Radial pin for shaft-hub connection

The easiest and oldest way joints. It is a joint with a shape contact. The pin serves primarily to ensure the mutual positioning of the two parts. They are cylindrical or conical. The pins are dimensioned under simplified assumptions without will and without the pressing effect. When designing a pin, the cross section of the pin in the shear area must be the nominal cross-section of the pin.

Fig.1 Radial pin for shaft-hub connection

Torsion stress in the shaft:

τ_{s} = \frac{{16 M}_{T}}{π D^{3}} * \frac{J_{t u b e (s)}}{J_{n e t (s)}} \leq τ_{a l l}

\frac{J_{t u b e (s)}}{J_{n e t (s)}} = 1 / \frac{J_{n e t (s)}}{J_{t u b e (s)}}

τ_s - torsion stress in the shaft - [MPa]

M_T - torque - [Nm]

D - diameter of the shaft - [mm]

τ_all - allowable shear stress - [MPa]

Allowable shear stress:

τ_{a l l} = \frac{0,4 R_{p 0,2 T}}{S_{F}} * C_{c}

τ_all - allowable shear stress - [MPa]

R_p0,2T - the minimum yield strength or 0,2% proof strength at calculation temperature - [MPa]

S_F - safety factor - []

C_c - coefficient of use of joints according to load - []

Coefficient of use of joints according to load:

load	[]
Unidirectional load, non-impact load	0,8
Unidirectional load, with a small impact load	0,7
Unidirectional load, with a big impact load	0,6
Alternating load, with a small impact load	0,45
Alternating load, with a big impact load	0,25

Shear stress in the pin:

τ_{p} = \frac{{4 M}_{T}}{π * d^{2} * D} + \frac{{2 F}_{A}}{π * d^{2}} \leq τ_{a l l}

τ_p - shear stress in the pin - [MPa]

M_T - torque - [Nm]

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

F_A - axial force - [N]

τ_all - allowable shear stress - [MPa]

Bearing stress in the pin and shaft:

p_{1} = \frac{{6 M}_{T}}{D^{2} * d} + \frac{F_{A}}{D * d} \leq σ_{a l l}

p₁ - bearing stress in the pin and shaft - [MPa]

M_T - torque - [Nm]

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

F_A - axial force - [N]

σ_all - allowable bearing stress - [MPa]

Allowable bearing stress:

σ_{a l l} = \frac{0,9 R_{p 0,2 T}}{S_{F}} * C_{c}

σ_all - allowable bearing stress - [MPa]

R_p0,2T - the minimum yield strength or 0,2% proof strength at calculation temperature - [MPa]

S_F - safety factor - []

C_c - coefficient of use of joints according to load - []

Bearing stress in the pin and hub:

p_{2} = \frac{{4 M}_{T}}{d * (D_{h}^{2} - D^{2})} + \frac{F_{A}}{d * (D_{h} - D)}

\leq σ_{a l l}

p₂ - bearing stress in the pin and hub - [MPa]

M_T - torque - [Nm]

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

D_h - diameter of the hub - [mm]

F_A - axial force - [N]

σ_all - allowable bearing stress - [MPa]

Torsion stress in the hub:

τ_{h} = \frac{{16 M}_{T} D_{h}}{π (D_{h}^{4} - D^{4})} * \frac{J_{t u b e (h)}}{J_{n e t (h)}} \leq τ_{a l l}

\frac{J_{t u b e (h)}}{J_{n e t (h)}} = 1 / \frac{J_{n e t (h)}}{J_{t u b e (h)}}

τ_h - torsion stress in the hub - [MPa]

M_T - torque - [Nm]

D - diameter of the shaft - [mm]

D_h - diameter of the hub - [mm]

d - diameter of the pin - [mm]

τ_all - allowable shear stress - [MPa]

If the shaft and hub is loaded with the bending moment in the joint, the bending stress must be checked. If the shaft and hub is loaded with a shear force in the joint, the shear stress must be checked. The shaft and hub may be load in the joint by axial force. The shaft and hub must be checked for axial stresses. When calculating the different load types, it is necessary to calculate the combined stress.

