hec mcu00scrn fc101 rev.0

Codigo de Diseno: Design Code:

CRN No. Interno.:

Doc. no. 1007200

Aprobado por:

Appr.

Zheng Yan 2010-08-20 Clase de Doc:

Doc. kind

Calculation Note

Chequeado:

Checked:

Zhao Chunfu 2010-08-20 Proyecto:

Project

Phase II Rehabilitation Works C.H. Machupicchu

Autor:

Prep.

Niu Pengfei 2010-08-20

Departmento Emisor:

Resp. dept

Auxililary Mechanical System Cliente:

Customer

Proveedores:

Suppliers:

No. de Proyecto:

Proj. no.

A001186 Proveedor / Supplier doc. no.:

r

No. de Doc.: Doc. no.:

Lenguaje:Lang.

Indice de Rev.: Rev. ind.

Pagina:

HEC-MCU00CRN-FC101 en 0 No. de p.:

No. of p.

13

Phase II Rehabilitation Works C.H. Machupicchu

Calculation Sheet for Bridge Crane of Powerhouse

QD210/25t

Doc. kind:

Caculation Note Project Phase II Rehabilitation Works C.H. Machupicchu

Title: Caculation for Bridge Crane of Powerhouse

Customer GyM S.A. / EGEMSA

Proj. no.: A001186 Supplier doc. no.: 1007200

HEC Inc.

Doc. no.:

HEC-MCU00SCRN-FC101Lang.: Rev. Ind.: Page:

2

En 0 No. of pages: 13

Revision

Rev.: Date: Description: Creator: Checked: Appr.: Doc. Status:

0 2010-08-20 Initial Release Niu Pengfei Zhao Chunfu Zheng Yan BPA

Doc. Status

Code Description

PRE Preliminary

INF For Information

BPO For Review

BPD For Design

BPA For Approval

BPE Issued for Construction

CCO As Built

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Table of contents

1. Overview/概述 ......................................................................................................... 4

2 .Reference documents/参考文件 ............................................................................ 4

3. Parameters of bridge crane /桥式起重机主要参数 ................................................ 4

4. Calculation of trolley/小车计算 .............................................................................. 5

4.1 Calculation of lifting mechanism/起升机构计算 .................................................. 5 4.1.1 Max. static tension of the cable of main lifting /主起升钢丝绳最大静拉力. 5 4.1.2 Drum speed calculation/卷筒转速计算…. ................................................. 5 4.1.3 Lifting static power /起升静功率 ................................................................ 6 4.1.4 Selection of gearbox/选择减速器 ............................................................. 6 4.1.5 Selection of Brake/选择制动器 ................................................................. 7

4.2 Calculation of mechanism of translation of the trolley /运行机构计算 ................. 7 4.2.1 Static resistance under steady operation/稳态运行静阻力…… .................. 7 4.2.2 Static power of motor /电动机静功率. ......................................................... 8

5. Calculation of bridge frame/ 桥架计算 .................................................................. 8

5.1 Main parameters /主要参数 ............................................................................. 8 5.2 Calculation of static stiffness/静刚度计算 ........................................................ 9 5.3 Calculation of strength /强度计算 .................................................................. 10 5.4 Calculation of stability/稳定性计算 ................................................................ 10

6. Traveling machanism of the bridge / 大车运行机构计算 .................................... 11

6.1 Static resistance under steady operation /稳态运行静阻力 ........................... 11 6.2 Static power of motor /电动机静功率............................................................. 11

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1.Overview/概述

This calculation sheet is based on the technical

requirements and technical parameters of the

bridge-crane of Machupicchu technical

specifications.

本计算书基于 Machupicchu 技术合同中对桥式

起重机设备的技术要求和技术参数.

2. Reference documents/参考文件

HEC-MCU00SCRN-IG101 General drawing of bridge crane

3. Main parameters of bridge crane /桥式起重机主要参数

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Item Values

Capacity 2100 (KN)

Hook (ascent/descent) 0.2~2m/min

Rated capacity 2100(KN)

Travel of the hook 30(m)

Working class Class A

项目：数值

起升能力 2100(KN)

吊钩（起升/降落） 0.2~2m/min

额定重量 2100(KN)

吊钩行程 30（m）

工作级别轻型

4 .Calculation of trolley/小车计算 4.1 Calculation of lifting mechanism /起升机构计算 4.1.1 Max. static tension of the cable of main lifting/主提升钢丝绳的计算

Maximum static tension calculation of the cable of main lifting is as follows:

KNmx

PS Q 6.178

98.026

2100max

Where: QP --Lifting loads， QP =2100 KN

m -- Pulley ratio，m=6 -- Cable lifting efficiency =0.98

x -- Drum double rope around, x =2

The selection of cable diameter “ d ” is as follows:

mmScd 9.35178600085.0max

Where: c -- Cable selection factor, c =0.085

The cable of 38NAT6×19W+FC+1870 is selected base on the maximum static tension and its diameter. Where:

38 -- cable diameter (mm) NAT -- smoothly surfaced steel wire 6X19W -- number of steel core FC+1870– means fiber core and tensile

strength is 1870Mpa.

