Machine having reciprocating slider crank mechanism, and method for designing machine having reciprocating slider crank mechanism

Patent metadata

Field	Value
Publication number	US-10161476-B2
Application number	US-201615511029-A
Country	US
Kind code	B2
Filing date	Jun 7, 2016
Priority date	Feb 19, 2016
Publication date	Dec 25, 2018
Grant date	Dec 25, 2018

Abstract

A machine having a reciprocating slider crank mechanism, wherein an axis of a crankshaft, an axis of a first balancer shaft and an axis of a second balancer shaft are not arranged on the same plane, wherein vibration is highly controlled. The machine includes the reciprocating slider crank mechanism configured so as to satisfy setting formulae below:

U Cr =U P ×0.5

α Cr =180°

U B(Fr) ={U 1 B(Fr) + +U 2 B(Fr) 2 } 1/2

U 1 B(Fr) =−U P ×0.5×{ Lx′ B(Rr) /( Lx′ B(Rr) −Lx′ B(Fr) )}

U 2 B(Fr) =U P ×0.5×{ Ly′ B /( Lx′ B(Rr) −Lx′ B(Fr) )}

α B(Fr) =180°−arctan( U 2 B(Fr) /U 1 B(Fr) )

U B(Rr) ={U 1 B(Rr) 2 +U 2 B(Rr) 2 } 1/2

U 1 B(Rr) =−U P ×0.5×{ Lx′ B(Fr) /( Lx′ B(Fr) −Lx′ B(Rr) )}

U 2 B(Rr) =−U 2 B(Fr)

α B(Rr) =180°−arctan( U 2 B(Rr) /U 1 B(Rr) ).

First claim

The invention claimed is:

1. A machine having a reciprocating slider crank mechanism, the machine comprising:
a cylinder;
a reciprocal movement portion including
a piston configured to reciprocate in the cylinder,
a piston pin, and
a small end portion of a conrod, the small end portion being connected to the piston by the piston pin;

a rotary movement portion including
a rotatable crankshaft having a crank pin portion, and
a big end portion of the conrod, the big end portion being connected to the crank pin portion of the crankshaft;

a first balancer shaft configured to rotate, together with the rotation of the crankshaft, in an opposite rotation direction to that of the crankshaft at a same rotation speed as that of the crankshaft; and
a second balancer shaft arranged on an opposite side from the first balancer shaft with respect to a center line of the cylinder as seen from an axial direction of the crankshaft, the second balancer shaft configured to rotate, together with the rotation of the crankshaft, in an opposite rotation direction to that of the crankshaft at the same rotation speed as that of the crankshaft; wherein:
an axis of the crankshaft, an axis of the first balancer shaft and an axis of the second balancer shaft are not arranged on a same plane; and
the reciprocating slider crank mechanism is configured so as to satisfy a setting formulae below:
U Cr =U P ×0.5,

α Cr =180°,

U B(Fr) ={U 1 B(Fr) 2 +U 2 B(Fr) 2 } 1/2 ,
U 1 B(Fr) =−U P ×0.5×{ Lx′ B(Rr) /( Lx′ B(Rr) −Lx′ B(Fr) )},

U 2 B(Fr) =−U P ×0.5×{ Ly′ B /( Lx′ B(Rr) −Lx′ B(Fr) )},

α B(Fr) =180°−arctan( U 2 B(Fr) /U 1 B(Fr) ),

U B(Rr) ={U 1 B(Rr) 2 +U 2 B(Rr) 2 } 1/2 ,
U 1 B(Rr) =−U P ×0.5×{ Lx′ B(Fr) /( Lx′ B(Fr) −Lx′ B(Rr) )},