Bending stress in the shaft:

σ_{B (s)} = \frac{{32 M}_{B}}{π D^{3}} * \frac{Z_{t u b e (s)}}{Z_{n e t (s)}} \leq σ_{B a l l}

\frac{Z_{t u b e (s)}}{Z_{n e t (s)}} = 1 / \frac{Z_{n e t (s)}}{Z_{t u b e (s)}}

σ_B(s) - bending stress in the shaft - [MPa]

M_B - bending moment - [Nm]

D - diameter of the shaft - [mm]

σ_Ball - allowable bending stress - [MPa]

Allowable bending stress:

σ_{B a l l} = \frac{0,6 R_{p 0,2 T}}{S_{F}} * C_{c}

σ_Ball - allowable bending stress - [MPa]

R_p0,2T - the minimum yield strength or 0,2% proof strength at calculation temperature - [MPa]

S_F - safety factor - []

C_c - coefficient of use of joints according to load - []

Bending stress in the hub:

σ_{B (h)} = \frac{{32 M}_{B} D_{h}}{π (D_{h}^{4} - D^{4})} * \frac{Z_{t u b e (h)}}{Z_{n e t (h)}} \leq σ_{B a l l}

\frac{Z_{t u b e (h)}}{Z_{n e t (h)}} = 1 / \frac{Z_{n e t (h)}}{Z_{t u b e (h)}}

σ_B(h) - bending stress in the hub - [MPa]

M_B - bending moment - [Nm]

D - diameter of the shaft - [mm]

D_h - diameter of the hub - [mm]

σ_Ball - allowable bending stress - [MPa]

Shear stress in the shaft:

τ_{s (s)} = \frac{{4 F}_{R}}{π D^{2}} * \frac{A_{t u b e (s)}}{A_{n e t (s)}} \leq τ_{a l l}

\frac{A_{t u b e (s)}}{A_{n e t (s)}} = 1 / \frac{A_{n e t (s)}}{A_{t u b e (s)}}

τ_s(s) - shear stress in the shaft - [MPa]

F_R - shear force - [N]

D - diameter of the shaft - [mm]

τ_all - allowable shear stress - [MPa]

Shear stress in the hub:

τ_{s (h)} = \frac{{4 F}_{R}}{π (D_{h}^{2} - D^{2})} * \frac{A_{t u b e (h)}}{A_{n e t (h)}} \leq τ_{a l l}

\frac{A_{t u b e (h)}}{A_{n e t (h)}} = 1 / \frac{A_{n e t (h)}}{A_{t u b e (h)}}

τ_s(h) - shear stress in the hub - [MPa]

F_R - shear force - [N]

D - diameter of the shaft - [mm]

D_h - diameter of the hub - [mm]

τ_all - allowable shear stress - [MPa]

Axial stress in the shaft:

σ_{A (s)} = \frac{{4 F}_{A}}{π D^{2}} * \frac{A_{t u b e (s)}}{A_{n e t (s)}} \leq σ_{A a l l}

\frac{A_{t u b e (s)}}{A_{n e t (s)}} = 1 / \frac{A_{n e t (s)}}{A_{t u b e (s)}}

σ_A(s) - axial stress in the shaft - [MPa]

F_A - axial force - [N]

D - diameter of the shaft - [mm]

σ_Aall - allowable axial stress - [MPa]

Allowable axial stress:

σ_{A a l l} = \frac{0,45 R_{p 0,2 T}}{S_{F}} * C_{c}

σ_Aall - allowable axial stress - [MPa]

R_p0,2T - the minimum yield strength or 0,2% proof strength at calculation temperature - [MPa]

S_F - safety factor - []

C_c - coefficient of use of joints according to load - []

Axial stress in the hub:

σ_{A (h)} = \frac{{4 F}_{A}}{π (D_{h}^{2} - D^{2})} * \frac{A_{t u b e (h)}}{A_{n e t (h)}} \leq σ_{A a l l}

\frac{A_{t u b e (h)}}{A_{n e t (h)}} = 1 / \frac{A_{n e t (h)}}{A_{t u b e (h)}}

σ_A(h) - axial stress in the hub - [MPa]

F_A - axial force - [N]

D - diameter of the shaft - [mm]