主起升钢丝绳的最大静拉力计算如下 :

KNmx

PS Q 6.178

98.026

2100max

式中： QP －起升载荷， QP =2100KN

m －滑轮组倍率， m =6

－钢丝绳起升效率 =0.98

x －卷筒双联 x =2 钢丝绳直径 d 的选择

mmScd 9.35178600085.0max

式中： c－为钢丝绳选择系数 c =0.085 根据钢丝绳的最大静拉力及钢丝绳直径

选择其型号：38NAT6×19W＋FC+1870

其中:

38 为直径(mm)

NAT 为光面钢丝

6×19W 为钢丝绳芯数

FC+1870 为纤维芯的钢丝绳，

抗拉强度为 1870

此钢丝绳的破断拉力:891KN

由此得知钢丝绳的安全系数为:891 / 178.6=4.99

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The breaking force of steel rope is 891KN, so the safety factor will be 891/178.6=4.99. This calculation result is meet 5 specified in the specification, and meets the contract requirement.

符合合同安全系数为 5 的要求

4.1.2 Drum speed calculation/卷筒转速计算

Calculation of drum rotational speed:

min/7.3038.114.3

26r

D

mVn

Ot

Where:

V -- Max. lifting speed, 2 m/min

OD -- Loop diameter of the cable

D -- Drum diameter, D=1000mm d -- Cable diameter ,d=38mm

OD =D＋d=1000＋38=1038mm

卷筒转速计算：

min/7.3038.114.3

26r

D

mVn

Ot

式中：V－起升最大速度 V=2m/min

0D －缠绕直径

0D =D＋d=1000＋38=1038mm

D 为卷筒直径=1000mm

d 为钢丝绳直径=38mm

4.1.3 Lifting static power /起升静功率

Lifting static power :

KWVP

P QJ 4.82

85.0100060

2102100

100060

3

Where:

-- Mechanical transmission efficiency, =0.85

V -- Lifting speed, V =2 m/min Primary motor:

PJC=G x J

P =0.8×82.4=65.92KW

G -- The average coefficient of steady-state, G=0.8

Type of motor selected: YZP315S2-8

nP =75KW（JC=40%） n =739r/min

Check of motor overload:

起升静功率:

KWVP

P QJ 4.82

85.0100060

2102100

100060

3

式中：－为机械传动效率, =0.85 初选电动机:

PJC=Gx JP =0.8×82.4=65.92KW

式中：G－稳态平均系数,G=0.8

选电动机型号为:YZP315S2‐8 nP =75KW

（JC=40%） n =739r/min

电动机过载验算:

KWpm

HP J

md 4.524.82

3.31

1.2

式中：H －补偿电压及负载系数,H=2.1

m －电动机的数量 m=1

λm－相对最大转矩系数

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KWpm

HP J

md 4.524.82

3.31

1.2

Where:

H -- Compensation voltage and the load factor, H =2.1

m – The number of motor, m =1

m -- Relative maximum torque coefficient

m =3.3

ndPP

Based on the above results, the overload of selected motor meets the requirements.

nd PP

基于上面计算结果，可以满足电动机过载

要求..

4.1.4 Selection of gearbox/选择减速器

Selection of gearbox:

7.1997.3

739

tn

ni i ‐‐Speed ratio

The proximal ratio to 199.7 is taken 200. Based on i =200, p=75KW, n =739r/min, the gearbox of No.M4PHT-90-200-24 is selected and this gearbox meets the design requirements.

减速器的选择:

速比: i

7.1997.3

739

tn

ni 取接近值 i =200

根据 i =200 ,p=75KW, n =739r/min

选减速器:M4PHT‐90‐200‐24,满足设计要求。

4.1.5 Selection of brake/选择制动器

Selection of brake:

jzhzh MKM =1. 25×772=965 mN.

mNmi

DPM Q

j

772

20062

85.010382100

20

Where:

zhK -- Safety factor for the brake , zhK is taken

1.25 when working class for light duty. -- Mechanical transmission efficiency,

=0.85

选择制动器:

jzhzh MKM =1. 25×772=965 mN.

mNmi

DPM Q

j

772

20062

85.010382100

20

式中：－为机械传动效率, =0.85

zhK 为制动安全系数，工作级别为轻级时

取 zhK =1. 25

选制动器其型号为 YWZ9‐400/E121,

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The brake type YWZ9-400/E121 is selected. The braking device has double brakes. The total braking torque M=2x(1000-2000) mN M zhM , so this braking device meets the design

requirement.

