DE2108861A1 - Pistons for internal combustion engines - Google Patents

Description

PATENT ADVOCATE!

DR.CLAUS RE ^ LANDS

WPL-INC. KLAUS BtRNHAROT

D-8 MONCHSN 60

IXCKiRSTRASSiI

223/1

Associated Engineering Italy S.p.A. 1-10091 ALPIGUANO (Turin, Italy)

Pistons for internal combustion engines Priority March 5, 1970 Italy 67735-A / 70

In internal combustion engines with reciprocating pistons is each piston, which transmits the movement generated by the compressive force of the gas to the crankshaft, old the corresponding one Connecting rod connected by means of a cylindrical bolt. The eye of the connecting rod sits on the piston pin in the middle section of its cylinder-shaped casing, while the two Ends of the piston pin in matching bores, the piston pin bosses, are mounted and diametrically in the wall of the piston offset position are recessed.

This known type of aeöhanlaöhen connection between the piston and the connecting rod, determines 41s the dimensions of the points of the Zülbmt * where the Kolbaabolsen is mounted, namely in £ 92113 aal Dltelmndsr aujais umhUngenda KaÖTeraältnleae between!

flae iCoibanbolüana, directly through the wetness of the btefciwBfc bsv, through the InntndttrchicesBtr des

109838/1555

Cylinder in which the piston runs back and forth; Diameter of the piston pin that is large enough and in any case, be adapted to his® length asus »um to absorb the specific surface pressures well, to which it is constantly subjected, so that its deflection is reduced to a minimum; Diameter of the piston pin eyes or the ait of the Wall of the bolt connected housing, best loaded by the Eolbenbolzendurehmesser, which is also the oechanleche Required strength, which is required of the piston bolt eyes will, and aoaiit also their size and weight; and

clear width between the inner edges of the piston pin bosses, which parameter within a beatiawten The size range is to be selected and soatlt the above mentioned Dimensional proportions sitssdingt.

If old now

X s length of the piston pin,
ds the diameter of the piston bolt,

s clear width between the opposing Xnneijlmnten of the golhenbolzeaaugsii, in which the Solbenbolz is stored iac, which are recessed directly in the wall of the piston in diametrically opposite position, and with
D »ZyliaäarJtajTGhaassör, in dea the piston runs, warden, & £ g®b®n see swisufeen these filing precise hiltnlss®, which are taken into account in the design and manufacture of piston pins for Terbrenmasgsaiotoreii with reciprocating pistons»

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aaü äeanaöto, au @ h äia il * 3i? 5susgaa der Pl ^ ualetaage mieät γIageγa mayο

109838/1555

The necessary consideration of the dimensional proportions brings certain dimensions with sieves, which are connected to some components, which depend on the impossibility of reducing the values of the changing inertial mass "below a certain limit *" rich coffers, of course, from the weight of the piston, the piston pin and the connecting rod are dependent. Serartige disadvantages at high Brehzahlen (the GröBenordung of 10,000 u / min or less) are particularly sensitive, safeblower achievable by conventional motors with Bolssen services d one.

In order to avoid the above mentioned Haehteile, flasks were manufactured in which the internal structure provides that the pistons » bolt eyes. extend from the bottom of the piston head inwards and form a whole with the piston head, whereby a Shortening the piston pin length and the clear width (1) between the opposing inner edges of the piston pin bosses is made possible, line such a design 1st has practically been abandoned because there is no precise policy » Lines were drawn up to determine the correct Mafi ratio between the individual files on the piston.

The object of the invention is to improve pistons for internal combustion engines and, in particular, pistons with a diameter of less than 130 mm for engines with a speed of less than 10,000 rpm. The piston according to the invention for internal combustion engines, the piston pin bosses of which are not recessed in the wall of the piston, but are carried by parallel axial extensions directly connected to the piston head, is characterized by mafi ratios, which are defined between the files that determine the design of the piston, and · what determine the matching dimensions and determine the need to have the individual partial · _t in order to achieve a correct design and manufacture of the pistons.

1098 38 / 15SS

The invention takes into account the rules for a design of the pistons in a conventional way not, because earlier © versions according to the guidelines did not produce satisfactory results

Di® proportions for the flowering of the individual, the Piston forming ropes result from the solution of the task, the detrimental effect of the alternating movements of the haters involved in an internal combustion engine minimizes to press. The solution to this problem was sought in two ways, namely analytically and experimentally. From the achieved. The results were as given in the claims and in the description below, with reference to the drawing showing an example will. Show in the drawing

1 shows a piston according to the invention in a vertical, diametral® view Section in a plane perpendicular to the axis of the piston pin bosses,

Flg. 2 the same piston from the side at 90 ° opposite Pig. 1

rotated with a rope cut in a vertical plane passing through the bolt axis, and

Fig. 3 shows a cross section through the same piston in a through the section line IV-I? according to Fig. 2 going horizontal plane.

According to the invention, the piston pin 5 is shown in FIG Dashed lines drawn in the two piston pins 6 mounted, which form a rope of the two * corresponding extensions derived directly from the piston head 8 · each direct Connection between the bearing parts 6, 7 of the piston pin 5 and the piston skirt 9 is therefore excluded · In this arrangement, the piston pin 5 is directly connected to the piston head.

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As shown in Pig * 2 and 5, there are 9 in the skirt of the piston two lockers 10 are provided, the diameter of which is slightly larger than the diameter of the piston 5 is "around the installation of the piston" Bolt from the outside, through the eyes 6 and the interposed connecting rod (not shown) guided will.