D_h - diameter of the hub - [mm]

σ_Aall - allowable axial stress - [MPa]

Combined stress in the shaft:

σ_{t r e s c a (s)}

= \sqrt{{(\frac{Z_{n e t (s)}}{Z_{t u b e (s)}} * K_{t B (s)} * σ_{B (s)})}^{2} + {(\frac{A_{n e t (s)}}{A_{t u b e (s)}} * K_{t A (s)} * σ_{A (s)})}^{2} + 4 ({(\frac{J_{n e t (s)}}{J_{t u b e (s)}} * K_{t s} * τ_{s})}^{2} + τ_{s (s)}^{2})}

\leq σ_{C a l l}

\frac{Z_{n e t (s)}}{Z_{t u b e (s)}} = 1 - (16 / 3 / π) (d / D)

\frac{A_{n e t (s)}}{A_{t u b e (s)}} = 1 - 4 / π (d / D)

\frac{J_{n e t (s)}}{J_{t u b e (s)}} = 1 - (8 / 3 / π) (d / D) \{1 + {(d / D)}^{2}\}

σ_tresca(s) - combined stress in the shaft - [MPa]

K_tB(s) - concentration factor shaft in bending stress - []

σ_B(s) - bending stress in the shaft - [MPa]

K_tA(s) - concentration factor shaft in axial stress - []

σ_A(s) - axial stress in the shaft - [MPa]

K_ts - concentration factor shaft in torsion stress - []

τ_s - torsion stress in the shaft - [MPa]

τ_s(s) - shear stress in the shaft - [MPa]

σ_Call - allowable combined stress - [MPa]

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

Concentration factor shaft in bending stress:

K_{t B (s)} = 3,000 - 6,250 (\frac{d}{D})

+ 41,000 {(\frac{d}{D})}^{2} - 45,000 {(\frac{d}{D})}^{3}

K_tB(s) - concentration factor shaft in bending stress - []

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

Concentration factor shaft in axial stress:

0 \leq d / D \leq 0,7

K_{t A (s)} = 12,806 - 42,602 (\frac{d}{D})

+ 58,333 {(\frac{d}{D})}^{2}

K_tA(s) - concentration factor shaft in axial stress - []

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

Concentration factor shaft in torsion stress:

K_{t s} = 4,000 - 6,055 (\frac{d}{D})

+ 32,764 {(\frac{d}{D})}^{2} - 38,330 {(\frac{d}{D})}^{3}

K_ts - concentration factor shaft in torsion stress - []

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

Allowable combined stress:

σ_{C a l l} = \frac{R_{p 0,2 T}}{S_{F}} * C_{c}

σ_Call - allowable combined stress - [MPa]

R_p0,2T - the minimum yield strength or 0,2% proof strength at calculation temperature - [MPa]

S_F - safety factor - []

C_c - coefficient of use of joints according to load - []

Combined stress in the hub:

σ_{t r e s c a (h)}

= \sqrt{{(\frac{Z_{n e t (h)}}{Z_{t u b e (h)}} * K_{t B (h)} * σ_{B (h)})}^{2} + {(\frac{A_{n e t (h)}}{A_{t u b e (h)}} * K_{t A (h)} * σ_{A (h)})}^{2} + 4 ({(\frac{J_{n e t (h)}}{J_{t u b e (h)}} * K_{t h} * τ_{h})}^{2} + τ_{s (h)}^{2})}

\leq σ_{C a l l}

\frac{Z_{n e t (h)}}{Z_{t u b e (h)}} = 1 - \frac{1}{1 - {(D / D_{h})}^{4}}

* (16 / 3 / π) (d / D_{h}) [1 - {(D / D_{h})}^{3}]

\frac{A_{n e t (h)}}{A_{t u b e (h)}} = 1 - \frac{1}{1 - {(D / D_{h})}^{2}}

* 4 / π (d / D_{h}) [1 - (D / D_{h})]

\frac{J_{n e t (h)}}{J_{t u b e (h)}} = 1 - \frac{1}{1 - {(D / D_{h})}^{4}}

* (8 / 3 / π) (d / D_{h}) \{[1 - {(D / D_{h})}^{3}] + {(d / D_{h})}^{2} [1 - (D / D_{h})]\}

