 1/0077

the top of its groove, which by design "serves particularly well, is caused to a standstill - feature tertio of the description - as well as his upper lip with the cylinder.

During the first part of this stroke, inertia tries to release the ring from contact with the upper wall *, only under the associated effects of friction, negative pressure J The hold of the oil control ring against the top of the groove remains on the top and oil pressure on the bottom secured.

Incidentally, several of the special features of the description have a conjugated positive effect «a) the increased sealing is only reached between the adjacent undersides of the compression ring and the groove - a special feature of primo - des Verdxchtungsringes and its groove;

b) the oil control ring takes the maximum effect of this negative pressure on its upper side - primo feature of the oil control ring and its groove;

c) the oil control ring takes due to its design f the maximum effect of the oil pressure on its underside - feature secundo of the oil control ring and its groove. In this way, an arrangement consisting of a piston and a piston ring according to the invention combines the most favorable Conditions to the upper adjacent surfaces of the oil control strip ring and to keep its groove in connection, as close as possible to top dead center, at the end of the Intake stroke; In addition, this positive hold brings with it increased effectiveness because of the condition tertio of the oil control ring and its groove.

During the compression and exhaust strokes, the piston moves from top dead center in the direction of arrow N.

2 0 9 8 8 1/0077

The compression ring 211, Pig * 2-, and the oil control ring 412, Fig. 4, during the first part of their stroke against their undersides due to the conjugate effect of the gas pressure, of friction and inertia printed * at * compression ring 21Ϊ closes the combustion chamber and leaves only a loss of est, which pulls the oil control ring 412 the residual oil from the upper lip on the cylinder is wiped off, as well as the remaining passage loss. During the last part of the piston stroke the inertial force is reversed, it comes ~ thus less strongly on the position of the rings, both in terms of on the gas loss as well as on the oil consumption, since the quantities in question and those of the one as well as the other are pretty low.

Compression ring and groove according to FIG. 3 have the same Functioning as already described with reference to FIG. 2, taking into account that, because of their Construction - after all, they are adjacent to the parallel surfaces to each other - meet the characteristics of primo, secundo and tertio that are required for compression rings and compression grooves according to the invention have been described. The same applies to the oil control ring according to FIG. 5, which, although they are adjacent have parallel surfaces that have features from primo to quarto of the oil control rings and their grooves according to the invention, which ensures the same function with them as with the oil control ring according to FIG. 4.

The oil control ring and its groove according to FIG. 6 have the same mode of operation, but here it applies that the construction of the adjacent surfaces of ring and groove shown in FIG. 8 for a compression ring and its groove are shown,

20988 1/007 7

Regulation extras through radial displacement of the having circular penetrations 627 and 629, which represent parameters in the design of the rings. in the rest means falling back on neighboring parallel surfaces -of ring and groove at the point where their clearances are measured, a simplification in production and control.

The ring consisting of two rails and its groove - after

7, 7a, 7b and 7c - work like the rings and %

Grooves according to FIGS. 4, 5 »6, due to the fact that they have the desired characteristics from primo to quarto. The knurling of the rails 733 and the grooves 734- - 735 or only the imperfections of the surfaces ensure the desired persistence of the effect of the pressures 718 act against the surface and at 721 against the underside. The combination of side pressure of the rails against their grooves with the clearance they have to approach from the expander defines an area for the pressures necessary to open the channels between adjacent surfaces with an increased tendency for small quantities, compared to the rings of the previous figures.

How the compression ring and its groove work 8 is analogous to that shown in FIGS. 2 and 3 and this embodiment has the same particular features Advantages as set out above for the oil control ring and its groove according to FIG. 6. Incidentally, is the special one It is to be expected that the advantage of the compression ring is that the marking of the groove is eliminated by the inner angle of the ring or is reduced. The compression ring 811 is in contact under the slight pressure against its groove, with the part 843-844 of the side of their groove that is parallel to the Own surface lies and, against the top dead center of the work cycle at the moment of ignition, the increased pressure deforms

209 88 1/00 7 7

the compression ring and presses it against the inclined part 844 - 846 of the underside of the groove, as previously explained:

.The inside angle of the side of the ring is so from the contact with this surface at the moment of increased stresses on the ring against its surface of the groove and the Marking of the groove by this angle occurs in Fort-P, but is at least weakened.