The fixing of the piston pin 5 in place can be on some kind can be achieved, e.g. by the fact that the connecting rods » rod on the dumbbell of the piston pin with a tight fit ~ is pulled so that the ends of the piston pin are in the gudgeon pin eyes can rotate freely, but any Eäagsver ~> pushes through the connecting rod are prevented, or the connecting rod is free with the jacket of the piston pin 5 rotatably connected and the piston pin is held by snap rings held in the outer grooves of the two piston pin bosses.

Among these goal exposures, referring to FIG Pig. 3s in the

13 - diameter of the piston ring 9 »
ds diameter of the piston pin 5 »

I) s distance between the outer edges of the piston pin bosses 6 and 1 ~ Distance between the inner edges of the same piston pin

Eyes 6 are that, unlike conventional pistons, it is possible to use a piston pin 5 whose length ⁿ L ″ is significantly smaller than the piston diameter.

It also results from the fact that the deflection of the piston pin is significantly smaller than the deflection of a piston pin in a conventional piston with the same load due to inertia forces and the gas pressure on the piston head 3, so that the "1 ^R is higher haban must »The reduction

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1098 38 / 1SS

• C * ■ * ■ 1 I · d

results

There is ferae "di @ H $ §l £ © li2e" it _f the flight before this' esMittes s © sm iim @ iis £ © siieren * the opiinal value thereby. © r & £ @ lt wirde i & ll SE & s äes & ¥ @ s? Td @ s iimereai Abstasdes ^R l ^w changes, der- ie obigsm B ^^ imkt for de »flMshsainfealt des Aiiilagequer» sehaitt @ s @ Ia © loll® epl®lt _s wobal ile? @ i * g7ÖSerung Seeflächenlafealtes fi @ s Esllsssibolsse ^ -Aiiflii ^ equeifscfe.iiittea the possibility gives «, the width i®r Pleiielstaage. 2 ^ Tersiiigeni _{t of} course within leg ¹ fe © ast © _e "ii® ensure ale festi ^ ceii * S © r connecting rods.

From these considerations one can s®hX ± eBen _s that by reducing the & © sa®tliBg® "L · ^{15 of} the same & bolt the Burcbia eater ^ d" of the same sas also the corresponding Solbanbolsen'-eyes 6 can be seated smaller «Whereby the danger of an out-of-roundness of the Solbsabolzeas 5 is also reduced and the hydrodynamic maintenance of the same« rain for yorimndsnseins τοπ sshosiersittelß during the operation of the engine is improved.

As a guest effect of the above genaiuit theoretical and Experiaantellea Betracfetiisg there is the possibility of all © Maß® er den. Piston parts carrying piston pins smaller ¥ orsusehsiij whereby a® aserklicha 3 © weight reduction of the Connecting rod and piston pin is achieved, which G-a- «Is it negative for the degree of engine operation? affects da as the alternating inertial forces of the entire crank mechanism proportionally increases.

The difficulty was in U aj? Sraiitfelung uni definition more precisely _; for you aimsaliisii from »

dlesta Solbeas aaS © ^ f®yölmiieh2äf'Βμ

ti -. · '' J -Y a

Ratio values that are intended to be used to determine the values of the corresponding parameters for the dimensioning of all parts to determine that are to be taken into account in the design of such a piston and on the entire dynamic Process of operation of one equipped with these pistons Combustion engine are involved.

The ratio values given above and in the claims, which characterize the invention and the correct dimensioning of the sizes B, L, d and 1 for the construction of a Enable pistons can be used together and / or separately.

10 98 38/1555

Claims (2)

2108881 223/1 Claims 1 ./Piston for internal combustion engines, in which the piston pin bosses, in which the gudgeons of the piston pin are mounted, extend symmetrically from the bottom of the piston head, parallel to one another
and _r are substantially extending also to Itängsachse dea piston extensions saved AXW _r characterized in that the parts de :? ilo3l-eüf. · and the piston piston are dimensioned according to the following ratios Ratio between nominal diameter of piston (D) and piston = bolsendurcüineßser Cd) j 4,3 ^ D / d 6 5, Ratio swiss-.ben lienndurchmesiier de «Kolbens (D) and greatest length of the entire piston pin bearing (L) ι 1.45 <ί D / L £ 1.9 and Nenndurchiaesser relationship between the piston fD) and Ab · = jatand between the inner Kauten (l) of the piston pin bosses (6} ϊ £ 3.5 D / l έ = 6 2. Jfnlben i «ai Li Aiißp? uch 1, thereby ßelcennEeichiiet, dai ^! bti inside ηχή- ^: -τρρΐ> _ acntea folbenbolnsa aod Eo3benbolzenaug6ii _f wob * »J- ■;. ■ - ■" which on d? n Fo3 iJimbc-Jsen during the Hotorbetriebes vd ^ Jc & ViFfiV-.j Beanspruciiunßi-r run Eolbenkopf on / _v enon? ir «'.:". are '. · da' ratio F / # / i £ icho.n S "3l>ondurctaaess" i ^ i: 3) aint Kolbenbolseiidurch- ^diameter: ύ) - ^ b'svs tj-i 4 * 3, 5 "Eolb" i - j '4ü3pru? ht or 2 ₁ characterized in that the ratio -, iiifi ^ & iecben piston throughaisiooej '(D) and the CL) eats greater than 1.45 ", 4 Pistons iiaaii one of the preliminary tests iUisprücb.e ₍ aaduxcli denotes that the ratio Stflaclien 2ylinderdurnii '"r _? Fser (D) and loved' width between äan both piston bolsünai ^" ui (greater than 3f5 iptr 1 0 9 i-1 ';