Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J1/00—Pistons; Trunk pistons; Plungers
  • F16J1/10—Connection to driving members
  • F16J1/14—Connection to driving members with connecting-rods, i.e. pivotal connections
  • F16J1/16—Connection to driving members with connecting-rods, i.e. pivotal connections with gudgeon-pin; Gudgeon-pins

Definitions

• the invention relates to a piston pin bearing for an internal combustion engine with hub bores in which a piston pin is mounted.
• DE 21 52 462 B2 proposes a hub shape in which the surface line of the hub bore is bent, the axis of the hub bore has a slightly curved course towards the center of the piston and the cross section of the bore is oval, the small one Semi-axis of the oval runs parallel to the longitudinal axis of the piston.
• DE 16 50 206 A1 proposes an oval hub bore in which the large axis of the oval comes to lie transversely to the longitudinal axis of the piston. This is to increase seizure safety and low noise between the piston pin and the hub bore.
• the object of the invention is to provide an improved hub bore shape for a piston pin bearing compared to the prior art, which allows a significant reduction in mechanical stresses in the piston and thus also an extension of the piston life.
• the design is intended to avoid noise formation in the piston pin bearing.
• the one-sided circular cylindrical shape which is only in the equator-nadir-equator-hub area and in which the surface line of the cylinder lying in the nadir of the hub bore runs parallel to the hub bore axis, advantageously achieves that the play between the piston pin and the hub when the piston pin changes over from the top of the hub to the bottom of the hub is minimized.
• the inventive shaping of the hub bore achieves a significant increase in the service life of the piston compared to the known prior art.
• FIG. 1 shows a partial longitudinal section through a piston.
• FIG. 2 shows a cross section of the hub bore, cut along the line yy.
• Figure 3 is a piston in perspective view showing various highly stressed points A-E.
• FIG. 4 shows a graphical representation of the influence of different hub bore designs on the service life according to the locations according to FIG. 3;
• 5.1 shows a representation of the radial stresses in the hub bore as a development of a cylindrical hub shape between the equator -Zenit-equator with a circular-cylindrical hub shape between the equator -Nadir-Equator;
• a piston 1 for an internal combustion engine has a hub bore 2 with an upper hub region 2.1 and a lower hub region 2.2, in which a circular cylindrical piston pin (not shown) is mounted.
• the upper hub area is arranged on the gas force side, in which the circumferential surface of the hub bore 2, designated 5, has a high oval shape along the entire longitudinal axis X of the hub in the area of the hub equator - hub zenite - hub equator and the parameter representation of the oval
• the lateral surface 5 is formed in the shape of a circular cylinder along the entire longitudinal axis X of the hub between the hub equator-hub adir - hub equator, the following applying to both hub areas:
• the outer lines 3 and 4 in the zenith and nadir are parallel to the longitudinal axis of the hub, which is perpendicular to the longitudinal axis of the piston.
• the ovality is expediently 0.05 to 0.2% of the hub bore diameter D.
• FIGS. 3 and 4 a drastic increase in the service life can be ascertained by the hub design according to the invention, which results from a 1000 hour piston stress test for a light metal diesel piston with an ignition pressure of 190 bar.
• the piston with shaft 6, connecting rod 7 and piston pin 8 and the measuring points A - E are explicitly shown.
• Figures 5.1 and 5.2 show in developments of the upper hub area 2.1 the surface pressure distributions in cylindrical and highly oval design as well as according to Fig. 5.3 the difference in surface pressure distribution from Figs. 5.1 and 5.2 using a light metal diesel piston at an ignition pressure of 175 bar.
• the radial stresses in the outer areas of the Hub bore higher, so that - due to the enlarged lever arm in relation to the pin axis - there is a greater moment, which reduces the bending of the piston around the pin axis. This results in lower tangential stresses at the edge of the bowl, for example, but other areas in the combustion bowl are also less stressed.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• Pistons, Piston Rings, And Cylinders (AREA)

Applications Claiming Priority (3)

Publications (1)

Family

ID=29413998

Family Applications (1)

Country Status (9)

Families Citing this family (13)

Family Cites Families (15)

• 2002
  • 2002-05-22 DE DE10222463A patent/DE10222463A1/de not_active Withdrawn
• 2003
  • 2003-05-20 EP EP03727239A patent/EP1509712A1/de not_active Withdrawn
  • 2003-05-20 JP JP2004505570A patent/JP4488511B2/ja not_active Expired - Lifetime
  • 2003-05-20 CN CNB038115875A patent/CN100346093C/zh not_active Expired - Lifetime
  • 2003-05-20 WO PCT/DE2003/001616 patent/WO2003098078A1/de active Application Filing
  • 2003-05-20 US US10/515,098 patent/US7107893B2/en not_active Expired - Lifetime
  • 2003-05-20 BR BRPI0311220-9A patent/BR0311220B1/pt active IP Right Grant
  • 2003-05-20 KR KR1020047018740A patent/KR100976642B1/ko active IP Right Grant
• 2005
  • 2005-10-14 HK HK05109099A patent/HK1077352A1/xx not_active IP Right Cessation

Non-Patent Citations (1)

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