σ_tresca(h) - combined stress in the hub - [MPa]

K_tB(h) - concentration factor hub in bending stress - []

σ_B(h) - bending stress in the hub - [MPa]

K_tA(h) - concentration factor hub in axial stress - []

σ_A(h) - axial stress in the hub - [MPa]

K_th - concentration factor hub in torsion stress - []

τ_h - torsion stress in the hub - [MPa]

τ_s(h) - shear stress in the hub - [MPa]

σ_Call - allowable combined stress - [MPa]

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

D_h - diameter of the hub - [mm]

Concentration factor hub in bending stress:

d / D_{h} \leq 0,4; D / D_{h} \leq 0,9

K_{t B (h)} = C_{1 B (h)} + C_{2 B (h)} (\frac{d}{D_{h}})

+ C_{3 B (h)} {(\frac{d}{D_{h}})}^{2} + C_{4 B (h)} {(\frac{d}{D_{h}})}^{3}

C_{1 B (h)} = 3,000

C_{2 B (h)} = - 6,250 - 0,585 (D / D_{h})

+ 3,115 {(D / D_{h})}^{2}

C_{3 B (h)} = 41,000 - 1,071 (D / D_{h})

- 6,746 {(D / D_{h})}^{2}

C_{4 B (h)} = - 45,000 + 1,389 (D / D_{h})

+ 13,889 {(D / D_{h})}^{2}

K_tB(h) - concentration factor hub in bending stress - []

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

D_h - diameter of the hub - [mm]

C_1B(h) - coefficient - []

C_2B(h) - coefficient - []

C_3B(h) - coefficient - []

C_4B(h) - coefficient - []

Concentration factor hub in axial stress:

0 < D / D_{h} \leq 0,9; d / D_{h} \leq 0,45

K_{t A (h)} = C_{1 A (h)} + C_{2 A (h)} (\frac{d}{D_{h}})

+ C_{3 A (h)} {(\frac{d}{D_{h}})}^{2}

C_{1 A (h)} = 3,000

C_{2 A (h)} = 0,427 - 6,770 (D / D_{h})

+ 22,698 {(D / D_{h})}^{2} - 16,670 {(D / D_{h})}^{3}

C_{3 A (h)} = 11,357 + 15,665 (D / D_{h})

- 60,929 {(D / D_{h})}^{2} + 41,501 {(D / D_{h})}^{3}

K_tA(h) - concentration factor hub in axial stress - []

D - diameter of the shaft - [mm]

d - diameter of the pin - [mm]

D_h - diameter of the hub - [mm]

C_1A(h) - coefficient - []

C_2A(h) - coefficient - []

C_3A(h) - coefficient - []

Concentration factor hub in torsion stress:

d / D_{h} \leq 0,4; D / D_{h} \leq 0,8

K_{t h} = C_{1 (h)} + C_{2 (h)} (\frac{d}{D_{h}})

+ C_{3 (h)} {(\frac{d}{D_{h}})}^{2} + C_{4 (h)} {(\frac{d}{D_{h}})}^{3}

C_{1 (h)} = 4,000

C_{2 (h)} = - 6,055 + 3,184 (D / D_{h})

- 3,461 {(D / D_{h})}^{2}

C_{3 (h)} = 32,764 - 30,121 (D / D_{h})

+ 39,887 {(D / D_{h})}^{2}

C_{4 (h)} = - 38,330 + 51,542 \sqrt{D / D_{h}}

- 27,483 (D / D_{h})

Literature:

AISC: Specification for structural steel buildings: Allowable Stress design and plastic design 1989

Walter D. Pilkey, Deborah F. Pilkey: Peterson’s stress concentration factors. 2008

Joseph E. Shigley, Charles R. Mischke, Richard G. Budynas: Konstruování strojních součástí 2010.

MET-Calc: Allowable stress

A. Bolek, J. Kochman a kol.: Části a mechanismy strojů I. 1989.

K. Kříž a kol.: Strojní součásti 1. 1984.

Download PDF:

Radial pin for shaft-hub connection.pdf

Social media: