Rotor of brushless motor
A rotor of a brushless motor used in a fuel pump includes a permanent magnet having first and second ends that are configured to have a thickness ratio so that a degree of margin of those ends, which is a difference between an allowable stress and a temperature stress due to expansion and contraction of a rotor core caused by a temperature change is equal to or greater than a preset value. As a result, a cracking of the permanent magnet on the both ends that is caused by repeated expansions and contractions of the rotor core is prevented.
1. A rotor for a brushless motor which rotates an impeller of a fuel pump, the rotor comprising:
a shaft;
a single inner core fixed to the shaft; and
a permanent magnet, wherein the permanent magnet is a single bonded magnet of a resin material with magnetic particles and is formed by injection molding, the permanent magnet including
a cylinder part positioned radially outside of the single inner core,
a first end having a tabular shape and located on one axial end relative to the cylinder part and the single inner core, and
a second end having a tabular shape and located on an other axial end relative to the cylinder part and the single inner core, wherein
the permanent magnet has plural magnetic poles arranged around a circumference of the permanent magnet, and
when a full length of the permanent magnet along an axial direction is defined as “a” and a thickness of the first end of the permanent magnet along the axial direction is defined as “b” so that a ratio of b/a satisfies a condition where 0.1≦(b/a)≦0.17.
2. The rotor in claim 1 , wherein
when a thickness of the second end of the permanent magnet along the axial direction is defined as “c”, the permanent magnet satisfies a condition 0.1≦(c/a)≦0.17.
3. The rotor in claim 2 , wherein
the thickness “b” of the first end of the permanent magnet is the same as the thickness “c” of the second end of the permanent magnet.
4. The rotor in claim 1 , wherein
a cross sectional shape of the inner core perpendicular to the axial direction is non-circular.
5. The rotor in claim 4 , wherein
when a maximum thickness along a radial direction between an outer planar face of the inner core and an outer circumferential face of the permanent magnet is defined as “d”, and a minimum thickness thereof is defined as “e”,
a condition (d/e)≧1.4 is satisfied.
6. The rotor in claim 1 , wherein
a gate that serves as an inlet for material during the die-forming process of the permanent magnet is positioned on an end face of the permanent magnet in the axial direction.
7. The rotor in claim 1 , wherein
b/a satisfying the condition where 0.1≦(b/a)≦0.17 results in a difference between allowable stress and an applied stress being greater than or equal to a margin,
b/a being less than 0.1 results in a difference between the allowable stress and the applied stress being less than the margin, and
b/a being greater than 0.17 results in a difference between the allowable stress and the applied stress being less than the margin.
8. The rotor in claim 1 , wherein
the condition 0.1≦(b/a)≦0.17 includes a range of values where a difference between allowable stress and stress is greater than or equal to a predetermined value.
9. The rotor in claim 8 , wherein
the predetermined value prevents cracking.
10. A rotor for a brushless motor which rotates an impeller of a fuel pump, the rotor comprising:
a shaft;
a single inner core fixed to the shaft; and
a permanent magnet, wherein the permanent magnet is a single bonded magnet of a thermoplastic material with magnetic particles and is formed by injection molding, the permanent magnet including
a cylinder part positioned radially outside of the single inner core,
a first end having a tabular shape and located on one axial end relative to the cylinder part and the single inner core, and
a second end having a tabular shape and located on an other axial end relative to the cylinder part and the single inner core, wherein
the permanent magnet has plural magnetic poles arranged around a circumference of the permanent magnet, and
a full length of the permanent magnet along an axial direction is defined as “a”, a thickness of the first end of the permanent magnet along the axial direction is defined as “b”, and a ratio of b/a satisfies a condition where 0.1≦(b/a)≦0.17.
11. The rotor in claim 10 , wherein a thickness of the second end of the permanent magnet along the axial direction is defined as “c” and the permanent magnet satisfies a condition 0.1≦(c/a)≦0.17.
12. The rotor in claim 11 , wherein the thickness “b” of the first end of the permanent magnet is the same as the thickness “c” of the second end of the permanent magnet.
13. The rotor in claim 10 , wherein a cross sectional shape of the inner core perpendicular to the axial direction is non-circular.
14. The rotor in claim 13 , wherein a maximum thickness along a radial direction between an outer planar face of the inner core and an outer circumferential face of the permanent magnet is defined as “d”, a minimum thickness is defined as “e”, and a condition (d/e)≧1.4 is satisfied.
15. The rotor in claim 10 , wherein a gate that serves as an inlet for material during a die-forming process of the permanent magnet is positioned on an end face of the permanent magnet in the axial direction.
16. The rotor in claim 10 , wherein
b/a satisfying the condition where 0.1≦(b/a)≦0.17 results in a difference between allowable stress and an applied stress being greater than or equal to a margin,
b/a being less than 0.1 results in a difference between the allowable stress and the applied stress being less than the margin, and
b/a being greater than 0.17 results in a difference between the allowable stress and the applied stress being less than the margin.
17. The rotor in claim 10 , wherein the condition 0.1≦(b/a)≦0.17 includes a range of values where a difference between allowable stress and stress is greater than or equal to a predetermined value.
18. The rotor in claim 17 , wherein the predetermined value prevents cracking.
19. The rotor in claim 7 , wherein the applied stress is stress due to thermal expansion or contraction.
20. The rotor in claim 16 , wherein the applied stress is stress due to thermal expansion or contraction.