Abstract
The three-dimensional EHD lubrication and wear loss of piston ring-cylinder liner components for five rings in the firing diesel engine was studied by using VC++ programs. The gas blowby, variable density and viscosity of lubricant, the surface roughness, friction heat flux and the normal elastic deformation are all considered in the EHD lubrication analysis algorithm. Meanwhile, the wear loss of the cylinder liner was also calculated when the diesel was started under cold starting condition in which the wearing was more serious than that in warm starting condition. The simulated results were compared with the wear measurement of the cylinder liner, and they matched well. It was found that the hydrodynamic friction force was larger than the asperity friction force, and the wear distribution of the barrel piston ring was very different from that of the rectangular piston ring. The distribution trend of the nominal oil film thickness was similar to the normal elastic deformation, but opposite to the wear loss of the piston rings. The wear loss caused by the first piston ring was the biggest and played a dominant role in the wear loss of cylinder liner. The greatest wear loss of the cylinder liner occurs at the time near top dead centre.
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Abbreviations
- a c :
-
piston acceleration, m/s2
- A :
-
apparent area of contact, m2
- A 1~A 5 :
-
blowby area of five ring gaps, m2
- A c :
-
real area of contact, m2
- b :
-
effective axial height of the piston ring, m
- C A , C B , D t :
-
empirical parameter of density-pressure
- E′:
-
comprehensive elastic modulus, Pa
- E 1 :
-
elastic modulus of piston ring, Pa
- E 2 :
-
elastic modulus of cylinder liner, Pa
- F 1 :
-
gas force acting on the leading edge of the piston ring, N
- F 2 :
-
gas force acting on the trailing edge of the piston ring, N
- F e :
-
elastic force of the piston ring, N
- F r :
-
radial friction force acting on the piston ring, N
- F t :
-
axial viscosity friction force acting on the piston ring, N
- F x :
-
axial hydrodynamic force acting on the piston ring, N
- F A :
-
friction force caused by shearing of asperities, N
- F G :
-
total gas force acting on the back of the piston ring, N
- F Z :
-
normal hydrodynamic force acting on the piston ring radially, N
- g :
-
gravity constant = 9.81, m/s2
- h :
-
nominal oil film thickness, m
- h 0 :
-
minimum oil film thickness, m
- h x :
-
axial variation of oil film thickness, m
- h y :
-
circumferential variation of oil film thickness, m
- h T :
-
actual oil film thickness, m
- H :
-
film thickness ratio, H = h/σ
- k :
-
gas specific heat
- K c :
-
gas flow coefficient
- L :
-
circumferential length of the piston ring, m
- Mg :
-
gravity of piston ring, N
- p :
-
oil film pressure, Pa
- \(\bar p\) :
-
average oil film pressure, Pa
- p 0 :
-
gas pressure in the crankcase, Pa
- p 1~p 4 :
-
inter-ring gas pressure, Pa
- p i :
-
cylinder pressure, Pa
- p R :
-
Reolands’ reference pressure, Pa
- p 1(t):
-
gas pressure acting on the leading edge of the piston ring, Pa
- p 2(t):
-
gas pressure acting on the trailing edge of the piston ring, Pa
- R g :
-
gas constant = 8.314, J/mol K
- R x :
-
groove’s axial reaction force acting on the piston ring, N
- S 0 :
-
Roelands’ viscosity-temperature coefficient
- t :
-
time, s
- T :
-
oil film temperature, °C
- T 0 :
-
ambient temperature, °C
- T 1~T 4 :
-
gas temperature of the four air chambers, °C
- T R :
-
Reolands’ reference temperature, °C
- U :
-
the relative velocity between the piston ring and cylinder liner, m/s
- v(x, y):
-
normal elastic deformation, m
- V 1~V 4 :
-
volume of the four air chambers, m3
- V r1 :
-
a scale factor, V r1=(σ 1/σ)2
- W i~W 4 :
-
blowby among five piston ring gap, kg/s
- W A :
-
asperity contact load, N
- x :
-
axial coordinate, m
- x c :
-
rupture location of oil film, m
- x i :
-
inlet location of lubricant, m
- x o :
-
outlet location of lubricant, m
- y :
-
circumferential coordinate, m
- z :
-
Roelands’ viscosity-pressure coefficient
- α 0 :
-
boundary friction coefficient
- β :
-
radius of curvature at peak of asperity, m
- δ 1 :
-
random roughness amplitudes of piston ring, m
- δ 2 :
-
random roughness amplitudes of cylinder liner, m
- κ :
-
wear constant of the lubricant
- μ :
-
lubricant viscosity, Pa.s
- μ 0 :
-
lubricant viscosity at atmosphere pressure and ambient temperature, Pa.s
- μ R :
-
Roelands’ reference viscosity, Pa.s
- ν 1 :
-
Poisson’s ratio of piston ring
- ν 2 :
-
Poisson’s ratio of cylinder liner
- ρ :
-
lubricant density, kg/m3
- ρ 0 :
-
lubricant density at atmosphere pressure and ambient temperature, kg/m3
- σ :
-
comprehensive roughness, m
- σ 1 :
-
roughness of piston ring, m
- σ 2 :
-
roughness of cylinder liner, m
- σ s :
-
yield limits of material, Pa
- τ 0 :
-
shear strength constant
- η :
-
density of asperity
- φ c :
-
a dimensionless factor
- φ f , φ fs :
-
shear stress factor
- φ x :
-
pressure flow factor in x direction
- φ y :
-
pressure flow factor in y direction
- φ s :
-
shear flow factor
- φ :
-
crank angle, °
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Jiang, Y.K., Zhang, J.P., Hong, G. et al. 3D EHD lubrication and wear for piston ring-cylinder liner on diesel engines. Int.J Automot. Technol. 16, 1–15 (2015). https://doi.org/10.1007/s12239-015-0001-x
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DOI: https://doi.org/10.1007/s12239-015-0001-x