147
– an angle of turn δφ
3
of the gear 3;
– a translational vertical displacement δs
Q
of the load Q;
– a horizontal displacement δs
B
of the slider B;
– a displacement δs
A
of the particle A perpendicular to OA.
e sum of work performed in the virtual displacements:
Qδs
Q
– Fδs
B
= 0. (7.1)
Next, we will determine a relationship between the virtual displacements of the particles of the system. e dis-
placements of the load Q and the point of the rim of the disc 1 are equal as a thread holding the load Q is inelastic
and the slipping between the thread and the disc 1 is ignored. erefore, the virtual angle of turn of the disc 1 along
with the gear 2:
δφ
1
=
δs
Q
.
r
1
A virtual displacement of the point K of the rim of the gear 2:
δs
1
= r
2
δφ
1
=
r
2
δs
Q
.
r
1
e virtual displacements of the contact points of the gears 2 and 3 are equal as the slipping between them is ignored.
en, the virtual angle of turn of the gear 3:
δφ
3
=
δs
1
=
r
2
δs
Q
.
r
3
r
1
r
3
e virtual displacement of the point A of the crank rigidly attached to the gear 3:
δs
A
= OA δφ
3
=
r
2
l
δs
Q
.
r
1
r
3
To dene a relationship between the virtual displacements δs
A
and δs
B
we nd a position of the instantaneous center
of rotation P of the link AB. en:
δs
B
=
PB
.
δs
A
PA
From here:
δs
B
=
PB
δs
A
.
PA
From the triangle ∆APB:
PB
=
1
.
PA cos 30°
Hence,
δs
B
=
r
2
l
δs
Q
.
r
1
r
3
cos 30°
e force of the elasticity of the spring is proportional to its deformation:
F = ch.
7.3 SOLUTION