U 2 B(Rr) =−U 2 B(Fr) , and
α B(Rr) =180°−arctan( U 2 B(Rr) /U 1 B(Rr) ),

where
as seen from the axial direction of the crankshaft, the axis of the crankshaft is an origin, an axis extending from the origin toward the piston along the center line of the cylinder is a Y axis and an axis perpendicular to the Y axis is an X axis,
as seen from the axial direction of the crankshaft, the rotation direction of the crankshaft is a forward rotation direction and an opposite direction to the rotation direction of the crankshaft is a reverse rotation direction,
Lx B(Fr) : a X coordinate value of the axis of the first balancer shaft as measured on the X axis,
Ly B(Fr) : a Y coordinate value of the axis of the first balancer shaft as measured on the Y axis,
Lx B(Rr) : a X coordinate value of the axis of the second balancer shaft as measured on the X axis,
Ly B(Rr) : a Y coordinate value of the axis of the second balancer shaft as measured on the Y axis,
β: as seen from the axial direction of the crankshaft, a first angle, in the forward rotation direction, being measured between a straight line, connecting between the axis of the first balancer shaft and the axis of the second balancer shaft, and the Y axis, the first angle being 90°+arctan {(Ly B(Rr) −Ly B(Fr) )/(Lx B(Rr) −Lx B(Fr) )},
γ B(Fr) : as seen from the axial direction of the crankshaft, a second angle, in the forward rotation direction, between a straight line, connecting between the axis of the first balancer shaft and the axis of the crankshaft, and the Y axis, the second angle being 90°+arctan(Ly B(Fr) /Lx B(Fr) ),
γ B(Rr) : as seen from the axial direction of the crankshaft, a third angle, in the forward rotation direction, between a straight line, connecting between the axis of the second balancer shaft and the axis of the crankshaft, and the Y axis, the third angle being 90°+arctan(Ly B(Rr) /Lx B(Rr) ),
X′ axis: an axis inclined from the X axis by β-90° in the forward rotation direction,
Y′ axis: an axis inclined from the Y axis by β-90° in the forward rotation direction,
Lx′ B(Fr) : a X′ coordinate value of the axis of the first balancer shaft as measured on the X′ axis=(Lx B(Fr) −Ly B(Fr) )/tan β)×sin β,
Ly′ B : a Y′ coordinate value of the axis of the first balancer shaft and the second balancer shaft as measured on the Y′ axis=(Lx B(Fr) +Ly B(Fr) ×tan β)×cos β,
Lx′ B(Rr) : a X′ coordinate value of the axis of the second balancer shaft as measured on the X′ axis=(Lx B(Rr) −Ly B(Rr) /tan β)×sin β,
θ Cr : an angle of rotation of the crankshaft in the forward rotation direction (where θ Cr is assumed to be 0° when the crank pin portion of the crankshaft is on the Y axis),
U P : an unbalance amount of the reciprocal movement portion=m P ×R (where m P is the mass of the reciprocal movement portion, and R is a crank radius),
U Cr : an unbalance amount of the rotary movement portion=m Cr ×r Cr (where m Cr is the mass of the rotary movement portion, and r Cr is a distance between the axis of the crankshaft and the center of gravity of the rotary movement portion),
α Cr : an angle in an unbalance direction, which is in the forward rotation direction from the Y axis, of the rotary movement portion when θ Cr =0°,
U B(Fr) : an unbalance amount of the first balancer shaft=m B(Fr) ×r B(Fr) (where M B(Fr) is the mass of the first balancer shaft, and r B(Fr) is a distance between the axis of the first balancer shaft and the center of gravity of the first balancer shaft),
U1 B(Fr) : a Y-axis direction component of the unbalance amount of the first balancer shaft U B(Fr) when θ Cr =0°,
U2 B(Fr) : a X-axis direction component of the unbalance amount of the first balancer shaft=U B(Fr) when θ Cr =0°,
α B(Fr) : an unbalance direction (the angle in the forward rotation direction from the Y axis) of the first balancer shaft when θ Cr =0°,
U B(Rr) : an unbalance amount of the second balancer shaft=m B(Rr) ×r B(Rr) (where m B(Rr) is the mass of the second balancer shaft, and r B(Rr) is a distance between the axis of the second balancer shaft and the center of gravity of the second balancer shaft),
U1 B(Rr) : a Y-axis direction component of the unbalance amount of the second balancer shaft U B(Rr) when θ Cr =0°,
U2 B(Rr) : a X-axis direction component of the unbalance amount of the second balancer shaft U B(Rr) when θ Cr =0°, and
α B(Rr) : an angle in an unbalance direction, which is in the forward rotation direction from the Y axis, of the second balancer shaft when θ Cr =0°.

2. A machine having a reciprocating slider crank mechanism, the machine comprising:
a cylinder;
a reciprocal movement portion including
a piston configured to reciprocate in a cylinder,
a piston pin, and
a small end portion of a conrod, the small end portion being connected to the piston by the piston pin;

a rotary movement portion including
a rotatable crankshaft having a crank pin portion, and
a big end portion of the conrod, the big end portion being connected to the crank pin portion of the crankshaft;

a first balancer shaft configured to rotate, together with the rotation of the crankshaft, in an opposite rotation direction to that of the crankshaft at a same rotation speed as that of the crankshaft; and
a second balancer shaft arranged on an opposite side from the first balancer shaft with respect to a center line of the cylinder as seen from the axial direction of the crankshaft, the second balancer shaft configured to rotate, together with the rotation of the crankshaft, in an opposite rotation direction to that of the crankshaft at the same rotation speed as that of the crankshaft, wherein:
an axis of the crankshaft, an axis of the first balancer shaft and an axis of the second balancer shaft are not arranged on a same plane;
as seen from the axial direction of the crankshaft, a center line of the cylinder is offset from the axis of the crankshaft; and
the reciprocating slider crank mechanism is configured so as to satisfy a setting formulae below:
U Cr =U

Assignees

• Yamaha Motor Co Ltd

Inventors

• Maeda Kazuyuki
• Onodera Masahiro

Classifications

• F16F15/265 Primary

  Arrangement of two or more balancer shafts (F16F15/267 takes precedence) · CPC title

• F02F7/0004

  Crankcases of one-cylinder engines · CPC title

• F02B75/06

  Engines with means for equalising torque · CPC title

• F02B61/02

  for driving cycles · CPC title

• F16F2228/001

  Specific functional characteristics in numerical form or in the form of equations · CPC title