制动力矩 M =2×(1000‐2000)N.m ，双制动。

M zhM 满足合同规范要求

4.2 Calculation of traveling mechanism of the trolley /小车运行机构计算 4.2.1 Static resistance under steady operation /稳态运行静阻力

Static resistance under steady operation:

wpmj FFFF =27181.99+4942.18＋

0=32124.17N

forceFriction --mF wPpF

GQm)( = （ 2100000+371090 ） ×

0.011=27181.99N

resistance Ramp --pF

iPpFGQp)( =（2100000+371090）×

0.002=4942.18N

wF -- Wind resistance, as for indoor use,

So, wF =0

QP -- Lifting capability, QP =2100000N

GP -- Trolley weight， GP =371090N

w -- Friction coefficient，w =0.011 i -- Rampway-related factor， i =0.002

稳态运行静阻力；

wpmj FFFF =27181.99+4942.18＋

0=32124.17N

mF 为摩擦阻力

wPpFGQm)( =（ 2100000+371090）×

0.011=27181.99N

pF 为坡道阻力：

iPpFGQp)( =（ 2100000+371090）×

0.002=4942.18N

wF 为风阻力，因室内使用，所以 wF =0

QP 为起重重量, QP =2100000N

GP 为小车自重， GP =371090N

w摩擦阻力系数，w =0.011

i 与坡道有关的系数， i =0.002

4.2.2 Static power of motor /电动机静功率

Static power of motor：

KWm

VFP yj

J 58.1285.0100060

517.32124

1000

Where: yV -- Trolley speed， yV =5 m/min

m – Number of motor, m =2

电动机静功率：

KWm

VFP yj

J 58.1285.0100060

517.32124

1000

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-- Mechanical transmission efficiency，

=0.85

P= 1.896KW1.581.2 jd pK

i -- Speed ratio

i = 988.3981000560

60450138014.3

60

nV

nD

According to JP and calculated “ i ”, the triple

device of motor, gearbox and brake PK10-RF07-YVPEJ-100L1-4-M1-J2 is selected.

P=2×2.2KW speed ratio i =370

yV 为小车运行速度， yV =5m/min

m 为电动机个数 m =2

为机械传动效率， =0.85

P= jd pK =1.2×1.58=1.896KW

i ‐‐速比

i = 988.3981000560

60450138014.3

60

nV

nD

根据 JP ， i 选三合一电动机，减速器，制动器

PK10‐RF07‐YVPEJ‐100L1‐4‐M1‐J2

P=2×2.2KW 速比 i =370

5. Calculation of bridge / 桥架计算 5.1 Main parameters /主要参数

1. Known values:

Rated lifting capacity 2100KN Trolley weight 371.09KN The total weight of main beam, rails, railings

and electrical appliances will be approximate 105KN

Bridge’s span 12.7m. 2. The following calculation is based on that the

load acts on the center of span. It is safety calculation.

The outline of main beam is as follows:

The moment of inertia of main beam is as follows:

2.13×1010 4mm

The section modulus of main beam is as follows:

1. 已知参数：

·额定起重量 2100KN

·小车自重 371.09KN

·主梁，轨道，栏杆，电器等重 105KN,

·大车跨度 12.7m

2.以下计算按集中载荷作用于跨中,是偏安

全计算.

主梁截面如下图：

主梁惯性矩 2.13×10

10 4mm

主梁抗弯截面模量 W =3.2×107mm3

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W =3.2×107mm3

5.2 Calculation of static stiffness/静刚度计算

Mid-span deflection

Ymm

EI

PLY

x

12

1013.21006.248

1270023710901270022100000

48 105

333

Where: capability Lifting --PQ 2100000N PQ

trolleyofweight -self The --PG 0N71093PG

L -- Span. L=12700mm E --The elasticity modulus of main beam

materials, E =2060002N/mm

The vertical static stiffness shall be less than L/750 from the standard “ Lightweight Classification Group”.

mmLY 9.16750 ≥Y

Based on the above results, the static stiffness meets the requirements.

静刚度计算

跨中挠度:

Ymm

EI

PLY

x

12

1013.21006.248

1270023710901270022100000

48 105

333

式中： QP －起重重量, QP =2100000N

GP －小车自重， GP =371090N

L－跨度，L=12700mm

E — 主梁材料弹性模量； E =

2060002N/mm

对于轻量级工作级别,垂直静刚度不大于 L/750。

mmLY 9.16750 ≥Y

刚度满足设计要求

5.3 Calculation of strength 强度计算

The dynamic load factor of lifting load( ):

= 1 + 0.7 V = 1 + 0.7 0.034 =1.0238

Where: V -- Lifting speed；V=2/ 60 =0.034 m/s The max. bending moment in the beam center line.

84

)2/2/( 2

max

qLLPPM GQ

8

127008100

4

12700)2/3710902/2100000(0238.1

2

mmN.1042.0 10

起升载荷动载系数

=1 + 0.7 V = 1 + 0.7 0.034 =1.0238 式中： V－起升速度；V =2/ 60 =0.034m/s

梁最大弯矩在梁中心

84

)2/2/( 2

max

qLLPPM GQ

=

8

127008100

4

12700)2/3710902/2100000(0238.1

2

mmN.1042.0 10

aMPW

M3.131

102.3

1042.07

10

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aMPW

M157

102.3

1042.07

10

The main beam is made of Q345B(ASTM-A242): Where: n -- Safety factor n =1.5

aS MP

n230

5.1

345

Based on the above results, the strength meets the design requirements.

主梁材质为 Q345B(ASTM-A242)

aS MP

n230

5.1

345

安全系数 n =1.5

故强度满足要求。

5.4 Calculation of stability /稳定性计算

The overall stability of the main beam：

3795.1800

1436

b

ha

Where: a -- In the ratio of height to width h -- Section height of main beam b – Section width of main beam It is unnecessary to check its overall stability if “ a ” is less than 3.

稳定性计算：

主梁整体稳定性： 3795.1800

1436

b

ha 时，

不必验算其整体稳定性。

式中：a ‐‐ 高宽比

h --主梁截面高度

b －主梁截面宽度

6. Traveling machanism of the bridge / 大车运行机构计算

6.1 Static resistance under steady operation /稳态运行静阻力

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Steady state static resistance；

wpmj FFFF =16856+5618.7＋0=22474.7N

mF -- The friction drag

N16856

0.006 0)093570000012()(

wPpF GQm

resistanceRampway pF

5618.7N

0.002 7093500)2100000( )(

iPpF GQp

Where:

wF -- Wind resistance, as to indoor use, wF =0

QP -- Lifting weight, QP =2100000N

GP -- The self-weight of entire trolley, GP =709350N

w -- Friction drag factor，w =0.006

i -- Ramp-related factor， i =0.002

稳态运行静阻力；

wpmj FFFF =16856+5618.7＋0=22474.7N

mF 为摩擦阻力

N16856

0.006 0)093570000012()(

wPpF GQm

pF 为坡道阻力：

5618.7N

0.002 7093500)2100000( )(

iPpF GQp

wF 为风阻力，因室内使用，所以 wF =0

QP 为起重重量, QP =2100000N

GP 为整车自重， GP =709350N

w摩擦阻力系数，w =0.006

i与坡道有关的系数， i =0.002

6.2 Static power of motor/电动机静功率

Static power of motor：

KWm

VFKP yjd 97.3

285.0100060

157.224742.1

100060

Where: Kd -- to consideration with the value of power

magnification factor of inertia effect during start up, Kd=1.2

m -- The number of motor. m =2

yV -- Bridge translation speed. yV =15 m/min

Select gearbox:

电动机静功率：

KWm

VFKP yjd 97.3

285.0100060

157.224742.1

100060

式中：Kd－考虑起动时惯性影响的功率增大系

数， Kd=1.2

m 电动机个数, m =2

yV －大车运行速度， yV =15m/min

减速器选择

速比 33.17360/151000

60014.31380

600

V

Dni

式中：D－车轮直径，D =600

n－输入转速，n =1380r/min，

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33.17360/151000

60014.31380

600

V

Dni

Where:

i -- Speed ratio D -- Wheel diameter. D =600 n – Input rotating speed. n =1380 r/min

Based on speed ratio: i =173.33 P =3.8KW The triple device of motor is selected as follows: PK10-YVPEJ-112M-4 -M1-J2

P =2×4KW i= 178.64 Based on the above result, it meets the requirements.

根据速比， i =173.33 P =3.8kw

选择三合一减速器 PK10‐YVPEJ‐112M‐4 ‐M1‐J2

P =2×4KW i = 178.64 满足使用要求。

Finished

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