The various piston ring grooves shown in FIGS. 2, 4, 6 and 8, the mode of operation of which is explained below will have weak openings on adjacent faces of rings and grooves.

Since these openings only have to fulfill the task the access of the pressures between themselves and their neighboring ring tops with the smallest quantities or zero quantities. it is sufficient that they are very small. For example, you have satisfactory results with openings with an angle of 10 to 15 'obtained when applied "on Eolben grooves in automobiles to openings in the order of magnitude from 0.01 to 0.02 mm per area.

For the outside of the compression ring and the associated groove, it is important that this opening remains very small, so that the ring will move against this side of the groove under the action of the increased pressures to which it is subjected can support, by means of a fairly small deformation, so effectively not the foundation to modify its external contact with the cylinder.

For the remaining small openings, i. i.e., the neighboring ones Surfaces of the compression ring and groove and those of the two

209881/0077

The surfaces of the oil control ring and its groove apply same rigorous limit on the size of the Do not open because these rings are never subjected to the increased stresses that they would be able to deform to such an extent that they are in contact with the openings in these neighboring areas were made.

With regard to the adjacent upper sides of the compression ring and its groove, experience has shown that a very small opening from 10 to 15 'the task of access of the pressure, which is normal because of the increased pressures.

For the adjacent surfaces of the oil control rings are the Pressures which it is desired to have access between them are much lower; under certain speed conditions It can be useful, especially with very fast running engines, to have larger openings between them fall back so as not to access the low pressure through delaying or questioning an access circle that is too narrow. "

For this reason, the entry chamfers or roundings of the grooves or any other training are also included A favorable angle for the outflow of the pressure medium is preferably used in the grooves of the oil control rings, as these the access of the pressure medium, gas and oil, under low pressure facilitate.

Generally speaking, an advantage of the invention is that it provides opportunities for the pressure access circles between adjacent surfaces of rings and grooves to

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a deviation from the way the rings work Fast moving. Prevent motors.

FIGS. 1, 5, 6 and 7 show different embodiments the openings in the bottom of the groove according to the invention. 4He these openings work with the dynamic caused by that contained in the groove of the oil control ring Effect that is assisted by the movement of the piston on its descent to make it the central space of the piston and to prevent it from finding itself again in the upper part of the groove, where all the defects are the sealing of the surface and the upper lip of the oil control ring under the influence of dynamic pressure would collect as the usual openings make possible, for example the opening 4-09 shown in FIG. Such oil pressure, when it forms, can be detrimental Play a role in the oil consumption when the piston goes down.

For the same reason, on the one hand, there are the deflection walls 640 according to FIG. 6 and 740 according to FIG. 7, in order to transfer to the central space of the piston the sprayed from the crankshaft To guide oil to the openings 609 and 709 against this protection; on the other hand is the penetration of the oil outlet openings with the central cavity of the piston inclined, as the penetration 741 in Fig. 7 shows, so that when opening, wärtshub the lower edge of these openings does not run the risk of oil sprayed off by inertia, which is in the upper part of the Cavity of the piston is located to collect.

The orientations of these oil return openings and those below arranged baffle are generally favorable in terms of oil consumption if they are used in all pistons at all oil return openings penetrating the piston wall Find use when these openings open into the interior. The same applies to the location of the connection on the underside

209881/0077

these openings with the wall of the interior of the piston, which is further from the center of the piston than that Location of the connection between its upper side and the wall of the interior of the piston.

In this way the oil recirculation openings increase the bottom of the groove to the invention, the effectiveness of the good seal of the adjacent tops of oil ring and groove and contribute to the reinforcement of the feature tertio, as it is according to the invention in the oil control rings and their grooves · ■% application.

