)
)
=
=
8
8
[ [
σ
] ]
t t
f f
J
J
( ( D
p p
a a
=
=
f f
o
o
δ
δ
[ [ [ − σ σ
f
p
f
a
D
] ] ] = = t t
f f
f f
M
M
M
f f
i
i
L
D
D
) ) J +
r
r
a
f f
i
i
f f
i
i
a
=
=
=
=


=
J
D
F
F
D
F
p
r
r
F
+
f f
o
o
f
f
o
o
L
L
L
L
r
r
−
−
G
=
=
3671891 N 2096257 N
外径Ddo×内径Ddi×厚度δg 1099 × 1049 × 4.5
垫片压紧力作 1081.11 mm 用中心圆直径DG
b = 2.53 b0
2 G
流体压力引起的总轴向力 F = 0.785D pc = 预紧状态最小垫片压紧力 Fa = 3.14DG by = 操作状态最小垫片压紧力 Fp = 6.28DG bmpc = 预紧状态螺栓载荷Wa = 3.14DG yb = 操作状态螺栓载荷W p = F + Fp = 需要螺栓面积 Am = max
设计条件 计算压力pc 设计温度Tc 腐蚀裕量C 法兰材料 法兰外径Do 法兰内径Di
螺栓中心圆直径Db
垫片及螺栓计算 4.0 MPa 160 ℃ 2.0 mm 16Mn 1215 mm 1004 mm 1155 mm 22 mm 34 mm 42 mm 33 mm 178 MPa 178 MPa 实际螺栓面积 Ab = 垫 片 材料 缠绕垫 接触宽度ω=N 当b0≤6.4时 b=b0 当b0>6.4时 b0 b y m 25 mm 12.5 mm 8.9449 mm 69 MPa 3.00
法 小端有效厚度δ0 兰 大端有效厚度δ1 颈锥高度h 螺栓孔直径db 许用 应力 [σ ]tf 螺栓材料 许用 [σ ]b 应力 [σ ]t b 螺 螺栓直径 d B 栓 螺距P 螺纹小径di 螺杆直径d0 螺栓数量n=
[ σ ]
f
729133 N
2096257 N 4401024 N
[σ ] f
Wa
[σ ]b
,
Wp [σ ]tb
21364 mm2
π
4
(min(di , d0 ))2 n
实际 ) πDb L= 螺距 n
25900 mm2 5388164 N > 75.59 mm 70 mm
35CrMoA
228 MPa W = 0.5( Am + Ab ) • [σ ]b = 206 MPa 最大 ) 6δ f Lmax＝2d B + 231.429 m + 0.5 30 mm 螺距 3.5 mm 26.211 mm 30 mm 48 个 最小螺栓间距Lmin
] ] ] ] ] ] ] b b ]
+
b b d b f
f
f
f
0
0
B
.
.
5
5
δ
δ
f
A
A
m m
a a
1 1
=
=
=
=
=
=
0 0
( 3 3 . . F
F
7 8 5 7 8 5
.
1 4 1 4
+
+
F
F
D
D
D
D
p p
) G
G G G
/ /
[ y b σ p
y b p
c c
] b
b
=
=
=
=
操作情况下法兰的受力
min( 1.5[σ ]f ,2.5[σ ]n )
t t
267
MPa 201.06873 198.99967 196.93264
[σ ]f ＝
t
(1.33 f ⋅ e +1)M0 δ
MPa
178
λδf2 Di
M 0Y − Zσ R = δ f2 D i
= MPa 32.427892 31.600469 30.796592
假设法兰厚度δ f
许用值
应力计算 轴向应力σ H = 径向应力σ R = 切向应力 σ T = 综合应力
ψ = δ1e + 1 β = 4 / 3δ f e + 1 γ =ψ / T η = δ 3 / d1 f λ = γ +η
fM o = λδ 12 D i
1.5924454 1.5924454 1.5924454 1.7899272 1.7978265 1.8057258 0.8678871 0.8678871 0.8678871 0.4533672 0.4671047 0.481117 1.3212543 1.3349918 1.349004
W
W
预紧情况下法兰的力矩
199065201 N·mm
FG = W =
β
5388164 N
[ [ [ [ [ [ σ σ [ σ [ σ
R R
LG = 0.5(Db − DG ) = 36.9449 mm M a = FF LG =
F
F
1
1
=
a r c s i n
a r c s i n
σ
σ
σ
σ
σ
σ
σ
i i
)
(查GB150表9-3)
螺栓直径和分布满足要求,法兰最小尺寸满足要求。 垫片最小有效密 b = A b [σ ] b = 11.7932 min 封宽度： 2πDb y
A m
mm
<
实际垫片有 效密封宽度b
1
=
(
F
+
F
p
)
/
[ σ
]
b
=
法兰受力计算 预紧情况下法兰的受力
垫片最小宽度满足预紧要求。 预紧情况下法兰的力臂
[σ ]f t＝
MPa
178
MPa 74.428717 73.962144 73.512784
[σ ]f t＝
法兰校核结果
MPa
178
max( 0.5(σ H + σ R ),0.5(σ H + σ T )) MPa 137.74872 136.48091 135.22271
校核合格 校核合格 校核合格
D
D
=
=
f f
i
i
f f
i
i


=
=
N
N
·
m m
m m
240592945 N·mm 240592945 N·mm
M0=MP或Ma×
[σ ]f t (二者中的大者)= [σ ] f
形状常数
h0 = Diδ0 = 148.62 mm
h = h0
0.2826 mm
K=
D0 δ1 = 1.21016 mm = Di δ0
729133 N
L
r
3166776 N
LD = LA + 0.5δ1 =
M D = FD LD =
1.9E+08 N·mm 2.7E+07 N·mm
28398832 N·mm
=
δ
f
2
−
δ
2
cos
β
−
l
=
1
F
F
G
r
r
=
=
=
W
F
F
D
D
=
•
•
c t t
c
g g
β
1 1
=
=
L
G
=
0
0
.
.
5
5
(
(
D
b
−
D
G
L
T= Z= 1.83485 5.30584 10.2859 11.3032
1.54545 mm
查图9-3 F1= 0.88049 查图9-4 V1= 0.36862 查图9-7 f = 1.28156
查表 Y= 9-5 U=
e=
F1 = h0
0.00592
d1 =
U h0δ 02 = V1
100
2205717 101 102
力臂
力矩 58.5
FD = 0.785 D pc =
2 i
FG = Fp =
F
LG = 0.5(Db − DG ) = 36.9449 mm M G = FG LG = LT = 0.5(LA + δ1 + LG ) = 56.2225 mm M T = FT LT = FT = F − FD = 505116 N M 操作力矩： p = FD LD + FG LG + FT LT =