The functioning of the various variants or improvements shown according to Mg. 9 "to 28 is as follows

The grooves 9-4-7 and 104-8 of the bearing surfaces 917 and 1017 Pig. 9 "and 10 - each used to seal the lower part of the Compression ring 911 and the upper seal of the oil control ring it was carried out in 1012, increase the reliability of the seal desired for these bearing surfaces, by impressions such as those caused in the long run by the inner angle of the piston ring or its edge, if this is rounded is, are marked on the surface of the groove of the piston, ™ in the absence of this} these impressions "damage the seal, since the concentricities of the piston and cylinder during the Operation fluctuate within the limits of the piston clearance in the cylinder. The sealing of the compression rings 911 and of the oil control ring 1012, as required according to the invention are improved by the grooves 917 and 1017.

An analogous paragraph 114-9 of the top of the groove of the compression ring and another, 1250, the bottom of the groove of the

209881/0077

Oil control ring - shown in Figs. 11 and 12 can also be recessed pein. It must be pointed out, however that the improvement of the sealing of the compression ring during the intake stroke of the engine is not is always favorable, since, as was shown before, at the end of the suction stroke the one in the space between the rings 1218 The prevailing negative pressure, together with the friction and pressure of the oil against its underside, contributes to the fact that the oil control ring continues to be held against the top of the groove against the force of inertia trying to remove it. The groove 1250 can provide a means to create the contact circle between the undersides of the oil control ring and its hat at the desired point to realize the is away from the lower outer edge of the ring; with a U-shaped folded oil control ring made of sheet steel - ring 1212 this arrangement is quite suitable for making tight contacts near the center of the non-perforated part of this To ensure areas.

The various shown in Figs Seals contribute to the sealing effect of the compression ring, on the one hand by sealing the lower and / or upper adjacent surfaces of the ring and groove, on the other hand, help to press the ring against the cylinder; Their most important function, however, is to counteract the unexpected phenomenon of oil pumping, which according to the invention is tested Using individual compression rings has been found to remedy the greatly increased sealing on their underside showed.

By pumping oil, oil is forced up in the cylinder promoted; this became higher even with oil control rings

209881/0077

Effectiveness determined. After the most exacting examinations the explanation for this seems to be as follows: With each intake stroke the compression ring opens, which opposes the top of the groove is printed, along its bottom the game with which it is mounted in the groove and along the path opened in this way, that emerges from the 3? ilm stripped on the cylinder by the compression ring native oil in the bottom of the groove. With an effective oil control ring, the one in the bottom of the groove is for everyone Suction stroke guided amount of oil tiny, but it is pre- ^

act. As long as the neighboring undersides of the compression ring and its groove does not have a greatly increased sealing effect, this tiny amount of oil is removed from the floor the groove under the compression ring is sent back against the cylinder on each working stroke of the piston, namely due to the effect of the gas flow, which is the blow-by; that little to-and-fro movement of the oil runs unnoticed while the engine is running. Through the Piston ring training according to the invention, on the other hand, in which the seal is significantly increased, each device for At the bottom of the groove during the suction stroke, traces of oil that get into a trap there and cannot go back; how small even the trapped oil trace may be, with every work cycle " the repetition of this phenomenon yields a non-negligible amount. The oil first fills the bottom of the groove and is then up (relative to the piston) between the adjacent tops of the hing and groove pushed back. Forcibly pumping the oil towards the explosion chamber housing is obviously detrimental and not in accordance with the objects of the invention.

In order to eliminate this disadvantage, there are three according to the invention Funds provided:

The first and most important is closely related to the invention and is characterized by the features primo to quarto des

20988 1/0077

oil control ring defines that by having a very good Regulation of the piston on the cylinder during the downstroke Allowing left behind oil allows this pumping effect to dry up at the source; the optional second and third means are that the piston-piston ring assembly either together or separately as a part a seal is added between the bottom of the hat and the ring of which Figs. 22-26 Examples show, is arranged so as to counteract the passage of the pumped oil, on the other hand one for the outer wall A suitable profile is added to the compression ring in order to achieve the return through the well-known oil wedge effect along the walls of the cylinder of the oil coming from the bottom of the groove and over the compression ring is pumped.

The various profiles shown in Figures 13 and 14 accomplish this task. The symmetrically curved profile 1385 according to FIG. 13 ensures good return; the profile 1485 domed downward in contact enables a piston ring 1411, which is deformedly pressed against a slightly inclined underside 1417, to maintain an upward angle of return during the deformation of the ring. ■ ^v

The behavior of the various shown in FIGS. 13-15 Seals that lead to a reduction in or shutdown of the oil pumping will now be described.

The seals, with a cross section of several contact elements connected to the same body, for example as shown in Figs. 13, 14 and 15 have a stable behavior in the high and low speed ranges, probably due to the fact because of them

209881/0077

177595a

are all in permanent sealing contact against the inner surface of the compression ring, which is very close to the underside of the ring, whereby the path by which the oil is closed through the interface of the ring at the beginning, from the lower angle of the ring or very close from the beginning, this takes place at points 1387 in FIG. 13 and 1487 in FIG * To remain effective when the distance between the inner wall of the ring and the bottom of the groove increases under the influence of wear and tear, without becoming excessively large when the ring and cylinder are new.

The seal 1368 of FIG. 13 has those mentioned above Advantages as well as those known for this type of seal. It ensures a good seal against the passage of gas as against pumping oil.

The seal 1469 of FIG. 14 superimposes the advantages mentioned above, an increased effectiveness against the Pumping of oil, partly because of the constant contact |

its lower lip with the lower limit of the inner surface of the ring at 1487, on the other hand because of the contact through the lip that seals a flow is favorable for the pressure medium with a small amount and with a low pressure, d. i.e., under conditions for pumping oil, that must be prevented.

A ring with one or more sealing tips as shown in Fig. 15 operates like those previously mentioned. the Sealing tip 1576 opposite the bottom of the inner surface

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177595a

of the sealing ring effectively resists pumping of oil and shows a tendency to accompany the ring during wear.

The seal, which occupies almost the entire volume of the bottom of the groove between the (piston) ring and piston, is reduced. small dead spaces for the fuel gases and transmits it in a known manner to reduce the atmospheric pollution in, in which the tasks already described for the previous seals ensure be provided ψ.

Finally, all types of seal designs that have one or more circular sealing contacts between ensure the bottom of the groove and the inside of the compression ring, may the sealing contact now any Shape such as lobes, lips, possibly geometric ribs according to the invention ensure that the pumping of oil and the passage of gas under the compression ring can be reduced.

These seals made of resilient rubber, which are between the ring and. are squeezed to the bottom of the groove, whose * Functional description with regard to oil consumption incidentally bring striking new effects with them.

Not only do they press the ring against the wall of the cylinder by exerting a load on it that is nature's is specific to the seal and the type of compression to which the ring is subjected and which is evenly distributed. Depending on its size, this stress can lead to tension contribute to or replace the ring. It also allows a simpler one, if its value is sufficiently great

209881/0077

and use less brittle sealing ring, d. H., one made of materials other than currently used cast iron or alloy steels, for example Carbon steel, its use so far due to its loss of elasticity at high working temperatures was not possible; also, the piston ring can be similar to a diameter in terms of simple shapes that of the cylinder can be machined instead of making geometrically difficult machining that is necessary because of an equal distribution of tension in the input over its entire circumference, taking into account its Elasticity.

Also keep these provided at the bottom of the groove from yielding Existing rubber seals the head of the piston and contribute to its mechanical behavior. In particular, the knocking of the piston is avoided, which occurs in cold running in different engines or after one a certain degree of wear on pistons and cylinders can be observed.

Incidentally, if these seals are placed under sufficient tension, they will prevent the compression rings from rotating. This is a beneficial factor as the rings go through Grinding in deformations and wear of the cylinder should be adjusted. Compression rings rotatably mounted in this way have a reduction in wear during operation of their Surfaces and their piston grooves shown.

These seals take part in the reduction of the small dead spaces between the ring and the bottom of the groove and thus contribute to a reduction in the amount of unburned material, as is well known is a significant contributor to air pollution.

209 88 1/0077

How the in Pig. 27 oil control rings shown with a seal, which is embedded at all points in 2778, is in all respects the same function as the different types of oil control rings, be it that they have a fixed height or rails that resiliently against their adjacent surfaces of the Grooved and fitted with a sealing element between the adjacent tops of Hing and Hut; but one has found in the implementation of tests on Wk such seals that under increased tempera ture conditions and excessive lubrication that occurred in the course of operation, the seal lost its stiffness and under the thrust of the blow-by pressure the tendency showed to bulge into the bottom of the groove.

The small installation provided in the surface of the groove 2778 resists the sliding of the seal, thus avoiding the noted disadvantage.

The mode of operation of the groove shown in Fig. 28 is as follows:

If it is the groove of oil ring associated as W reaches its acute angle to the oil film during the downward movement of the piston, and stores the oil} during the upward passage of the piston it is this oil to the cylinder due to the wedge effect of the oil, the lip 2880 generated, back. It can also interact with the oil control ring in order to delay the moment when the oil inlet is opened. It should be noted that the peak of the gas leakage loss, which the oil control ring has to evacuate, is in the vicinity of the top dead center and that, in contrast to this, the maximum amount of the stripped oil to be withdrawn is much further down

209881/0077

is located more towards the middle or the lower area of the piston path, this can be done with the floating Oil control ring combined groove oil for the moment store the highest amount of gas - first third of the stroke and the oil control ring only after this moment make them swim. In other words, the presence of this groove may in part do that for. the amount of oil and gas necessary play that the oil control ring must evacuate to the housing during the work cycle, 'weaken, on the other hand return the stored oil to the cylinder when it is returned to the part that has been dried by the stripping of the cylinder is raised.

The explanation of the functionality and experiments on arrangements consisting of a piston and a compression ring and an oil control ring according to the invention show that these arrangements each of their two Binge assign precisely predetermined roles by certain positive means in each moment of a four-stroke cycle, which are completely reproducible; this is a logical consequence of the coercive nature of the means used.

The following is a list of the resulting advantages.

Is the sealing of a piston in its cylinder for example on a vehicle equipped with an explosion engine with 1,100 ecm, the following comparative values result:

209881/007 7

Usual piston-invention differences (piston) ring-like piston arrangements ben- (piston)

ring arrangement

gene

When the engine is warm on the compression pressure recorder read pressures for a yolumetric Ratio of 8.5 to 1 in kg / cm ^

11.5

20th

Blow-by value in slow speed in l / min

0.70

- 82

Blowvby value, max.speed at full load, in liters / min.

18/20

- 79

This greatly increases the sealing of the piston in his Cylinder ensures, on the one hand, an improvement in the thermal efficiency of the working cycle by reducing it or elimination of the combustion gas losses that pass from the explosion chamber into the crankcase, on the other hand for a reduction in air pollution in the city running motor vehicles, by improving the combustion at very low loads; especially in slow speed the combustion is much more regular. In these speed ranges you often find misfires, because the pressures reached at the moment of ignition are only low and due to the sealing tolerances on values which can no longer reach the flash point, fall. The high sealing of the compression ring, however, regulates the Pressurize and thus reduce the proportion of unburned components in the exhaust gases.

209881/0077

In addition, recent studies have shown the harmful Effect of recirculation of the gases from the crankcase on the behavior of the carburetor controls and the quality of lubricating oils shown.

Reducing the amount of recirculated gases further reduces these disadvantages. With increasing experience in the application of the measures according to the invention, further port steps will be achieved which drive this reduction even further. This is a completely new way *

to protect the mechanical parts and the "lubricating oils of Combustion engines against the harmful effects of the passage of gases.

This increase in the pressure obtained leads to the same Filling level, moreover, to further increase the favorable ignition conditions and, for this reason, considerably To facilitate cold starts of engines.

It can also be pointed out that the reduction the gas passage between piston and cylinder protects the rings against contamination in an extremely effective way.

In addition, according to the invention, a new lubrication cycle is created for the piston, in particular at the top of the cylinder. Namely there due in part to the fact that the oil which escapes scraping and remains on the top walls in the cylinder runs around the compression ring and then to the crankcase during the downward movement under the action of the oil control ring and its wide open play in the groove is returned, more oil can be used for the oil control than with conventional systems that are bad or not to recycle at all without having to do so

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1775958

more would be consumed. In addition, the oil that the Cylinder lubricated up, not an insulated one exposed to the degradation of a non-renewed and burned oil oil more, rather it renews itself and retains a quality equal to that of the oil in the crankcase. This new lubrication cycle at the top of the cylinder also has the advantage on that, while maintaining an excellent mechanical condition of the elements in question, viz Cylinders, pistons and (piston) rings show excellent economy in oil consumption.

The elimination of a ring as well as the manufacture of the mechanical Support surface over the entire height of the piston make it possible to reduce the total height of the piston. On the one hand, his head can adjust the height of the ring and the cylindrical (oil) ring that have been omitted. For example, do this for automotive engines Reduction in height by about 5 to 10 mm. On the other hand, it allows the rubbing part of the shaft to be moved upwards to: to the head of the cylinder besides the already mentioned better mechanical behavior of the piston in the cylinder same friction surface between cylinder and piston also "by shortening, starting from below, the height of the piston skirt To shorten. ■ -. ,

Each of these reductions in the height of the piston, made in total or separately, allows one more economical use of the coming height, not only of the piston, but also of the engine. With the same cylinder content, a transverse disk in the motor can be placed in the Saving of the order of 5 to 15 mm in motor vehicles will. From this again follows a lighter weight of the moving organs moving to and fro, what for that

209881/0077

Performance is favorable, a weight saving of the Motors and an improved storage option as well as a considerable cost saving.

The overpressure of a ring, the reduction of the tension on the oil control ring, as explained in the description contribute to reducing the friction between the ring formations and the cylinder; the results ^ thus lead to an improvement in performance and to a "™ Reduction in wear.

The piston (piston) ring arrangements also have the advantage that they are well suited, because of the most varied of control devices, to implement each of the parameters that allow adaptation to the special requirements of each engine. Rings and grooves of the type shown in FIG. 8 for the compression ring and its groove or, according to FIG G

Surfaces of the grooves to the effect desired for the pressures between each adjacent surface of the ring and groove modify. Modifying the openings between adjacent surfaces and, if necessary, the addition of bevels or roundings at the entry into the groove, which can be more or less strong, modify the speed with which the desired effect the pressures on the surfaces and the respective play of the Ülabstreifringes in the groove, the pressure levels around them Modified surfaces around.

The various parameters that determine the behavior of the Pistons and piston ring assemblies, for these in particular

209 88 1/007 7

control the pressures between two elements, the hydraulic one Pressure under the oil control ring and the pressure of the oil control ring The various characteristics of each engine, especially its stroke, can be applied to the cylinder. its degree of filling, its speed range and its Charge ratio to be adjusted. Finally, in the case of the oil control ring, it has an effect on the play of the ring in its groove, on the surface of the sections of each of its faces exposed to the action of pressure is and on the recesses and sections where the ^ pressure medium has access to the surfaces of the ring, the Set the lowest tension of the ring, which can be above that of the pressure medium, gas or oil that is in the be able to set different moments of the work cycle on one or the other of these surfaces; This method leads to the tension of the oil control rings on a Minimum and thus the wear of rings and cylinders and power losses due to friction to reduce.

In summary it can be said that through this invention there is a potential for completely new possibilities for Today's internal combustion engines can be created by * on the one hand their weight, their space requirements, their costs, the mechanical wear and tear as well as their share of air pollution can be reduced, on the other hand their performance behavior, as well as their running conditions and their operational stability can be improved.

The invention was particularly applied to piston (piston) ring assemblies described with only two rings, a compression ring and an oil control ring. The invention can be of course also apply to piston (piston) rings that

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1775958

have a larger number of rings, in particular Piston * (piston) on the inlet flange with at least one assignment of piston * (piston) ring groove according to the invention and at least one zurodming a common groove one Piston ring »

209881/0077

Claims (32)

-50- 17759S6 Patent Claims 1. Piston and (piston) ring assembly for Internal combustion enginesj characterized by a means of increased sealing between the di§ Main work-taking area of each binge and the neighboring area of its hat, on at least one fc near the inner limit of the pool of the ring provided circle j and by a smock for access to the pressure prevailing above the ring against at least a substantial portion of the surface area between the adjacent tops of each ring and its groove, so that the entire assembly already with two rings alone, a compression ring and a oil control ring, the dual task of sealing the combustion chamber between the piston and cylinder and the To prevent most of the oil thrown onto the cylinder walls from entering the combustion chamber, is met. ψ 2. Arrangement according to claim 1, characterized in that the sealing means from the. There is grinding in at least one pair of adjacent surfaces of the ring and groove. 3. Arrangement according to claim 1, characterized in that the sealing means from a high-precision machining at least one pair of adjacent faces of the ring and groove. 209881/0077 4-. Arrangement according to claim 1, characterized in that a groove bottom seal (1368, 1469, 1575) of the compression ring is installed between the inner surface of the ring and the bottom of the groove, this seal having a known geometric shape, in particular round, square in cross section , rectangular, provided with flaps or lips or • can have any combination of these shape and that a seal, in particular of rectangular cross section, apart from the expansion fills the entire space zwisc-hen * compression ring and the associated groove bottom. 5 · Arrangement according to claim 4, characterized in that the sealing material is a resilient and elastic product is composed of one resistant to hydrocarbons, their products of combustion, temperature and aging Special sealing material. i 6. Arrangement according to claim 5, characterized in that g e k e η η - ζ indicates that the sealing material is a known fluorinated elastomer, namely a linear Copolymer of vinylidene fluoride and hexafluoropropylene | 7. Arrangement according to claim 5 »characterized by g e k e η η, that the seals are adapted to the material, such that the seal against a constructive compression between the inside of the ring and the bottom of the groove a least Reaction force is given such that the seal withstands prolonged use as well as the signs of wear and tear on the cylinder and ring. 2 0 9 8 8 1/0077 8. Arrangement according to claim 1, characterized in that that for the access of the pressure Means providing against the "adjacent upper sides of the ring" are formed by opening these upper sides seen from the ring and groove from the piston to the outside. 9 · Arrangement according to claim 1, characterized in that the access of the pressure between the adjacent surfaces of the ring and ^ anger-securing means is formed by approximately parallel ™ constructive formation of these surfaces of ring and groove} but the construction is not tight (313J314) (516j 517). 10. Arrangement according to claim 1, characterized in that the lower adjacent surfaces of compression ring and groove a device for the access of the pressure prevailing under these surfaces against a significant part of their surface. 11. Arrangement according to claim 1 and 10, characterized in that g e k e η η fc shows that the pressure access means is formed by an opening (d, j) in the adjacent undersides of compression ring and groove, this opening necessarily being very small, such that the support of these two undersides of "ring and groove under the action of the increased pressures within the elastic limits of the ring and without any noticeable change in the basis of their circumferential contact with the cylinder. 209881/0077 12. The arrangement according to claim 1, characterized e i c h η e t that the return of oil to the crankcase via means in addition to the space between adjacent undersides of the oil control ring and groove. 13, arrangement according to claim 1, characterized in that the entire underside of the groove of the oil control ring has a discontinuous circular area. 14. Arrangement according to claim 1, characterized in that the entire underside of the groove of the oil control ring has a continuous circular area. 15. Arrangement according to claim 1 and 14, characterized in that the access of the below adjacent undersides of the oil control ring prevailing over a considerable part of the pressure between them adjacent surfaces is ensured. 16. Arrangement according to one of claims 1, 14 and 15, characterized G ek e η η ζ e i chn e t that the pressure access means between adjacent undersides of the oil control ring and groove through an opening (d, f, h) of these undersides is formed outwardly from the ring and groove seen from the piston. 20988 1/00 7 7 17. Arrangement according to claim 1, 14 and 15, characterized in that ■ _t « I know that the means of access to the Druok between the neighboring undersides of the oil control ring and the hat by a roughly parallel but not tight one Construction of these surfaces (519 »520) is formed, 18. Arrangement according to claim 1, characterized in that g e k e η η ', that on the one hand the sealing contact between adjacent surfaces of rings and grooves P a circular ring near the inner limit of the Surface of the ring is effected and on the other hand, the pressure prevailing outside the ring only on a significant portion of the surface area between adjacent surfaces that is outside the Contact ring is, takes place. 19. Arrangement according to one of claims 1, 8 and 18, characterized g ekennz e i c hn e t that between adjacent Upper sides of the compression ring and groove on the one hand a continuous seal over a circular ring of the surface of the ring and a circular ring of the area of the groove (841 - ^ 842), which are parallel to each other, butting against each other and are provided in the vicinity of the inner edge of the face of the ring, and on the other hand the access of the pressure prevailing above these adjacent surfaces via an opening (i) of these neighboring surfaces seen from the piston outwards, starting from the outer edge of their said circular rings is ensured. 209881/0077 20. Arrangement according to one of claims 1 to 3, 8, 10, 11 and 18, characterized geke η η ζ eich η et that between at least one pair of adjacent the main work of the ring taking over ring surfaces and surfaces of the ring on the one hand the increased sealing by a Circular ring of the ring surface and a circular ring of the groove surface (843-844) "(626-627) are ensured, which are arranged parallel to one another, adjacent to one another and in the vicinity of the inner edge of the surface of the ring and that on the other hand the access of the. M Pressure prevailing on the outside of the annular surface, which provides the main work, is ensured through an opening (j, e) of these adjacent surfaces, seen from the piston, to the outside, starting from the outer edge of the circular rings. 21. Arrangement according to one of claims 1, 12, 13, 16 and 18, characterized in that between adjacent undersides of the oil control ring and groove on the one hand a continuous seal by a circular ring the ring surface and a circular ring of the groove surface (628 - 629) is ensured, which are parallel to each other, abutting and near the inner edge | the annular surface are arranged and that on the other hand the access of the pressure prevailing below these adjacent surfaces through an opening (f) of these neighboring surfaces seen from the piston to the outside, starting from the outer edge of these circular rings ensured is. 22. Arrangement according to claim 1, characterized in that the connecting angle of the surfaces of the groove and oil control ring with the outer wall of the piston 209881/0077 to improve the outflow of the pressure medium and thus the access of the pressure between adjacent ones The surfaces of the groove and ring are grooved or offset. 23 · Arrangement according to claim 22, characterized in that the angular recess by a Chamfer (438, 439, 638, 639) is formed. 24. Arrangement according to claim 22, characterized in that the angular recess means curved lines (538, 539) to bring about the favorable outflow of the pressure medium is profiled. 25 · Arrangement according to claim 1, characterized in that the part of the between the inner contact circle of the neighboring faces of ring and . Groove and the floor arranged surface part on his Has a small circular groove (947, 1048, 1149-, 1250) for loosening. 26. Arrangement according to claim 1, characterized in that the upper walls of the oil return Guide openings (609 »709) to the central space of the piston have an inclination with respect to the outer wall of the head of the piston of at least 90 °. 27. The arrangement according to claim 1 and 26, characterized in that the oil return openings that the Connect the bottom of the groove of the oil control ring with the central cavity of the piston, at the bottom of the Groove open at the same height as (26) or above the surface of the groove. 209881/0077 28. Arrangement according to claim 1, characterized in that g e k e η η, that the oil return openings in the central cavity of the piston in this cavity above a wall (640, 740) of this cavity, which is inclined and towards the uppermost point of the central Space of the piston is oriented, open. 29. The arrangement according to claim 1, characterized in that the oil return openings in the central cavity of the piston a connection (628) of the lower wall of these openings with the inner wall of the central cavity of the piston, which is at a distance from the piston axis, which is greater than that of the connection (686) of the upper wall of these openings with the inner wall of the central Piston cavity. 30. Arrangement according to claim 1, characterized in that the outer surfaces of the compression ring be formed by any rotating body and have a return effect for the oil, which has reached above the compression ring and, for example, in the form of a symmetrical one Curvature (1385) or a curvature that has downward contact (1485) are formed. 31. Arrangement according to one of claims 1 or 30, characterized in that the compression ring carries a rounding (1585) which connects its top with the lateral outer surface of the wall. 20988 1/007 7 32. Arrangement according to claim 1, characterized in that the piston has a head, its height by the height of the (colons) rings and theirs oil rings is reduced. 33 · Arrangement according to claim 1 or 32, characterized in that the piston skirt is shortened downwards by the size of the mechanical support surface that is extended upwards. 209881/0077 Read e ί te